WO2018123289A1 - Module de commande - Google Patents

Module de commande Download PDF

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Publication number
WO2018123289A1
WO2018123289A1 PCT/JP2017/040447 JP2017040447W WO2018123289A1 WO 2018123289 A1 WO2018123289 A1 WO 2018123289A1 JP 2017040447 W JP2017040447 W JP 2017040447W WO 2018123289 A1 WO2018123289 A1 WO 2018123289A1
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WO
WIPO (PCT)
Prior art keywords
degree
control
refrigerant
superheat
heat exchanger
Prior art date
Application number
PCT/JP2017/040447
Other languages
English (en)
Japanese (ja)
Inventor
裕之 坂根
Original Assignee
株式会社デンソー
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 株式会社デンソー filed Critical 株式会社デンソー
Priority to DE112017006541.0T priority Critical patent/DE112017006541T5/de
Publication of WO2018123289A1 publication Critical patent/WO2018123289A1/fr

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    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/08—Air inlets for cooling; Shutters or blinds therefor
    • B60K11/085—Air inlets for cooling; Shutters or blinds therefor with adjustable shutters or blinds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B49/00—Arrangement or mounting of control or safety devices
    • F25B49/02—Arrangement or mounting of control or safety devices for compression type machines, plants or systems
    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60K—ARRANGEMENT OR MOUNTING OF PROPULSION UNITS OR OF TRANSMISSIONS IN VEHICLES; ARRANGEMENT OR MOUNTING OF PLURAL DIVERSE PRIME-MOVERS IN VEHICLES; AUXILIARY DRIVES FOR VEHICLES; INSTRUMENTATION OR DASHBOARDS FOR VEHICLES; ARRANGEMENTS IN CONNECTION WITH COOLING, AIR INTAKE, GAS EXHAUST OR FUEL SUPPLY OF PROPULSION UNITS IN VEHICLES
    • B60K11/00—Arrangement in connection with cooling of propulsion units
    • B60K11/02—Arrangement in connection with cooling of propulsion units with liquid cooling
    • B60K11/04—Arrangement or mounting of radiators, radiator shutters, or radiator blinds
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2500/00—Problems to be solved
    • F25B2500/19—Calculation of parameters
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2600/00—Control issues
    • F25B2600/11—Fan speed control
    • F25B2600/112—Fan speed control of evaporator fans
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/19—Pressures
    • F25B2700/197—Pressures of the evaporator
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B2700/00—Sensing or detecting of parameters; Sensors therefor
    • F25B2700/21—Temperatures
    • F25B2700/2117—Temperatures of an evaporator
    • F25B2700/21175—Temperatures of an evaporator of the refrigerant at the outlet of the evaporator
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
    • Y02T10/00—Road transport of goods or passengers
    • Y02T10/80—Technologies aiming to reduce greenhouse gasses emissions common to all road transportation technologies
    • Y02T10/88—Optimized components or subsystems, e.g. lighting, actively controlled glasses

Definitions

  • the present disclosure relates to a control module that controls a heat exchange unit provided in a vehicle.
  • the vehicle is equipped with multiple heat exchangers.
  • a heat exchanger includes an evaporator that is a part of an air conditioner configured as a refrigeration cycle (see, for example, Patent Document 1 below).
  • a heat exchanger provided in a vehicle is often unitized together with a device such as an electric expansion valve that adjusts the flow of refrigerant, and the whole is often configured as one heat exchange unit.
  • the heat exchange unit is arranged at a front portion of the vehicle so that air flowing in from the front grille of the vehicle passes through the heat exchanger.
  • the opening degree of the electric expansion valve is adjusted so that the degree of superheat of the refrigerant at the outlet portion of the evaporator matches a predetermined target value.
  • This disclosure is intended to provide a control module capable of quickly changing the degree of superheat of the refrigerant so that heat exchange in the heat exchange unit is appropriately performed.
  • the control module is a control module that controls a heat exchange unit provided in a vehicle.
  • the heat exchange unit described above has a flow rate of a heat exchanger that evaporates the refrigerant inside by performing heat exchange between the air-conditioning refrigerant and air, and air that flows from the front grill of the vehicle and passes through the heat exchanger.
  • an air control device for adjusting the air pressure.
  • the control module includes a control unit that controls the operation of the air control device, and an acquisition unit that acquires the degree of superheat of the refrigerant discharged from the heat exchanger. The control unit controls the operation of the air control device based on the degree of superheat acquired by the acquisition unit.
