US20110214627A1 - Controller for engine cooling system - Google Patents

Controller for engine cooling system Download PDF

Info

Publication number
US20110214627A1
US20110214627A1 US13/039,599 US201113039599A US2011214627A1 US 20110214627 A1 US20110214627 A1 US 20110214627A1 US 201113039599 A US201113039599 A US 201113039599A US 2011214627 A1 US2011214627 A1 US 2011214627A1
Authority
US
United States
Prior art keywords
coolant
temperature
engine
water pump
cooling fan
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.)
Abandoned
Application number
US13/039,599
Other languages
English (en)
Inventor
Michio Nishikawa
Nobuharu Kakehashi
Koji Ota
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.)
Denso Corp
Original Assignee
Denso 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
Priority claimed from JP2010046588A external-priority patent/JP2011179460A/ja
Priority claimed from JP2010049177A external-priority patent/JP5287769B2/ja
Application filed by Denso Corp filed Critical Denso Corp
Assigned to DENSO CORPORATION reassignment DENSO CORPORATION ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: KAKEHASHI, NOBUHARU, NISHIKAWA, MICHIO, OTA, KOJI
Publication of US20110214627A1 publication Critical patent/US20110214627A1/en
Priority to US13/943,818 priority Critical patent/US9404410B2/en
Abandoned legal-status Critical Current

Links

Images

Classifications

    • 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
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • 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
    • F01P7/02—Controlling of coolant flow the coolant being cooling-air
    • F01P7/04—Controlling of coolant flow the coolant being cooling-air by varying pump speed, e.g. by changing pump-drive gear ratio
    • 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
    • F01P7/164—Controlling of coolant flow the coolant being liquid by thermostatic control by varying pump speed
    • 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
    • F01P3/00—Liquid cooling
    • F01P3/02—Arrangements for cooling cylinders or cylinder heads
    • F01P2003/027—Cooling cylinders and cylinder heads in parallel
    • 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
    • F01P2003/185—Arrangements or mounting of liquid-to-air heat-exchangers arranged in parallel
    • 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
    • F01P2005/105—Using two or more pumps
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2025/00—Measuring
    • F01P2025/08—Temperature
    • F01P2025/30—Engine incoming fluid temperature
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01P—COOLING OF MACHINES OR ENGINES IN GENERAL; COOLING OF INTERNAL-COMBUSTION ENGINES
    • F01P2025/00—Measuring
    • F01P2025/60—Operating parameters
    • F01P2025/66—Vehicle speed
    • 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
    • F01P2031/00—Fail safe
    • F01P2031/30—Cooling after the engine is stopped
    • 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
    • F01P2060/08—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
    • F01P5/00—Pumping cooling-air or liquid coolants

Definitions

  • the present invention relates to a controller for an engine cooling system. Further, the present invention relates to an air-conditioner for an automobile in which heating is performed by use of engine coolant.
  • JP-8-144758A shows an engine cooling system in which engine coolant is circulated in order to cool a cylinder head and cylinder block of an engine.
  • a mechanical water pump circulating the engine coolant is driven by a driving force transmitted from a crankshaft of the engine. While the engine is running, the mechanical water pump is also driven in order to circulate the engine coolant.
  • a combustion chamber of the engine is also cooled, so that anti-knocking ability is improved.
  • the cylinder head temperature may be greater than a specified temperature when the engine is restarted. This specified temperature is established for improving the anti-knocking ability. If the engine is restarted with the cylinder head of high temperature, fuel consumption efficiency may be deteriorated.
  • U.S. Pat. No. 5,337,704 shows an engine cooling system in which engine coolant passed through a cylinder-head passage flows into a heat exchanger for heating a passenger compartment.
  • EP-1008474A1 shows a heating system which includes two heat exchangers into which engine coolant is respectively introduced.
  • a cylinder head In order to improve the anti-knocking ability, a cylinder head should be positively cooled.
  • a cylinder block should be kept at specified temperature or more.
  • a cylinder-head-passage and a cylinder-block-passage are formed in the system, and coolant flow rate flowing through the cylinder-head passage is made larger than that flowing through the cylinder-block-passage.
  • the present invention is made in view of the above matters, and it is an object of the present invention to provide a controller for an engine cooling system, which is capable of improving an anti-knocking ability even when the engine is restarted. Further, it is another object of the present invention to provide an air-conditioner for an automobile which can sufficiently heat a passenger compartment by use of an engine coolant passed through a cylinder head.
  • an electric pump is controlled in such a manner as to circulate a coolant so that a cylinder head of an internal combustion engine is cooled.
  • a controller for an engine cooling system includes: a temperature obtaining means for obtaining a temperature of the coolant; a temperature determination means for determining a target temperature of the coolant at which an anti-knocking ability of the internal combustion engine is improved; and a cooling control means for driving the electric pump to cool the cylinder head even after the internal combustion engine is shut off in a case that the temperature of coolant obtained by the temperature obtaining means exceeds the target temperature determined by the temperature determination means.
  • the cylinder head can be cooled in order to improve an anti-knocking ability.
  • a cylinder head temperature has been preferably controlled. Even at restarting of the engine, the anti-knocking ability can be improved.
  • the temperature determination means continues to execute a target temperature determination processing even after the internal combustion engine is shut off.
  • the cooling control processing can be executed.
  • the engine cooling system is applied to an engine cooling system of a hybrid vehicle equipped with both an internal combustion engine and an electric motor.
  • the cooling control means continues to drive the electric pump even when the temperature of the coolant becomes less than the target temperature of the coolant in a case that the internal combustion engine is shut off and a vehicle speed is greater than or equal to a specified value. Even when the engine is shut off, if the vehicle speed greater than a specified value, it is likely that the engine is restarted. That is, when the driver slightly steps on the accelerator pedal, the engine is restarted. Since the electric pump continues to be driven, a rapid increase in temperature of the cylinder head can be restricted.
  • the cooling control means includes a first cooling control means for increasing a coolant flow rate in such a manner that the coolant flow rate becomes greater than an reference flow rate in a case that the temperature of the coolant obtained by the temperature obtaining means is greater than the target temperature of the coolant; and a second cooling control means for decreasing the coolant flow rate in such a manner that the coolant flow rate becomes less that the reference flow rate in a case that a difference between the temperature of the coolant obtained by the temperature obtaining means and the target temperature of the coolant is within a specified range.
  • the difference between the coolant temperature and the target coolant temperature is within a range, the electricity supplied to the electric pump is reduced. Thus, the electric power of the battery can be saved.
  • the engine cooling system includes a radiator which cools the coolant by heat-exchanging with ambient air, and the temperature determination means obtains an ambient air temperature and determines the target temperature in such a manner as to be greater than the ambient air temperature.
  • an radiator is arranged downstream of a refrigerant condenser of an air conditioner, and the temperature determination means determines the target temperature of the coolant so that the target temperature is greater than a specified temperature which is obtained by adding an addition temperature to the ambient air temperature.
  • the addition temperature corresponds to a heat radiation quantity of the refrigerant condenser.
  • the engine cooling system includes a radiator and an electric cooling fan.
  • the radiator cools the coolant by heat-exchanging with ambient air.
  • the electric cooling fan introduces the ambient air toward the radiator.
  • the controller further includes a cooling fan control means for driving the electric cooling fan even after the internal combustion engine is shut off in a case that the temperature of the coolant exceeds the target temperature of the coolant. In a case that the internal combustion engine is started while the electric pump is stopped, the cooling control means starts driving the electric pump even though the temperature of the coolant does not exceeds the target temperature of the coolant.
  • the cooling fan control means does not starts the electric cooling fan even though the internal combustion engine is started while the electric cooling fan is stopped. In a case that the temperature of the coolant becomes greater than the target temperature, the electric cooling fan is started.
  • the temperature obtaining means obtains a temperature of the coolant in the radiator, a water jacket of the cylinder head, an outlet of the water jacket, or an inlet of the water jacket. Most preferably, the temperature obtaining means obtains the temperature of the coolant in the cylinder head or at outlet of a water jacket of the cylinder head. Thus, the temperature of the coolant can be correctly detected.
  • An air-conditioning system comprises a heat-exchanger for heating an air with a coolant of an internal combustion engine.
  • the internal combustion engine has a first coolant outlet through which the coolant passed through a cylinder head flows out, and a second coolant outlet through which the coolant passed through a cylinder block flows out.
  • the heat-exchanger is comprised of a first exchanging portion and a second exchanging portion. The first exchanging portion receives the coolant from at least the first coolant outlet, and the second exchanging portion receives the coolant from the second coolant outlet of which temperature is higher than that of the coolant flowing into the first exchanging portion.
  • the air temperature passed through the second exchanging portion can be increased more than the case where the air is heated by the low temperature coolant discharged from the first coolant temperature or the case where the air is heated by mixture of high-temperature coolant and the low-temperature coolant.
  • the air which will be introduced into a passenger compartment can be sufficiently heated.
  • FIG. 1 is a schematic chart showing an engine control system
  • FIG. 2A is a graph showing a relationship between a head-coolant temperature “Thead”, a block-coolant temperature “Tblock” and a fuel economy;
  • FIG. 2B is a graph showing a relationship between an ignition timing, a head-coolant temperature “Thead” and a fuel economy;
  • FIG. 3 is a flowchart showing a cooling control processing
  • FIG. 4 is a flowchart showing a control processing of a first water pump
  • FIG. 5 is a flowchart showing a control processing of a second water pump
  • FIG. 6 is a flowchart showing a control processing of a cooling fan
  • FIGS. 7A to 7F are time charts for explaining an operation of the cooling fan, the first water pump and the second water pump;
  • FIGS. 8A to 8C are schematic charts showing another cooling systems
  • FIG. 9 is a chart schematically showing an entire structure of an air conditioner according to a third embodiment.
  • FIG. 10 is a time chart showing a coolant temperature, a radiation heat quantity of heater cores and air flow rate of cooling fan;
  • FIG. 11 is a graph showing a variation in air temperature passed through the first heater core and the second heater core
  • FIG. 12 is a chart schematically showing an entire structure of an air conditioner according to a fourth embodiment
  • FIG. 13 is a chart schematically showing an entire structure of an air conditioner according to a fifth embodiment
  • FIG. 14 is a chart schematically showing an entire structure of an air conditioner according to a sixth embodiment
  • FIG. 15 is a chart schematically showing an entire structure of an air conditioner according to a seventh embodiment
  • FIG. 16 is a chart schematically showing an entire structure of an air conditioner according to an eighth embodiment.
  • FIG. 17 is a chart schematically showing an entire structure of an air conditioner according to a ninth embodiment.
  • FIG. 18 is a chart showing a first heater core and a second heater core according to a tenth embodiment.
  • FIG. 19 is a chart showing a first heater core and a second heater core according to an eleventh embodiment.
  • FIG. 1 schematically shows an entire configuration of a control system in a first embodiment.
  • a vehicle is equipped with an internal combustion engine 10 .
  • the engine 10 is comprised of a cylinder block 11 and a cylinder head 12 .
  • the cylinder block 11 has a cylinder (not shown) in which a piston is slidably provided.
  • the cylinder head 12 is provided on the cylinder block 11 to define a combustion chamber.
  • the power distribution portion 14 has a planetary gear mechanism including a planetary gear, a sun gear and a ring gear.
  • the planetary gear is connected to the output shaft 13 of the engine 10
  • the sun gear is connected to a first shaft 16 for driving a generator 15
  • the ring gear is connected to a second shaft 18 for driving a motor generator 17 .
  • the torque of the engine 10 is distributed to the first shaft 16 and the second shaft 18 through the power distribution portion 14 .
  • the second shaft 18 is connected to wheels 22 through a reduction gear mechanism 21 .
  • the generator 15 generates electricity which is charged in a battery 24 through an inverter 24 .
  • the motor generator 17 is driven receiving electric power from the battery 24 .
  • the torque generated by the motor generator 17 is transmitted to the wheels 22 through the second shaft 18 .
  • both the internal combustion engine 10 and the motor generator 17 When the vehicle is accelerated or the vehicle is running in a high-load condition, both the internal combustion engine 10 and the motor generator 17 generate the torque. When the vehicle is running in low speed, the internal combustion engine 10 is stopped and the motor generator 17 generates torque. Meanwhile, when the vehicle is decelerated, the internal combustion engine 10 is stopped and the motor generator 17 generates electricity by regenerating a running energy, so that the battery 24 is charged. It should be noted that the battery 24 can be charged by driving the engine 10 when the vehicle is stopped.
  • the vehicle is equipped with an air conditioning system 30 for cooling a passenger compartment.
  • the air conditioning system 30 is comprised of a compressor 31 , a condenser 32 , a receiver 33 , an expansion valve 34 , and an evaporator 35 .
  • the compressor 31 is an electric compressor utilizing the electric power charged in the battery 24 .
  • the vehicle is equipped with an engine cooling system 40 for cooling the engine 10 .
  • the engine cooling system 40 has a cylinder-block-passage 41 through which the engine coolant flows in order to cool the cylinder block 11 and a cylinder-head-passage 51 through which the engine coolant flows in order to cool the cylinder head 12 .
  • These passages 41 , 51 are fluidly isolated from each other.
  • the cylinder-block-passage 41 is fluidly connected to a water jacket 42 of the cylinder block 11 .
  • a first water pump 43 is provided in the cylinder-block-passage 41 to supply the engine coolant toward the water jacket 42 of the cylinder block 11 .
  • the first water pump 43 is an electric water pump utilizing the electric power charged in the battery 24 .
  • a first radiator 44 is arranged in the cylinder-block-passage 41 .
  • the first radiator 44 is for cooling the engine coolant passed through the water jacket 42 .
  • the cylinder-head-passage 51 is fluidly connected to a water jacket 52 of the cylinder head 12 .
  • a second water pump 53 is provided in the cylinder-head-passage 51 to supply the engine coolant toward the water jacket 52 of the cylinder head 12 .
  • the second water pump 53 is also an electric water pump utilizing the electric power charged in the battery 24 .