  • the operation of the air control device is controlled based on the degree of superheat of the refrigerant discharged from the heat exchanger, thereby adjusting the degree of superheat.
  • the air control device is, for example, a shutter device.
  • control for changing the flow rate of the air passing through the heat exchanger may be performed independently or may be performed together with the control for changing the opening degree of the electric expansion valve.
  • control module capable of quickly changing the degree of superheat of the refrigerant so that heat exchange in the heat exchange unit is appropriately performed.
  • FIG. 1 is a diagram schematically illustrating a state in which a heat exchange unit including a control module according to the first embodiment is mounted on a vehicle.
  • FIG. 2 is a diagram schematically illustrating the heat exchange unit of FIG. 1 as viewed from above.
  • FIG. 3 is a diagram showing an overall configuration of a vehicle air conditioner mounted on the vehicle.
  • FIG. 4 is a diagram illustrating the configuration of the outdoor heat exchanger and the electric expansion valve in the vehicle air conditioner of FIG. 3.
  • FIG. 5 is a block diagram schematically showing the heat exchange unit and the surrounding configuration.
  • FIG. 6 is a block diagram schematically showing the internal configuration of the control module.
  • FIG. 7 is a flowchart showing a flow of processing executed by the control module.
  • FIG. 8 is a graph schematically showing a temporal change in the degree of superheat.
  • FIG. 9 is a flowchart showing a flow of processing executed by the control module according to the second embodiment.
  • FIG. 10 is a diagram illustrating a correspondence relationship between the acquired degree of superheat and the target opening degree of the electric expansion valve.
  • FIG. 11 is a diagram illustrating a correspondence relationship between the acquired degree of superheat and the target opening degree of the shutter device.
  • FIG. 12 is a flowchart showing a flow of processing executed by the control module according to the third embodiment.
  • FIG. 13 is a diagram depicting the contents of the processing shown in FIG. 12 as a block diagram.
  • FIG. 14 is a flowchart showing a flow of processing executed by the control module according to the fourth embodiment.
  • FIG. 15 is a diagram depicting the contents of the processing shown in FIG. 14 as a block diagram.
  • the control module 100 is configured as a device for controlling the heat exchange unit 10 provided in the vehicle 50.
  • the configuration of the heat exchange unit 10 will be described first.
  • the heat exchange unit 10 is a unit obtained by combining a plurality of heat exchangers (outdoor heat exchanger 740 and radiator 31) and devices (such as the shutter device 20).
  • the heat exchange unit 10 is installed in the engine room ER of the vehicle 50.
  • the structure provided with a some heat exchanger like this embodiment may be sufficient as the heat exchange unit 10
  • the structure provided with only one heat exchanger may be sufficient as it.
  • the outdoor heat exchanger 740 is a part of a vehicle air conditioner 70 (see FIG. 3) described later.
  • the outdoor heat exchanger 740 is heat for exchanging heat between the air introduced into the engine room ER from the opening OP of the front grill GR and the air conditioning refrigerant circulating in the vehicle air conditioner 70. It is configured as an exchanger.
  • the radiator 31 is a heat exchanger for cooling the cooling water circulating through the engine 51, which is an internal combustion engine, by heat exchange with air.
  • the radiator 31 is disposed at a position on the rear side of the outdoor heat exchanger 740. For this reason, the air introduced into the engine room ER from the opening OP of the front grill GR is subjected to heat exchange with the refrigerant through the outdoor heat exchanger 740 as described above, and then passes through the radiator 31. It is used for heat exchange with cooling water.
  • the heat exchange unit 10 includes a shutter device 20, an electric fan 40, a shroud 43, an electric expansion valve 730, and a hot water valve 32. .
  • the shutter device 20 is a device for adjusting the flow rate of air introduced into the engine room ER from the opening OP, thereby adjusting the flow rate of air passing through the outdoor heat exchanger 740 and the like.
  • Such a shutter device 20 is a so-called “grill shutter”.
  • the shutter device 20 includes a shutter blade 21 and a shutter actuator 22.
  • a plurality of the shutter blades 21 are arranged in a line at a position on the front side of the outdoor heat exchanger 740.
  • opening degree of the shutter device 20 When the shutter blade 21 rotates and its opening degree (hereinafter referred to as “opening degree of the shutter device 20”) changes, the flow rate of the air passing through the shutter device 20 changes, and the outdoor The flow rate of air passing through each of the heat exchanger 740 and the radiator 31 changes.