  • a heater core 54 and a second radiator 55 are provided in the cylinder-head-passage 51 .
  • the engine coolant flows through the heater core 54 before flowing through the second radiator 55 .
  • the heater core 54 is for heating air which will be supplied to the passenger compartment.
  • the temperature in the passenger compartment is controlled by adjusting air flow rate flowing through the heater core 54 and bypassing the heater core 54 .
  • the second radiator 55 is for cooling the engine coolant passed through the water jacket 52 .
  • the first radiator 44 and the second radiator 55 are assembled together and are arranged downstream of the condenser 32 in an introduced outside-air-flow direction.
  • the first radiator 44 is arranged upstream of the second radiator 55 in the introduced outside-air-flow direction.
  • a cooling fan 56 is arranged downstream of the first and second radiators 44 , 55 to introduce the outside air toward the radiators 44 , 55 .
  • the cooling fan 56 is an electric fan utilizing electric power charged in the battery 24 .
  • the present control system is provided with an electronic control unit (ECU) 61 and an electronic control unit for air conditioner (AC-ECU) 62 .
  • the ECU 61 and the AC-ECU 62 are mainly constructed of a microcomputer having a CPU, a ROM, a RAM and a backup memory.
  • the AC-ECU 62 receives signals from a room temperature sensor 63 and a user interface 64 . Based on these signals, the AC-ECU 62 controls the compressor 31 based on the received signals.
  • the ECU 61 executes fuel injection control and ignition timing control. Further, the ECU 61 controls the generator 15 and the motor generator 17 .
  • the ECU 61 receives signals from a first coolant-temperature sensor 65 , a second coolant-temperature sensor 66 , a vehicle speed sensor 67 , and an ambient temperature sensor 68 .
  • the first coolant-temperature sensor 65 detects coolant temperature at an outlet or an inlet of the water jacket 52 of the cylinder head 12 . Alternatively, the first coolant-temperature sensor 65 may detect coolant temperature in the water jacket 52 of the cylinder head 12 .
  • the second coolant-temperature sensor 66 detects coolant temperature at an outlet or an inlet of the water jacket 42 of the cylinder block 11 or coolant temperature in the water jacket 42 of the cylinder block 11 .
  • the coolant temperature detected by the first sensor 65 is referred to as head-coolant temperature “Thead”
  • the coolant temperature detected by the second sensor 66 is referred to as block-coolant temperature “Tblock”, hereinafter.
  • each of temperature sensor 65 , 66 may detects coolant temperature in the corresponding radiator 44 , 55 .
  • the ECU 61 controls the first water pump 43 , the second water pump 53 and the cooling fan 56 so as to cool the cylinder block 11 and the cylinder head 12 . Further, the ECU 61 receives various information signals from the AC-ECU 62 .
  • the ambient temperature sensor 68 is provided to detect ambient air temperature around the condenser 32 and the radiators 44 , 55 .
  • the ECU 61 can be comprised of two units. One of units controls the engine 10 and the other controls the generator 15 and the motor generator 17 .
  • the block-coolant temperature “Tblock” when the block-coolant temperature “Tblock” is low, friction is increased. Thus, it is preferable that the block-coolant temperature “Tblock” is maintained at high temperature. Specifically, the block-coolant temperature “Tblock” should be maintained at 85° C. Meanwhile, as the head-coolant temperature “Thead” is lower, the anti-knocking ability is improved. Thus, it is preferable that the head-coolant temperature “Thead” is maintained at low temperature. As shown in FIG. 2B , as the head-coolant temperature “Thead” becomes lower, the ignition timing in trace knock is more advanced, so that the ignition timing comes close to the MBT.
  • This cooling control processing is executed in a specified cycle by the ECU 61 . It should be noted that this cooling control processing can be executed for a specified time period even after the ignition switch is turned off.
  • step S 101 the computer of the ECU 61 reads various signals from sensors, such as the first coolant-temperature sensor 65 , the second coolant-temperature sensor 66 , the vehicle speed sensor 67 , and the ambient temperature sensor 68 . Further, the computer receives information about a cooling requirement. If the cooling requirement exists, the computer receives information about heat radiation quantity of the condenser 32 .
  • the heat radiation quantity of the condenser 32 can be derived by use of a predetermined map. Based on a detection signal of a room temperature sensor 63 and a cooling requirement level, the heat radiation quantity of the condenser 32 is computed according to cooling load (load of air conditioner). Alternatively, the heat radiation quantity can be computed based on a driving condition of the compressor 31 , the refrigerant pressure and the cooling requirement level.
  • step 101 the computer receives information about a heating requirement. If the heating requirement exists, the computer receives information about a lower limit temperature of the coolant.
  • the information about the lower limit temperature of the coolant can be derived by use of a predetermined map based on the detection signal of the room temperature sensor 63 .
  • the process in step S 101 corresponds to an obtaining means of the present invention.
  • a coolant temperature threshold ⁇ is computed.
  • the processes for computing the threshold ⁇ corresponds to a temperature determining means of the present invention.
  • the coolant temperature threshold ⁇ is a parameter for switching a driving level of the second water pump 53 and/or the cooling fan 56 . In the case that the head-coolant temperature “Thead” is higher than the threshold ⁇ , the second water pump 53 and/or the cooling fan 56 is driven in high driving level.
  • step S 102 the computer determines whether the cooling requirement is established.
  • the procedure proceeds to step S 103 in which “ambient air temperature Tair detected by the sensor 68 +10° C.” is defined as the threshold ⁇ .
  • the threshold ⁇ is between 40° C. and 60° C.
  • step S 104 addition temperature ⁇ for cooling is computed.
  • This addition temperature ⁇ is computed based on the heat radiation quantity of the condenser 32 computed in step S 101 and air velocity flowing toward the condenser 32 and the radiators 44 , 55 .
  • the air velocity is computed based on the vehicle speed “VS” detected by the vehicle speed sensor 67 and the driving level of the cooling fan 56 .
  • step S 105 the threshold ⁇ is defined as “ambient air temperature Tair+10° C.+ ⁇ (° C.)”. Since the heat radiation of the condenser 32 has some effect on the cooling efficiency of the second radiator 55 , the threshold ⁇ is determined based on the addition temperature ⁇ .
  • the added temperature value “10° C.” is variable.
  • step S 106 the computer determines whether the threshold ⁇ is less than 40° C.
  • step S 107 the threshold ⁇ is reset to 40° C.
  • the threshold ⁇ is a reference to determine whether driving level of the second water pump 53 and the cooling fan 56 should be set higher. As the driving level is set higher, the electric power consumption of the battery 24 is increased. Therefore, the coolant temperature threshold ⁇ has a lower limit value.
  • step S 108 the procedure determines whether the heating requirement is established.
  • step S 109 the computer determines whether the current coolant temperature threshold ⁇ is less than the lower limit value “Tlow” associated with the heating requirement.
  • step S 110 the coolant temperature threshold ⁇ is reset to the lower limit value “Tlow” associated with the heating requirement.
  • step S 111 the coolant temperature threshold ⁇ is established to satisfy the heating requirement.
  • step S 111 a first water pump control is executed.
  • step S 112 a second water pump control is executed.
  • step S 113 a cooling fan control is executed.
  • FIG. 4 is a flow chart showing the first water pump control executed in step S 111 .
  • step S 210 the computer determines whether the first water pump 43 is stopped.
  • the procedure proceeds to step S 202 in which the computer determines whether the block-coolant temperature “Tblock” is greater than or equal to a start reference temperature “TSAR” (for example, 85° C.).
  • TSAR start reference temperature
  • step S 204 the computer determines whether the first water pump 43 is driven in high driving level. It should be noted that the discharge quantity of the first water pump 43 per unit time in high driving level is greater than that in low driving level. The first water pump 43 consumes more electricity in high driving level than in low driving level.
  • step S 205 the computer determines whether the block-coolant temperature “Tblock” is greater than or equal to a high-level reference temperature “THR” (for example, 100° C.).
  • THR high-level reference temperature
  • step S 204 the procedure proceeds to step S 207 in which the computer determines whether the block-coolant temperature “Tblock” is less than or equal to a low-level reference temperature “TLR” (for example, 95° C.).
  • TLR low-level reference temperature
  • step S 209 the computer determines whether the block-coolant temperature “Tblock” is less than or equal to stop reference temperature “TSOR” (for example, 80° C.).
  • TSOR stop reference temperature
  • the first water pump 43 is not started until the block-coolant temperature “Tblock” becomes the start reference temperature “TSAR”. After the first water pump 43 is started, the first water pump 43 keeps running until the block-coolant temperature “Tblock” becomes less than or equal to the stop reference temperature “TSOR”. Thereby, the block-coolant temperature “Tblock” is kept around the start reference temperature “TSAR” irrespective of whether the engine 10 is running.
  • the start reference temperature “TSAR” is established in such a manner that friction is restricted and heavy thermal load is not applied to the cylinder block 11 .
  • FIG. 5 is a flow chart showing the second water pump control executed in step S 112 . This control processing corresponds to cooling control means of the present invention.
  • step S 301 the computer determines whether the second water pump 53 is stopped.
  • step S 302 the computer determines whether the engine 10 has been started.
  • step S 302 the procedure ends.
  • step S 303 the second water pump 53 is driven in low driving level.
  • step S 304 the computer determines whether the engine 10 is stopped and the vehicle speed “VS” is “0”.
  • step S 305 the computer determines whether the second water pump 53 is driven in high driving level.
  • step S 306 the computer determines whether the second water pump 53 is driven in middle driving level. A discharge quantity of the second water pump 53 in the middle driving level is greater than that in low driving level and less than that in high driving level.
  • step S 306 the procedure determines whether the vehicle speed “VS” is greater than or equal to a reference vehicle speed “RVS” (for example, 30 km/h) or whether the head-coolant temperature “Thead” is greater than or equal to the coolant temperature threshold ⁇ .
  • RVS reference vehicle speed
  • step S 309 the procedure proceeds to step S 308 and step S 309 .
  • step S 308 the current coolant temperature threshold ⁇ is stored as momentum information “MI”.
  • step S 309 the driving level of the second water pump 53 is set to the middle driving level.
  • the head-coolant temperature “Thead” is not greater than or equal to the threshold ⁇ , when the vehicle speed “VS” is greater than the reference vehicle speed “RVS”, the driving level of the second water pump 53 is changed from the low driving level to the middle driving level. Thus, it is possible to enhance the cooling efficiency based on an estimation of engine start. It can be avoided that the head-coolant temperature “Thead” suddenly exceeds the threshold ⁇ .
  • step S 306 the procedure proceeds to step S 310 in which the computer determines whether the head-coolant temperature “Thead” is greater than or equal to an upper limit temperature “TUL” (for example, 70° C.). The upper limit temperature “TUL” is greater than the coolant temperature threshold ⁇ .
  • step S 311 the computer determines whether the current vehicle speed “VS” is less than or equal to “RVS ⁇ 15” and the head-coolant temperature “Thead” is less than or equal to “MI ⁇ 10”.
  • step S 311 the procedure proceeds to step S 312 in which the driving level of the second water pump 53 is set to the low driving level.
  • step S 313 the driving level of the second water pump 53 is set to the high driving level.
  • step S 305 the procedure proceeds to step S 314 in which the computer determines whether the head-coolant temperature “Thead” is less than or equal to “TUL ⁇ 10”.
  • step S 314 the procedure proceeds to step S 315 in which the momentum information “MI” is stored.
  • step S 316 the driving level of the second water pump 53 is changed to the middle driving level.
  • step S 317 the computer determines whether the head-coolant temperature “Thead” is greater than or equal to the coolant temperature threshold ⁇ .
  • step S 318 the second water pump 53 is stopped.
  • step S 319 the computer determines whether the head-coolant temperature “Thead” is greater than or equal to a value obtained by adding a specified value (for example, 10° C.) to the threshold ⁇ .
  • step S 319 the procedure proceeds to step S 309 in which the driving level of the second water pump 53 is set to the middle driving level.
  • step S 320 the driving level of the second water pump 53 is set to the low driving level.
  • FIG. 6 is a flow chart showing the cooling fan control executed in step S 113 . This control processing corresponds to cooling fan control means of the present invention.
  • step S 401 the computer determines whether the cooling fan 56 is stopped.