  • the shutter actuator 22 is an electric drive device for rotating the shutter blade 21 and adjusting its opening degree.
  • the shutter actuator 22 is provided in the vicinity of the shutter blade 21.
  • the operation of the shutter actuator 22 is controlled by the control module 100 described later.
  • the shutter device 20 adjusts the flow rate of air passing by changing the opening thereof, and adjusts the flow rate of air flowing from the front grill GR and passing through the outdoor heat exchanger 740 and the radiator 31. It is configured as a device for. Such a shutter device 20 corresponds to the “air control device” in the present embodiment.
  • the electric fan 40 is an electric fan for creating a flow of air that passes through the outdoor heat exchanger 740 and the radiator 31.
  • the electric fan 40 is arranged at a position on the rear side of the radiator 31.
  • the electric fan 40 includes a rotating blade 41 for creating an air flow and a fan motor 42 that is a rotating electric machine for rotating the rotating blade 41.
  • a fan motor 42 that is a rotating electric machine for rotating the rotating blade 41.
  • the electric fan 40 includes a sensor (not shown) for measuring the rotation speed of the rotary blade 41 per unit time. The number of rotations measured by the sensor is transmitted to the control module 100.
  • the shroud 43 is a member provided to cover the periphery of the electric fan 40 from the rear side. The air drawn by the electric fan 40 is efficiently guided to the outdoor heat exchanger 740 and the radiator 31 by the shroud 43.
  • the electric expansion valve 730 is a device that forms part of the vehicle air conditioner 70 together with the outdoor heat exchanger 740. As will be described later, the electric expansion valve 730 functions as an expansion valve that reduces the pressure of the refrigerant in the refrigeration cycle. The opening degree of the electric expansion valve 730 is controlled by the control module 100. The electric expansion valve 730 adjusts the flow of the refrigerant that circulates along the path passing through the outdoor heat exchanger 740. Such an electric expansion valve 730 corresponds to the “refrigerant control device” in the present embodiment.
  • the hot water valve 32 is an electric on-off valve provided in the middle of a flow path (not shown) through which cooling water circulates between the radiator 31 and the engine 51.
  • the hot water valve 32 is provided at a position adjacent to the radiator 31. When the hot water valve 32 is closed, the supply of cooling water to the radiator 31 is stopped. The operation of the hot water valve 32 is controlled by the control module 100.
  • the configuration of the vehicle air conditioner 70 will be described with reference to FIG.
  • the vehicle air conditioner 70 is configured as a refrigeration cycle in which refrigerant circulates.
  • the vehicle air conditioner 70 includes a refrigerant flow path 710, a compressor 720, an electric expansion valve 750, an indoor heat exchanger 760, an electric expansion valve 730, and an outdoor heat exchanger 740.
  • a part of the vehicle air conditioner 70 (outdoor heat exchanger 740 etc.) is arranged in the engine room ER of the vehicle 50, and the other part (indoor heat exchanger 760 etc.). ) Is disposed in the cabin IR of the vehicle 50.
  • the refrigerant flow path 710 is a pipe arranged in an annular shape to circulate the refrigerant. All of the compressors 720 and the like described below are arranged along the refrigerant flow path 710.
  • the compressor 720 is a device for pumping the refrigerant and circulating it in the refrigerant flow path 710.
  • the compressor 720 is being driven, the refrigerant that has been compressed in the compressor 720 and becomes high temperature and pressure is sent out toward the electric expansion valve 750 side.
  • the electric expansion valve 750 is provided at a position downstream of the compressor 720 in the refrigerant flow path 710.
  • the electric expansion valve 750 reduces the pressure of the refrigerant passing therethrough by reducing the flow passage cross-sectional area of the refrigerant flow passage 710 at the position.
  • the electric expansion valve 750 operates a valve body (not shown) by an electric actuator (not shown) and changes its opening degree.
  • a bypass flow path 751 for flowing the refrigerant so as to bypass the electric expansion valve 750 is provided at a position near the electric expansion valve 750.
  • An electromagnetic on-off valve 752 is provided in the middle of the bypass flow path 751.
  • the electromagnetic open / close valve 752 When the electromagnetic open / close valve 752 is in the closed state, the refrigerant circulates through the refrigerant flow path 710 through a path passing through the electric expansion valve 750.