  • step S 402 the computer determines whether the vehicle speed “VS” is lower than or equal to the reference vehicle speed “RVS”.
  • step S 403 the computer determines whether the vehicle acceleration “VA” is less than or equal to a reference acceleration “RVA”.
  • the vehicle acceleration “VA” is computed based on the vehicle speed “VS” detected by the vehicle speed sensor 67 .
  • step S 404 the computer determines whether the head-coolant temperature “Thead” is greater than or equal to the coolant temperature threshold ⁇ .
  • step S 405 the current coolant temperature threshold ⁇ is stored as momentum information “MI”.
  • step S 406 the cooling fan 56 is started to be driven in high driving level. It should be noted that the momentum information “MI” stored in step S 405 is independent from the momentum information “MI” stored in second water pump control shown in FIG. 5 .
  • step S 401 the procedure proceeds to step S 407 in which the computer determines whether the engine 10 is stopped and the vehicle speed “VS” is “0”.
  • step S 407 the procedure proceeds to step S 408 in which the computer determines whether the vehicle speed “VS” is less than or equal to a reference vehicle speed “RVS”.
  • step S 409 the cooling fan 56 is stopped.
  • the cooling fan 56 is stopped. Thereby, electric power consumption of the battery 24 can be reduced.
  • a timing at which the cooling fan 56 is started to be driven can be retarded relative to a timing at which the head-coolant temperature “Thead” becomes greater than or equal to the threshold ⁇ , whereby hunting of the cooling fan 56 can be avoided.
  • step S 408 the procedure proceeds to step S 410 in which the computer determines whether the driving level of the cooling fan 56 is high driving level.
  • step S 410 the procedure proceeds to step S 411 in which the computer determines whether the head-coolant temperature “Thead” is less than or equal to “MI ⁇ 10”.
  • step S 412 the driving level of the cooling fan 56 is set to low driving level. The air flow rate per unit time in high driving level is greater than that in low driving level.
  • step S 410 the procedure proceeds to step S 413 in which the computer determines whether the head-coolant temperature “Thead” is greater than or equal to the coolant temperature threshold ⁇ .
  • step S 413 the procedure proceeds to step S 414 in which the momentum information “MI” is stored.
  • step S 415 the driving level of the cooling fan 56 is changed to the high driving level.
  • step S 416 the computer determines whether the head-coolant temperature “Thead” is less than the coolant temperature threshold ⁇ .
  • step S 417 the cooling fan 56 is stopped.
  • FIGS. 7A-7F operations of the cooling fan 56 , the first water pump 53 and the second water pump 43 will be described, hereinafter.
  • FIG. 7A shows the vehicle speed “VS”
  • FIG. 7B shows the engine speed “NE”
  • FIG. 7C shows the coolant temperature “TCL”.
  • a solid line represents the head-coolant temperature “Thead”
  • a two-dashed line represents the block-coolant temperature “Tblock”.
  • FIG. 7D shows the driving level of the cooling fan 56
  • FIG. 7E shows the driving level of the second water pump 53
  • FIG. 7F shows the driving level of the first water pump 43 .
  • the head-coolant temperature “Thead” is higher than the coolant temperature threshold ⁇ and the cooling fan 56 is started in the high driving level.
  • the driving level of the second water pump 53 is changed from the low driving level to the middle driving level.
  • the vehicle speed “VS” exceeds the reference vehicle speed “RVS” and the cooling fan 56 is stopped.
  • the engine 10 is shut off.
  • the vehicle speed “VS” is not “0” and the head-coolant temperature “Thead” is greater than or equal to the threshold ⁇ , the second water pump 53 is driven in the middle driving level. Meanwhile, since the vehicle speed “VS” is greater than or equal to the reference vehicle speed “RVS”, the cooling fan 56 is kept OFF.
  • the vehicle speed “VS” is decelerated and the vehicle speed “VS” becomes lower than the reference vehicle speed “RVS” at timing t 5 .
  • the cooling fan is restarted in high driving level.
  • the head-coolant temperature “Thead” becomes lower than the coolant temperature threshold ⁇ .
  • the cooling fan 56 and the second water pump 53 are driven in the low driving level.
  • the vehicle speed “VS” becomes “0” and the cooling fan 56 and the second water pump 53 are stopped.
  • the block-coolant temperature “Tblock” is not greater than the start reference temperature “TSAR”, the first water pump 43 is kept stopped, so that the block-coolant temperature “Tblock” is increasing.
  • the driver operates the accelerator pedal to start the engine 10 , so that the second water pump 53 is started in the low driving level.
  • the head-coolant temperature “Thead” exceeds the threshold ⁇ and the driving level of the second water pump 53 is changed to the middle driving level. It should be noted that the vehicle acceleration “VA” is greater than the reference acceleration “RVA” at this moment. Thus, the cooling fan 56 is kept stopped.
  • the operation of the engine 10 is continued and the waste heat quantity of the engine 10 increases.
  • the block-coolant temperature “Tblock” is greater than the start reference temperature “TSAR” and the first water pump 43 is started in the low driving level.
  • the head-coolant temperature “Thead” exceeds the upper limit temperature “TUL”, so that the driving level of the second water pump 53 is changed to the high driving level.
  • the engine 10 is shut off at timing t 12 , so that the increase in head-coolant temperature “Thead” and block-coolant temperature “Tblock” is stopped.
  • the head-coolant temperature “Thead” becomes lower than the upper limit temperature “TUL”, so that the driving level of the second water pump 53 is changed to the middle divining level.
  • the block-coolant temperature “Tblock” becomes lower than the stop reference temperature “TSOR”, so that the first water pump 43 is stopped.
  • the vehicle speed “VS” is further decelerated and the cooling fan 56 is started in the high driving level at timing t 15 .
  • the vehicle speed “VS” becomes “0”. It should be noted that since the head-coolant temperature “Thead” is significantly greater than the coolant temperature threshold ⁇ , the cooling fan 56 and the second water pump 53 are kept driven in the current driving level.
  • the engine coolant is circulated to cool the cylinder head 12 .
  • the temperature of the cylinder head 12 will decrease to the desired value for improving the anti-knocking ability at a time of restarting the engine 10 .
  • the anti-knocking ability is improved and the fuel consumption efficiency can be enhanced.
  • the reducing of the power consumption of the battery has a priority to the decreasing of the head-coolant temperature “Thead”. Therefore, while reducing the power consumption of the battery 24 , the head-coolant temperature “Thead” can be kept low.
  • the driving level of the second water pump 53 is the middle driving level or the low driving level. Even when the head-coolant temperature “Thead” is greater than or equal to the threshold ⁇ , as long as a difference between the head-coolant temperature “Thead” and the threshold ⁇ is within a specified range, the second water pump 53 is driven in the low driving level. Thereby, in a situation that the head-coolant temperature “Thead” will decrease without circulating the engine coolant, the power saving of the battery 24 can be achieved.
  • the cooling fan 56 is driven to cool the engine coolant flowing through the cylinder head 12 .
  • the engine coolant is efficiently cooled by the cooling fan 56 , so that the cylinder head 12 can be cooled rapidly after the engine 10 is shut down.
  • the second water pump 53 is also restarted.
  • a rapid increase in temperature of the cylinder head 12 can be restricted easier than a case where the second water pump 53 is started when the head-coolant temperature “Thead” exceeds the coolant temperature threshold ⁇ .
  • the cooling fan 56 is not started. The cooling fan 56 is started when the head-coolant temperature “Thead” exceeds the coolant temperature threshold ⁇ . Therefore, the electric power for driving the cooling fan 56 can be saved.
  • the cylinder-block-passage and the cylinder-head-passage can be combined as one passage.
  • a flow rate control valve 73 is disposed at a branch portion of the water jackets 42 , 52 . According to control signals from the ECU 61 , the flow rate control valve 73 controls the flow rate of engine coolant flowing through each water jacket 42 , 52 .
  • a water temperature sensor is provided to each of outlets of the water jackets 42 , 52 to detect the head-coolant temperature “Thead” and the block-coolant temperature “Tblock”.
  • the ECU 61 controls the water pump 72 and the flow rate control valve 73 in order to control the head-coolant temperature “Thead” and the block-coolant temperature “Tblock”.
  • a thermostat 74 is provided in the coolant passage.
  • a bypass passage 75 is provided which bypasses the radiator 71 . When the engine coolant temperature is low, the engine coolant flows through the bypass passage 75 .
  • the thermostat 74 is a well known mechanical thermostat or an electrical thermostat.
  • the bypass passage 75 can be provided to the engine cooling system 40 in the first embodiment.
  • the engine coolant passed through the water jacket 42 can be introduced into the water jacket 52 through a bypass passage 76 .
  • the engine coolant passed through the water jacket 52 can be introduced into the water jacket 42 through a bypass passage 77 .
  • the present invention is not limited to the above-mentioned embodiments, for example, may be performed as follows.
  • the first water pump 43 is a mechanical water pump and the second water pump 53 is an electric water pump which can be driven even after the engine 10 is shut off. Since the first water pump 43 is driven by the engine torque, the electric power of the battery 24 can be saved.
  • the coolant temperature threshold ⁇ can be varied between when the engine 10 is ON and when the engine 10 is OFF. For example, when the engine is OFF, the threshold ⁇ can be set larger by a specified value than that of when the engine is ON. In this case, the threshold ⁇ is set for improving the anti-knocking ability. The electric power of the battery 24 can be saved.
  • the second water pump 53 can be stopped in a case that the head-coolant temperature “Thead” is not greater than the threshold ⁇ .
  • the engine coolant flowing through the cylinder head 12 can be cooled by the evaporator of the air conditioning system 30 .
  • the driving levels of the first water pump 43 , the second water pump 53 and the cooling fan 56 can be changed continuously instead of stepwise.
  • the second water pump 53 can be started according to a variation in head-coolant temperature “Thead”.
  • the present invention can be applied to a hybrid vehicle and a vehicle having a function of idle reduction control. Also, the present invention can be applied to a vehicle equipped with a conventional engine. Further, the present invention can be applied to a vehicle equipped with a supercharger. In such a vehicle, high compression ratio can be obtained.
  • the water jacket 42 and the water jacket 52 are fluidly connected in parallel. Alternatively, these water jackets 42 , 52 are fluidly connected in series.
  • FIG. 9 schematically shows an entire structure of an air conditioner according to third embodiment.
  • An air-conditioner is provided to a hybrid vehicle.
  • the air-conditioner 101 is provided with a first coolant circuit 110 and a second coolant circuit 120 .
  • the engine coolant passed through a cylinder head 131 flows in the first coolant circuit 110 .
  • the first coolant circuit 110 includes a first heater core 111 , a first water pump 112 , and a first temperature sensor 113 .
  • the engine coolant passed through a cylinder block 132 flows in the second coolant circuit 120 .
  • the second coolant circuit 120 includes a second heater core 121 , a second water pump 122 , and a second temperature sensor 123 .
  • a cylinder block 132 and a cylinder head 131 of the engine 130 have well-known configuration.
  • the cylinder head 131 has a first coolant inlet 131 a and a first coolant outlet 131 b .
  • the engine coolant flows through a coolant passage formed in the cylinder head 131 .
  • the coolant flows into the coolant passage through the first coolant inlet 131 a , and flows out from the coolant passage through the first coolant outlet 131 b.
  • the cylinder block 132 has a second coolant inlet 132 a and a second coolant outlet 132 b .
  • the engine coolant flows into a coolant passage formed in the cylinder block 132 through the second coolant inlet 132 a , and flow out through the second coolant outlet 132 b.
  • the first heater core 111 and the second heater core 121 have well known configuration comprised of tubes and fins.
  • first heater core 111 and the second heater core 121 are fluidly independent from each other.
  • a coolant inlet 111 a of the first heater core 111 is connected to the first coolant outlet 131 b through a pipe.
  • a coolant inlet 121 a of the second heater core 121 is connected to the second coolant outlet 132 b through a pipe.
  • the first heater core 111 and the second heater core 121 are accommodated in a duct (not shown) of the air-conditioner.
  • the first heater core 111 and the second heater core 121 are arranged in series with respect to an air flow.
  • the second heater core 121 is arranged downstream of the first heater core 111 .
  • a first temperature sensor 113 is disposed between the first coolant outlet 131 b and the coolant inlet 111 a of the first heater core 111 , so that the first temperature sensor 113 detects temperature of coolant discharged from the first coolant outlet 131 b .
  • a second temperature sensor 123 is disposed between the second coolant outlet 132 b and the coolant inlet 121 a of the second heater core 121 , so that the second temperature sensor 123 detects temperature of coolant discharged from the second coolant outlet 132 b.
  • a first water pump 112 and a second water pump 122 generate coolant flow and adjust coolant flow rate.
  • the first water pump 112 is arranged between the coolant outlet 111 b of the first heater core 111 and the first coolant inlet 131 a of the cylinder head 131 .
  • the second water pump 122 is arranged between the coolant outlet 121 b of the second heater core 121 and the second coolant inlet 132 a of the cylinder block 132 .
  • the first water pump 112 and the second water pump 122 are electric pumps. In the present embodiment, the first water pump 112 and the second water pump 122 are controlled in such a manner that the coolant flow rate in the cylinder head 131 is greater than that in the cylinder block 132 .
  • the coolant discharged from the first coolant outlet 131 b flows into the first heater core 111 , then flows into the engine 130 through the first coolant inlet 131 a.
  • the coolant discharged from the second coolant outlet 132 b flows into the second heater core 121 , then flows into the engine 130 through the second coolant inlet 132 a.
  • both the first coolant circuit 110 and the second coolant circuit are fluidly connected to a radiator (not shown).
  • FIG. 10 is a time chart showing a coolant temperature, a radiation heat quantity of heater cores 111 , 121 and air flow rate of cooling fan.
  • FIG. 10 shows a case where the coolant temperature rises to a minimum temperature necessary for heating and then the coolant temperature is maintained at this temperature.
  • a heating of the passenger compartment has priority.
  • the second water pump 122 is stopped and the first water pump 112 is driven to circulate a specified quantity of the coolant in the first coolant circuit 110 .
  • the coolant is circulated only in the first coolant circuit 110 .
  • the temperature of coolant flowing into the first core 111 is increased.
  • the circulating coolant flow rate is defined in such a manner that the coolant temperature reaches the first specified temperature T 1 and the second specified temperature T 2 as soon as possible.
  • the cooling fan is started. Then, when the coolant temperature becomes a second specified temperature T 2 at timing t 2 , the air flow rate of the cooling fan is increased to a specified value.
  • the second specified temperature T 2 is a minimum temperature necessary for obtaining a target outlet air temperature.
  • the second specified temperature T 2 is a reference temperature on which the computer determines whether the engine should be driven to heat the passenger compartment.
  • the first specified temperature T 1 is temperature at which the air can be introduced into the passenger compartment.
  • the second water pump 122 is started and the first water pump 111 is controlled in such a manner that the coolant flow rate in the cylinder head 131 is increased.
  • a warm-up of the engine 130 is completed.
  • the engine 130 is operated in a stable condition.
  • the computer controls the first and the second water pump 112 , 122 in such a manner that the coolant flow rate in the cylinder head 131 is greater than that in the cylinder block 132 .
  • the first water pump 112 is controlled so that the coolant temperature flowing into the first heater core 111 reaches a third specified temperature T 3 .
  • the third specified temperature T 3 is a target temperature of the coolant passed through the cylinder head 131 , which is established for positively cooling the cylinder head 131 .
  • the computer controls the second water pump 122 is such a manner that the coolant temperature flowing into the second heater core 121 becomes the second specified temperature T 2 .
  • the cylinder head 131 is kept at low temperature so that the anti-knocking ability is improved. Also, the cylinder block 132 is kept at high temperature so that viscosity of engine oil is hardly deteriorated. Thus, an increase in friction of the engine can be restricted.
  • the computer controls the cooling fan in such a manner that air flow rate of the cooling fan corresponds to a target air temperature TAO.
  • FIG. 10 also shows a comparative example in which the coolant passed through the cylinder head 131 and the coolant passed through the cylinder block 132 are merged in the engine 130 .
  • the merged coolant flows out from the engine 130 through a single coolant outlet and flows into a single heater core.
  • a ratio between the coolant flow rate in the cylinder head and the coolant flow rate in the cylinder block is fixed value.
  • the coolant temperature reaches the first specified temperature T 1 and the cooling fan is started.
  • the coolant temperature reaches the second specified temperature T 2 and the cooling fan is driven to obtain the air flow rate corresponding to the target air temperature TAO.
  • a radiation heat quantity of the second heater core 121 is greater than that of the comparative example. Consequently, as shown in FIG. 11 , the air temperature passed through the second heater core 121 can be made greater than that of the comparative example.
  • FIG. 11 is a graph showing a variation in air temperature passed through the first heater core 111 and the second heater core 121 .
  • the coolant passed through the cylinder head 131 is heat-exchanged with the air passing through the first heater core 111 .
  • the coolant temperature passed through the cylinder head 131 is lower that a minimum temperature required for heating the passenger compartment, the passing air can receive a lot of heat from the coolant of which flow rate is larger than that of the coolant passed through the cylinder block 132 .
  • the temperature of air A 1 passed through the first heater core 111 comes close to the coolant temperature Th 1 before flowing into the first heater core 111 .
  • the coolant passed through the cylinder block 132 is heat-exchanged with the air A 1 passed through the first heater core 111 . Since the coolant temperature passed through the cylinder block 132 is higher than the coolant temperature passed through the cylinder head 131 , the temperature of air A 2 passed through the second heater core 121 can be made higher that that of the air A 1 .
  • the computer adjusts the coolant flow rate passing through the second heater core 121 by controlling the second water pump 122 .
  • the air temperature passed through the second heater core 121 can be increased more than the case where the air is heated by the low temperature coolant discharged from the first coolant outlet 131 b or the case where the high-temperature coolant and the low-temperature coolant is merged.
  • the air is heated by using of low-temperature coolant passing through the first heater core 111 and high-temperature coolant passing through the second heater core 121 .
  • the temperature of air A 1 may be greater than the second specified temperature T 2 .
  • FIG. 12 schematically shows an entire structure of an air conditioner according to a fourth embodiment.
  • the second coolant circuit 120 has a bypass passage 124 and a flow path selector valve 125 .
  • the bypass passage 124 bypasses the second heater core 121 .
  • the flow path selector valve 125 switches a flow path between the bypass passage 124 and the second hater core 121 .
  • the engine coolant flows through the bypass passage 124 .
  • the flow path selector valve 125 can be replaced by a flow regulating valve.
  • FIG. 13 schematically shows an entire structure of an air conditioner according to a fifth embodiment.
  • a single water pump 143 circulates the coolant.
  • a hydraulic resistance in the first coolant circuit 110 is set lower than that in the second coolant circuit 120 , so that the coolant flow rate in the cylinder head 131 is greater than that in the cylinder block 132 .
  • the passage sectional area of the coolant passage in the cylinder head 131 is larger than that in the cylinder block 132 .
  • FIG. 14 schematically shows an entire structure of an air conditioner according to a sixth embodiment.
  • the present embodiment is based on the fifth embodiment shown in FIG. 13 .
  • a bypass passage 124 and a flow regulating valve 126 are added to the fifth embodiment.
  • the computer controls the flow regulating valve 126 in such a manner that the coolant flow rate in the cylinder head 131 is greater than that in the cylinder block 132 .
  • FIG. 15 schematically shows an entire structure of an air conditioner according to a seventh embodiment.
  • the fifth embodiment shown in FIG. 13 is modified as follows.
  • a diversion portion 142 is formed between the first coolant outlet 131 b and the first heater core 111 .
  • the coolant discharged from the first coolant outlet 131 b is diverged at the diversion portion 142 .
  • the diverged coolant flows into a radiator 151 , and then merged at a confluent portion 141 .
  • bypass passage 152 and a thermostat 153 are provided.
  • a diversion portion 145 is formed between the second coolant inlet 132 b and the second heater core 121
  • a confulent portion 146 is formed between the first coolant outlet 131 b and the first heater core 111 .
  • a flow regulating valve 147 is provided at the diversion portion 145 . The flow regulating valve 147 adjusts the coolant flow rate which flows toward the second heater core 121 and the confluent portion 146 .
  • a part of the high-temperature coolant discharged from the second coolant outlet 132 b is merged with the low-temperature coolant discharged from the first coolant outlet 131 b and then flows into the first heater core 111 .
  • the other high-temperature coolant discharged from the second coolant outlet 132 b flows into the second heater core 121 .
  • FIG. 16 schematically shows an entire structure of an air conditioner according to an eighth embodiment.
  • the seventh embodiment shown in FIG. 15 is modified so that the flow regulating valve 147 is replaced by a thermostat 148 .
  • FIG. 17 schematically shows an entire structure of an air conditioner according to a ninth embodiment.
  • the ninth embodiment is a modification of the eighth embodiment.
  • a confluent portion 149 is formed upstream of a radiator 151 .
  • This confluent portion 149 is fluidly connected to a confluent portion 141 downstream of the first and the second heater core 111 , 121 .
  • the coolant discharged from the radiator 151 flows into a water pump 143 .
  • the coolant temperature flowing into the cylinder head 131 can be made low.
  • FIG. 18 shows a first heater core 111 and a second heater core 121 .
  • the first heater core 111 and the second heater core 121 are integrated to one unit.
  • the first heater core 111 has an inlet tank having an inlet 111 a and a plurality of tubes.
  • the second heater core 121 has an inlet tank having an inlet 121 a and a plurality of tubes.
  • the first heater core 111 and the second heater core 121 have a common outlet tank 161 .
  • the outlet tank 161 has an outlet 161 b.
  • the low-temperature coolant passed through the first heater core 111 and the high-temperature coolant passed through the second heater core 121 are merged in the outlet tank 161 .
  • FIG. 19 shows a first heater core 111 and a second heater core 121 .
  • the first heater core 111 and the second heater core 121 are integrated to one unit.
  • the first heater core 111 has an outlet tank having an outlet 111 b and a plurality of tubes.
  • the second heater core 121 has an inlet tank having an inlet 121 a and a plurality of tubes.
  • the first heater core 111 and the second heater core 121 have a common header tank 161 .
  • This header tank 161 has an inlet 161 a which communicates with the first coolant outlet 131 b of the cylinder head 131 .
  • the high-temperature coolant discharged from the second coolant outlet 132 b flows through the second heater core 121 and flows into the common header tank 161 .
  • this coolant merges with the low-temperature coolant discharged from the first coolant outlet 131 b of the cylinder head 131 .
  • the merged coolant flows through the first heater core 111 and flows out from the outlet 111 b of the heater core 111 .
  • the coolant discharged from the first coolant outlet 131 b is the coolant which has cooled the cylinder head 131 .
  • the coolant discharged from the coolant outlet 131 b may include a part of the coolant which has cooled the cylinder block 132 .
  • the coolant discharged from the second coolant outlet 132 b is the coolant which has cooled the cylinder block 132 .
  • the coolant discharged from the second coolant outlet 132 b may include a part of the coolant which has cooled the cylinder head 131 .
  • the coolant temperature discharged from the second coolant outlet 132 b is higher than that discharged from the first coolant outlet 131 b.
  • the coolant flowing into the second heater core 121 is the coolant discharged from the second coolant outlet 132 b .
  • This coolant may include a part of the coolant discharged from the first coolant outlet 131 b.
  • the coolant temperature flowing into the second heater core 121 is higher than an average temperature of the coolant discharged from the second coolant outlet 132 b and the coolant discharged from the first coolant outlet 131 b.
  • the coolant flow rate flowing into the first heater core 111 can be set equal to the coolant flow rate flowing into the second heater core 121 .
  • the engine 130 has the first coolant inlet 131 a and the second coolant inlet 132 a .
  • the engine 130 may have only one coolant inlet.
  • the first heater core 111 and the second heater core 121 may be arranged in parallel.
  • the coolant temperature flowing into the first heater core 111 can be maintained at the third specified temperature T 3 .
  • waste heat of an engine for a hybrid vehicle is utilized as a heat source.
  • waste heat of supercharging engine, a range extender and the like can be utilized as a heat source.
  • the coolant is selected from various kinds of fluid for cooling the engine.

Landscapes

  • Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Air-Conditioning For Vehicles (AREA)
  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)
  • Combined Controls Of Internal Combustion Engines (AREA)
US13/039,599 2010-03-03 2011-03-03 Controller for engine cooling system Abandoned US20110214627A1 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
US13/943,818 US9404410B2 (en) 2010-03-03 2013-07-17 Controller for engine cooling system

Applications Claiming Priority (4)

Application Number Priority Date Filing Date Title
JP2010046588A JP2011179460A (ja) 2010-03-03 2010-03-03 エンジン冷却システムの制御装置
JP2010-46588 2010-03-03
JP2010049177A JP5287769B2 (ja) 2010-03-05 2010-03-05 車両用空調装置
JP2010-49177 2010-03-05

Related Child Applications (1)

Application Number Title Priority Date Filing Date
US13/943,818 Division US9404410B2 (en) 2010-03-03 2013-07-17 Controller for engine cooling system

Publications (1)

Publication Number Publication Date
US20110214627A1 true US20110214627A1 (en) 2011-09-08

Family

ID=44503085

Family Applications (2)

Application Number Title Priority Date Filing Date
US13/039,599 Abandoned US20110214627A1 (en) 2010-03-03 2011-03-03 Controller for engine cooling system
US13/943,818 Expired - Fee Related US9404410B2 (en) 2010-03-03 2013-07-17 Controller for engine cooling system

Family Applications After (1)

Application Number Title Priority Date Filing Date
US13/943,818 Expired - Fee Related US9404410B2 (en) 2010-03-03 2013-07-17 Controller for engine cooling system

Country Status (3)

Country Link
US (2) US20110214627A1 (zh)
CN (2) CN103174504B (zh)
DE (1) DE102011004998B4 (zh)

Cited By (33)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090321533A1 (en) * 2008-06-30 2009-12-31 Mark Bigler Variable electric auxiliary heater circuit pump
US20100243215A1 (en) * 2009-03-25 2010-09-30 Ferrari S. P. A. Cooling system for a vehicle with hybrid propulsion
US20110214628A1 (en) * 2010-03-08 2011-09-08 Matthias Honzen Cooling Circuit for an Internal Combustion Engine
US20120305232A1 (en) * 2011-06-01 2012-12-06 Joseph Vogele Ag Construction machine with automatic fan rotational speed regulation
US20130068202A1 (en) * 2010-05-25 2013-03-21 Zoltan Kardos Cooler arrangement for a vehicle powered by a supercharged combustion engine
US20130092108A1 (en) * 2011-10-17 2013-04-18 Ford Global Technologies, Llc Method for Warming an Internal Combustion Engine, and Internal Combustion Engine
US20130255600A1 (en) * 2010-12-24 2013-10-03 Toyota Jidosha Kabushiki Kaisha Vehicle and method for controlling the same
US20130319352A1 (en) * 2012-06-04 2013-12-05 Robert Bosch Gmbh Method for lowering the air temperature of an engine compartment of a vehicle
US20140000536A1 (en) * 2012-06-29 2014-01-02 GM Global Technology Operations LLC Powertrain cooling system with cooling flow modes
US20140148982A1 (en) * 2012-11-29 2014-05-29 GM Global Technology Operations LLC Hybrid thermal system with device-specific control logic
US20140196674A1 (en) * 2013-01-11 2014-07-17 Ford Global Technologies, Llc Liquid-cooled internal combustion engine with liquid-cooled cylinder head and with liquid-cooled cylinder block
US20150066263A1 (en) * 2013-08-31 2015-03-05 Ford Global Technologies, Llc Methods and devices for controlling a vehicle coolant pump
US20150184904A1 (en) * 2013-12-27 2015-07-02 Yanmar Co., Ltd. Engine driven heat pump
US20150183297A1 (en) * 2013-12-27 2015-07-02 Yanmar Co., Ltd. Engine driven heat pump
US20150275742A1 (en) * 2012-12-13 2015-10-01 Bayerische Motoren Werke Aktiengesellschaft Coolant Circuit for an Internal Combustion Engine
US20160109890A1 (en) * 2014-10-21 2016-04-21 Ford Global Technologies, Llc Wax thermostat
US20160115915A1 (en) * 2014-10-22 2016-04-28 Hyundai Motor Company Cooling system provided with intercooler and control method thereof
US20160214487A1 (en) * 2013-08-30 2016-07-28 Autonomous Tractor Corporation Hybrid electric drive system and method
US9404410B2 (en) 2010-03-03 2016-08-02 Denso Corporation Controller for engine cooling system
US20160230642A1 (en) * 2015-02-09 2016-08-11 GM Global Technology Operations LLC Method of controlling a cooling circuit of an internal combustion engine
US20160230639A1 (en) * 2013-09-16 2016-08-11 Avl List Gmbh Cooling system for an internal combustion engine
US20160298522A1 (en) * 2013-12-20 2016-10-13 Scania Cv Ab Cooler arrangement for cooling at least one cylinder of a combustion engine
US20160305309A1 (en) * 2015-04-17 2016-10-20 Toyota Jidosha Kabushiki Kaisha Cooling apparatus for internal combustion engine
US9869232B2 (en) * 2012-06-27 2018-01-16 Ford Global Technologies, Llc Variable-speed pump control for engine coolant system with variable restriction
US9950591B2 (en) 2013-07-26 2018-04-24 Panasonic Intellectual Property Management Co., Ltd. Vehicle air conditioner
US20180245503A1 (en) * 2015-12-17 2018-08-30 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US20180266304A1 (en) * 2016-01-06 2018-09-20 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US10174664B2 (en) 2014-11-12 2019-01-08 Hitachi Automotive Systems, Ltd. Cooling control apparatus for internal combustion engine and cooling control method therefor
US10450941B2 (en) * 2018-01-31 2019-10-22 Ford Global Technologies, Llc Engine cooling system and method
US10508587B2 (en) * 2017-07-28 2019-12-17 GM Global Technology Operations LLC Controlling coolant fluid in a vehicle cooling system using a secondary coolant pump
US11065981B2 (en) * 2018-07-25 2021-07-20 Hyundai Motor Company Air-conditioning apparatus for electric vehicle and method of controlling same
US11485196B2 (en) * 2019-09-11 2022-11-01 Mahle International Gmbh Air conditioning system for a motor vehicle
DE102022132340A1 (de) 2022-12-06 2024-06-06 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Temperieren einer elektrischen Antriebseinheit eines Kraftfahrzeugs, insbesondere eines Kraftwagens

Families Citing this family (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US9828932B2 (en) * 2013-03-08 2017-11-28 GM Global Technology Operations LLC System and method for controlling a cooling system of an engine equipped with a start-stop system
CN104833129B (zh) 2014-02-06 2017-12-19 翰昂汽车零部件有限公司 用于车辆的热泵***
DE102014004009A1 (de) * 2014-03-20 2015-12-03 Daimler Ag Kühlmittelkreislauf zum Kühlen einer Verbrennungskraftmaschine, insbesondere für einen Kraftwagen, sowie Verfahren zum Betreiben eines solchen Kühlmittelkreislaufs
WO2016069257A1 (en) * 2014-10-28 2016-05-06 Borgwarner Inc. A fluid system and method of making and using the same
US9533546B2 (en) * 2015-03-16 2017-01-03 Thunder Power Hong Kong Ltd. Electric vehicle thermal management system
US9550406B2 (en) 2015-03-16 2017-01-24 Thunder Power Hong Kong Ltd. Thermal dissipation system of an electric vehicle
US9533551B2 (en) 2015-03-16 2017-01-03 Thunder Power Hong Kong Ltd. Electric vehicle thermal management system with series and parallel structure
US10202886B1 (en) * 2015-05-02 2019-02-12 Darius Teslovich Engine temperature control system
JP2017002781A (ja) * 2015-06-09 2017-01-05 トヨタ自動車株式会社 内燃機関の制御装置
JP6489223B2 (ja) * 2015-09-15 2019-03-27 株式会社デンソー エンジン制御装置、空調システム、および、空調制御装置に用いるプログラム
CN105971715B (zh) * 2016-07-01 2018-07-06 无锡雨德智能物联网科技有限公司 一种用于发动机的散热装置
DE102016011070A1 (de) 2016-09-14 2018-03-15 Audi Ag Verfahren zum Betreiben einer Antriebseinrichtung sowie entsprechende Antriebseinrichtung
CN107882625B (zh) * 2016-09-29 2020-01-10 郑州宇通客车股份有限公司 一种发动机电子风扇的控制方法及装置
SE540324C2 (en) * 2016-10-28 2018-06-26 Scania Cv Ab A cooling system for cooling a combustion engine and a WHR system
CN108116222A (zh) * 2016-11-29 2018-06-05 长城汽车股份有限公司 冷却***及车辆
CN106988855A (zh) * 2017-05-11 2017-07-28 廖兴池 一种无人机上专用的发动机散热装置
CN109429467A (zh) * 2017-08-22 2019-03-05 浙江创力电子股份有限公司 基站冷却***冷却效率评价方法
JP6806016B2 (ja) * 2017-09-25 2020-12-23 トヨタ自動車株式会社 エンジン冷却装置
CN108327917B (zh) * 2018-04-16 2024-02-23 中电科芜湖通用航空产业技术研究院有限公司 串联式混合动力飞机冷却***
JP7190350B2 (ja) * 2018-12-28 2022-12-15 マーレジャパン株式会社 車両用の熱交換システム
CN112065565B (zh) * 2020-09-15 2021-11-30 奇瑞汽车股份有限公司 节温器总成、冷却***、发动机和汽车

Citations (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4381736A (en) * 1980-04-18 1983-05-03 Toyota Jidosha Kogyo Kabushiki Kaisha Engine cooling system providing mixed or unmixed head and block cooling
US5337704A (en) * 1993-09-29 1994-08-16 Chrysler Corporation Engine cooling system with thermostat coolant flow control between head and block
US20030019442A1 (en) * 2001-07-25 2003-01-30 Toyota Jidosha Kabushiki Kaisha Engine cooling apparatus
US6679201B2 (en) * 2001-06-13 2004-01-20 Aisan Kogyo Kabushiki Kaisha Engine cooling system
US6688263B1 (en) * 1999-11-25 2004-02-10 Honda Giken Kogyo Kabushiki Kaisha System for controlling the temperature of a cylinder wall in an engine
US6688262B2 (en) * 2001-06-21 2004-02-10 Aisan Kogyo Kabushiki Kaisha Engine cooling system
US20040103862A1 (en) * 2002-09-25 2004-06-03 Aidnik David Lee Engine temperature control apparatus and method
US6817321B2 (en) * 2001-10-15 2004-11-16 Nippon Thermostat Co., Ltd. Method for controlling electronically-controlled thermostat
US7325595B2 (en) * 2003-08-19 2008-02-05 Denso Corporation Automotive air conditioning system
US7363804B2 (en) * 1996-12-17 2008-04-29 Denso Corporation Method for detecting malfunction of a cooling system based on detected coolant temperature
US7377237B2 (en) * 2006-09-13 2008-05-27 Cummins Power Generation Inc. Cooling system for hybrid power system
US20090229543A1 (en) * 2005-07-08 2009-09-17 Toyota Jidosha Kabushiki Kaisha Cooling device for engine
US8052066B2 (en) * 2004-05-10 2011-11-08 Toyota Jidosha Kabushiki Kaisha Heating control system for vehicle

Family Cites Families (35)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5793620A (en) * 1980-12-02 1982-06-10 Toyota Motor Corp Cooler for engine
JPS5934472A (ja) * 1982-08-20 1984-02-24 Toyota Motor Corp 吸気通路壁加熱と車室内暖房の関連制御装置
JPS60113017A (ja) * 1983-11-25 1985-06-19 Toyota Motor Corp 二系統冷却式内燃機関の冷却ファンの運転制御方法
JPS6210414A (ja) * 1985-07-05 1987-01-19 Nissan Motor Co Ltd 内燃機関の沸騰冷却装置
JPS62247112A (ja) * 1986-03-28 1987-10-28 Aisin Seiki Co Ltd 内燃機関の冷却系制御装置
FR2615457B1 (fr) * 1987-05-21 1993-06-04 Valeo Installation de chauffage pour vehicule automobile comportant un generateur de chaleur
DE4104093A1 (de) * 1991-02-11 1992-08-13 Behr Gmbh & Co Kuehlanlage fuer ein fahrzeug mit verbrennungsmotor
JPH07150937A (ja) * 1993-11-27 1995-06-13 Honda Motor Co Ltd 火花点火式２サイクルエンジンの冷却装置
JP3175506B2 (ja) * 1994-11-21 2001-06-11 日産自動車株式会社 内燃機関の冷却装置
JP3555269B2 (ja) * 1995-08-31 2004-08-18 株式会社デンソー 車両用冷却水温度制御システム
BR9701062A (pt) * 1997-02-24 1998-11-10 Gen Motors Brasil Ltda Sistema independente de arrefecimento de motores alternativos de combustão interna
DE19910651A1 (de) * 1998-03-13 1999-09-16 Denso Corp Motorkühlvorrichtung
US6178928B1 (en) * 1998-06-17 2001-01-30 Siemens Canada Limited Internal combustion engine total cooling control system
US5901786A (en) * 1998-09-21 1999-05-11 Ford Motor Company Axial fan sandwich cooling module incorporating airflow by-pass features
DE59808921D1 (de) * 1998-12-07 2003-08-07 Ford Global Tech Inc Kühl- und Heizungskreislauf sowie Wärmetauscher für Kraftfahrzeuge mit zusätzlicher Kühlmittel-Heizeinrichtung
DE19857371C2 (de) 1998-12-11 2000-11-23 Trw Automotive Electron & Comp Haltevorrichtung für eine Platte, insbesondere eine Fensterscheibe bei einem Kraftfahrzeug
IT1308421B1 (it) * 1999-03-11 2001-12-17 Fiat Ricerche Sistema di raffreddamento per un motore a combustione interna.
DE10127219A1 (de) * 2001-05-23 2002-11-28 Behr Thermot Tronik Gmbh Kühlanlage für einen Verbrennungsmotor
JP4168638B2 (ja) 2002-02-15 2008-10-22 トヨタ自動車株式会社 ノック指標に基づいて冷却程度が制御される内燃機関
JP3956812B2 (ja) * 2002-09-13 2007-08-08 トヨタ自動車株式会社 エンジンの冷却制御装置及びその冷却制御装置を備えた車両
KR100656594B1 (ko) * 2002-10-24 2006-12-11 현대자동차주식회사 분리 냉각 시스템이 적용되는 엔진의 실린더 헤드와실린더 블럭용 워터 자켓의 구조
JP3906817B2 (ja) * 2003-03-20 2007-04-18 トヨタ自動車株式会社 エンジンの冷却装置
DE10332949A1 (de) * 2003-07-19 2005-02-10 Daimlerchrysler Ag Vorrichtung zum Kühlen und Vorwärmen
JP2005090236A (ja) 2003-09-12 2005-04-07 Mitsubishi Motors Corp 内燃機関の冷却装置
JP4341475B2 (ja) * 2004-06-04 2009-10-07 マツダ株式会社 エンジンの始動装置
KR100836686B1 (ko) * 2004-12-23 2008-06-10 현대자동차주식회사 엔진의 가변 분리냉각 구조
JP2006207448A (ja) * 2005-01-27 2006-08-10 Toyota Motor Corp 車両の制御装置
JP2006216303A (ja) * 2005-02-02 2006-08-17 Denso Corp 発熱機器の冷却構造
JP4327826B2 (ja) * 2006-07-11 2009-09-09 トヨタ自動車株式会社 内燃機関の冷却制御装置
US7717069B2 (en) * 2007-11-15 2010-05-18 Caterpillar Inc. Engine cooling system having two cooling circuits
JP4306782B2 (ja) 2007-11-21 2009-08-05 トヨタ自動車株式会社 車両の冷却制御装置および冷却制御方法
CN101368504B (zh) * 2008-08-13 2011-09-21 奇瑞汽车股份有限公司 一种发动机冷却***
CN101655027A (zh) * 2009-09-08 2010-02-24 奇瑞汽车股份有限公司 一种发动机冷却***及冷却方法
CN103174504B (zh) 2010-03-03 2015-11-18 株式会社电装 用于发动机冷却***的控制器
DE102010044026B4 (de) * 2010-11-17 2013-12-12 Ford Global Technologies, Llc Hybrid Kühlsystem eines Verbrennungsmotors

Patent Citations (14)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4381736A (en) * 1980-04-18 1983-05-03 Toyota Jidosha Kogyo Kabushiki Kaisha Engine cooling system providing mixed or unmixed head and block cooling
US5337704A (en) * 1993-09-29 1994-08-16 Chrysler Corporation Engine cooling system with thermostat coolant flow control between head and block
US7363804B2 (en) * 1996-12-17 2008-04-29 Denso Corporation Method for detecting malfunction of a cooling system based on detected coolant temperature
US7743651B2 (en) * 1996-12-17 2010-06-29 Denso Corporation Method for detecting malfunction of a cooling system based on detected coolant temperature
US6688263B1 (en) * 1999-11-25 2004-02-10 Honda Giken Kogyo Kabushiki Kaisha System for controlling the temperature of a cylinder wall in an engine
US6679201B2 (en) * 2001-06-13 2004-01-20 Aisan Kogyo Kabushiki Kaisha Engine cooling system
US6688262B2 (en) * 2001-06-21 2004-02-10 Aisan Kogyo Kabushiki Kaisha Engine cooling system
US20030019442A1 (en) * 2001-07-25 2003-01-30 Toyota Jidosha Kabushiki Kaisha Engine cooling apparatus
US6817321B2 (en) * 2001-10-15 2004-11-16 Nippon Thermostat Co., Ltd. Method for controlling electronically-controlled thermostat
US20040103862A1 (en) * 2002-09-25 2004-06-03 Aidnik David Lee Engine temperature control apparatus and method
US7325595B2 (en) * 2003-08-19 2008-02-05 Denso Corporation Automotive air conditioning system
US8052066B2 (en) * 2004-05-10 2011-11-08 Toyota Jidosha Kabushiki Kaisha Heating control system for vehicle
US20090229543A1 (en) * 2005-07-08 2009-09-17 Toyota Jidosha Kabushiki Kaisha Cooling device for engine
US7377237B2 (en) * 2006-09-13 2008-05-27 Cummins Power Generation Inc. Cooling system for hybrid power system

Cited By (59)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US20090321533A1 (en) * 2008-06-30 2009-12-31 Mark Bigler Variable electric auxiliary heater circuit pump
US8740104B2 (en) * 2008-06-30 2014-06-03 Chrysler Group Llc Variable electric auxiliary heater circuit pump
US20100243215A1 (en) * 2009-03-25 2010-09-30 Ferrari S. P. A. Cooling system for a vehicle with hybrid propulsion
US8281884B2 (en) * 2009-03-25 2012-10-09 Ferrari S.P.A. Cooling system for a vehicle with hybrid propulsion
US9404410B2 (en) 2010-03-03 2016-08-02 Denso Corporation Controller for engine cooling system
US20110214628A1 (en) * 2010-03-08 2011-09-08 Matthias Honzen Cooling Circuit for an Internal Combustion Engine
US8464669B2 (en) * 2010-03-08 2013-06-18 Audi Ag Cooling circuit for an internal combustion engine
US20130068202A1 (en) * 2010-05-25 2013-03-21 Zoltan Kardos Cooler arrangement for a vehicle powered by a supercharged combustion engine
US8584457B2 (en) * 2010-05-25 2013-11-19 Scania Cv Ab Cooler arrangement for a vehicle powered by a supercharged combustion engine
US8991338B2 (en) * 2010-12-24 2015-03-31 Toyota Jidosha Kabushiki Kaisha Vehicle and method for controlling the same
US20130255600A1 (en) * 2010-12-24 2013-10-03 Toyota Jidosha Kabushiki Kaisha Vehicle and method for controlling the same
US20120305232A1 (en) * 2011-06-01 2012-12-06 Joseph Vogele Ag Construction machine with automatic fan rotational speed regulation
US9376954B2 (en) * 2011-06-01 2016-06-28 Joseph Vogele Ag Construction machine with automatic fan rotational speed regulation
US9004020B2 (en) * 2011-10-17 2015-04-14 Ford Global Technologies, Llc Method for warming an internal combustion engine, and internal combustion engine
US20130092108A1 (en) * 2011-10-17 2013-04-18 Ford Global Technologies, Llc Method for Warming an Internal Combustion Engine, and Internal Combustion Engine
US9976471B2 (en) 2011-10-17 2018-05-22 Ford Global Technologies, Llc Method for warming an internal combustion engine, and internal combustion engine
US20130319352A1 (en) * 2012-06-04 2013-12-05 Robert Bosch Gmbh Method for lowering the air temperature of an engine compartment of a vehicle
US9869232B2 (en) * 2012-06-27 2018-01-16 Ford Global Technologies, Llc Variable-speed pump control for engine coolant system with variable restriction
US8978596B2 (en) * 2012-06-29 2015-03-17 GM Global Technology Operations LLC Powertrain cooling system with cooling flow modes
US20140000536A1 (en) * 2012-06-29 2014-01-02 GM Global Technology Operations LLC Powertrain cooling system with cooling flow modes
US8948946B2 (en) * 2012-11-29 2015-02-03 GM Global Technology Operations LLC Hybrid thermal system with device-specific control logic
US20140148982A1 (en) * 2012-11-29 2014-05-29 GM Global Technology Operations LLC Hybrid thermal system with device-specific control logic
US10030572B2 (en) * 2012-12-13 2018-07-24 Bayerische Motoren Werke Aktiengesellschaft Coolant circuit for an internal combustion engine
US20150275742A1 (en) * 2012-12-13 2015-10-01 Bayerische Motoren Werke Aktiengesellschaft Coolant Circuit for an Internal Combustion Engine
US9243545B2 (en) * 2013-01-11 2016-01-26 Ford Global Technologies, Llc Liquid-cooled internal combustion engine with liquid-cooled cylinder head and with liquid-cooled cylinder block
US20140196674A1 (en) * 2013-01-11 2014-07-17 Ford Global Technologies, Llc Liquid-cooled internal combustion engine with liquid-cooled cylinder head and with liquid-cooled cylinder block
US9950591B2 (en) 2013-07-26 2018-04-24 Panasonic Intellectual Property Management Co., Ltd. Vehicle air conditioner
US9956881B2 (en) * 2013-08-30 2018-05-01 Autonomous Tractor Corporation Hybrid electric drive system and method
US20160214487A1 (en) * 2013-08-30 2016-07-28 Autonomous Tractor Corporation Hybrid electric drive system and method
US9188053B2 (en) * 2013-08-31 2015-11-17 Ford Global Technologies, Llc Methods and devices for controlling a vehicle coolant pump
US20150066263A1 (en) * 2013-08-31 2015-03-05 Ford Global Technologies, Llc Methods and devices for controlling a vehicle coolant pump
US20160230639A1 (en) * 2013-09-16 2016-08-11 Avl List Gmbh Cooling system for an internal combustion engine
US10858980B2 (en) * 2013-09-16 2020-12-08 Avl List Gmbh Cooling system for an internal combustion engine
US20160298522A1 (en) * 2013-12-20 2016-10-13 Scania Cv Ab Cooler arrangement for cooling at least one cylinder of a combustion engine
US10634037B2 (en) * 2013-12-20 2020-04-28 Scania Cv Ab Cooler arrangement for cooling at least one cylinder of a combustion engine
US10047993B2 (en) * 2013-12-27 2018-08-14 Yanmar Co., Ltd. Engine driven heat pump
US9862252B2 (en) * 2013-12-27 2018-01-09 Yanmar Co., Ltd. Engine driven heat pump
US20150184904A1 (en) * 2013-12-27 2015-07-02 Yanmar Co., Ltd. Engine driven heat pump
US20150183297A1 (en) * 2013-12-27 2015-07-02 Yanmar Co., Ltd. Engine driven heat pump
CN105525978A (zh) * 2014-10-21 2016-04-27 福特环球技术公司 石蜡恒温器
RU2704710C2 (ru) * 2014-10-21 2019-10-30 Форд Глобал Текнолоджиз, Ллк Восковой термостат
US20160109890A1 (en) * 2014-10-21 2016-04-21 Ford Global Technologies, Llc Wax thermostat
US10866603B2 (en) * 2014-10-21 2020-12-15 Ford Global Technologies, Llc Wax thermostat
US20160115915A1 (en) * 2014-10-22 2016-04-28 Hyundai Motor Company Cooling system provided with intercooler and control method thereof
US9957926B2 (en) * 2014-10-22 2018-05-01 Hyundai Motor Company Cooling system provided with intercooler and control method thereof
US10174664B2 (en) 2014-11-12 2019-01-08 Hitachi Automotive Systems, Ltd. Cooling control apparatus for internal combustion engine and cooling control method therefor
US9976472B2 (en) * 2015-02-09 2018-05-22 GM Global Technology Operations LLC Method of controlling a cooling circuit of an internal combustion engine
US20160230642A1 (en) * 2015-02-09 2016-08-11 GM Global Technology Operations LLC Method of controlling a cooling circuit of an internal combustion engine
US20160305309A1 (en) * 2015-04-17 2016-10-20 Toyota Jidosha Kabushiki Kaisha Cooling apparatus for internal combustion engine
US20180245503A1 (en) * 2015-12-17 2018-08-30 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US10371041B2 (en) * 2015-12-17 2019-08-06 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US10605150B2 (en) * 2016-01-06 2020-03-31 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US20180266304A1 (en) * 2016-01-06 2018-09-20 Hitachi Automotive Systems, Ltd. Cooling device for internal combustion engine of vehicle and control method thereof
US10508587B2 (en) * 2017-07-28 2019-12-17 GM Global Technology Operations LLC Controlling coolant fluid in a vehicle cooling system using a secondary coolant pump
US10450941B2 (en) * 2018-01-31 2019-10-22 Ford Global Technologies, Llc Engine cooling system and method
US11065981B2 (en) * 2018-07-25 2021-07-20 Hyundai Motor Company Air-conditioning apparatus for electric vehicle and method of controlling same
US11485196B2 (en) * 2019-09-11 2022-11-01 Mahle International Gmbh Air conditioning system for a motor vehicle
DE102022132340A1 (de) 2022-12-06 2024-06-06 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum Temperieren einer elektrischen Antriebseinheit eines Kraftfahrzeugs, insbesondere eines Kraftwagens
WO2024120730A1 (de) 2022-12-06 2024-06-13 Bayerische Motoren Werke Aktiengesellschaft Verfahren zum temperieren einer elektrischen antriebseinheit eines kraftfahrzeugs, insbesondere eines kraftwagens

Also Published As

Publication number Publication date
CN103174504A (zh) 2013-06-26
US9404410B2 (en) 2016-08-02
CN102191991A (zh) 2011-09-21
DE102011004998B4 (de) 2017-12-14
CN103174504B (zh) 2015-11-18
DE102011004998A1 (de) 2011-09-08
US20130298851A1 (en) 2013-11-14

Similar Documents

Publication Publication Date Title
US9404410B2 (en) Controller for engine cooling system
EP1475532B1 (en) Thermoelectric generating device
US10371041B2 (en) Cooling device for internal combustion engine of vehicle and control method thereof
US10519875B2 (en) Diagnostic device
EP1491726B1 (en) Waste heat recovery system of heat source, with rankine cycle
US10753268B2 (en) Intercooler cooling apparatus and method for controlling transmission fluid and air conditioner refrigerant temperature
JP4627210B2 (ja) 排気熱回収装置およびその制御方法
US10605150B2 (en) Cooling device for internal combustion engine of vehicle and control method thereof
US10549605B2 (en) Heating system and method for heating a vehicle interior of a vehicle having an internal combustion engine
US20160363038A1 (en) Heat exchange apparatus of vehicle
KR102217930B1 (ko) 하이브리드 차량
JP5857899B2 (ja) 車載内燃機関の冷却システム
EP3428419B1 (en) Control apparatus of heat exchanging system
JP6358424B2 (ja) 吸気温度制御システム
US20200362746A1 (en) Control method for integrated thermal management system of vehicle
CN109228825B (zh) 热交换***的控制装置
US11597375B2 (en) Vehicle control device
JP2014141899A (ja) 車載内燃機関の冷却装置
US10696140B2 (en) Air conditioner for vehicle
CN109228826B (zh) 热交换***的控制装置
US10830122B2 (en) Intake and charge air cooling system
JPWO2016189741A1 (ja) 車両用空調システム
WO2019138582A1 (ja) 冷却システム及び冷却システムの制御方法
US11280251B2 (en) In-vehicle cooling system and method for controlling the same
CN109228819B (zh) 热交换***的控制装置

Legal Events

Date Code Title Description
AS Assignment

Owner name: DENSO CORPORATION, JAPAN

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:NISHIKAWA, MICHIO;KAKEHASHI, NOBUHARU;OTA, KOJI;REEL/FRAME:026147/0159

Effective date: 20110228

STCB Information on status: application discontinuation

Free format text: ABANDONED -- FAILURE TO RESPOND TO AN OFFICE ACTION