  • the electromagnetic on-off valve 752 When the electromagnetic on-off valve 752 is in the open state, the refrigerant hardly circulates through the electric expansion valve 750 and circulates through the refrigerant flow path 710 along a path passing through the bypass flow path 751.
  • the indoor heat exchanger 760 is provided at a position downstream of the electric expansion valve 750 in the refrigerant flow path 710.
  • the indoor heat exchanger 760 is a heat exchanger for exchanging heat between the air blown into the passenger compartment IR and the refrigerant circulating in the refrigerant flow path 710.
  • the vehicle air conditioner 70 performs air conditioning in the passenger compartment IR by heating or cooling air in the indoor heat exchanger 760.
  • the electric expansion valve 730 forms a part of the heat exchange unit 10 as described above, and is provided in the refrigerant channel 710 at a position downstream of the indoor heat exchanger 760.
  • the electric expansion valve 730 reduces the pressure of the refrigerant passing therethrough by reducing the flow passage cross-sectional area of the refrigerant flow passage 710 at the position.
  • the electric expansion valve 730 operates a valve body (not shown) by an electric actuator 730M (not shown in FIG. 3, see FIG. 4), and changes its opening degree.
  • a bypass flow path 731 for flowing the refrigerant so as to bypass the electric expansion valve 730 is provided at a position near the electric expansion valve 730.
  • An electromagnetic on-off valve 732 is provided in the middle of the bypass flow path 731.
  • the electromagnetic on-off valve 732 When the electromagnetic on-off valve 732 is in the closed state, the refrigerant circulates through the refrigerant flow path 710 through a path that passes through the electric expansion valve 730.
  • the electromagnetic open / close valve 732 When the electromagnetic open / close valve 732 is in the open state, the refrigerant hardly circulates through the electric expansion valve 730 and circulates through the refrigerant flow path 710 through a path passing through the bypass flow path 731.
  • the outdoor heat exchanger 740 is a part of the heat exchange unit 10 as described above.
  • the outdoor heat exchanger 740 is provided at a position downstream of the electric expansion valve 730 in the refrigerant flow path 710 and upstream of the compressor 720. A specific configuration of the outdoor heat exchanger 740 will be described later.
  • a pressure sensor 61 and a temperature sensor 62 are provided in a portion of the refrigerant flow path 710 downstream of the outdoor heat exchanger 740, specifically, a portion through which the refrigerant immediately after being discharged from the outdoor heat exchanger 740 passes. And are provided.
  • the pressure sensor 61 is a sensor for measuring the pressure of the refrigerant discharged from the outdoor heat exchanger 740. The refrigerant pressure measured by the pressure sensor 61 is transmitted to the control module 100.
  • the temperature sensor 62 is a sensor for measuring the temperature of the refrigerant discharged from the outdoor heat exchanger 740. The refrigerant temperature measured by the temperature sensor 62 is transmitted to the control module 100.
  • a wind speed sensor 63 for measuring the wind speed of the air passing through the outdoor heat exchanger 740 is provided.
  • the wind speed measured by the wind speed sensor 63 is transmitted to the control module 100.
  • the electromagnetic open / close valve 732 When the vehicle interior IR is heated by the vehicle air conditioner 70, the electromagnetic open / close valve 732 is switched to the closed state, and the electromagnetic open / close valve 752 is switched to the open state.
  • the refrigerant circulates through the refrigerant flow path 710 along a path that passes through the electric expansion valve 730, and reduces its temperature and pressure when passing through the electric expansion valve 730. That is, when the interior of the passenger compartment IR is heated, the electric expansion valve 730 functions as an “expansion valve” of the refrigeration cycle.
  • the low-temperature and low-pressure refrigerant that has passed through the electric expansion valve 730 is supplied to the outdoor heat exchanger 740.
  • the outdoor heat exchanger 740 heat is absorbed from the air by the low-temperature refrigerant, whereby the refrigerant evaporates inside. That is, when the interior of the passenger compartment IR is heated, the outdoor heat exchanger 740 functions as an “evaporator” of the refrigeration cycle.
  • the refrigerant that has passed through the outdoor heat exchanger 740 is compressed by the compressor 720, and is sent downstream with its temperature and pressure increased.
  • the high-temperature and high-pressure refrigerant is supplied to the indoor heat exchanger 760 through the bypass channel 751.
  • the indoor heat exchanger 760 In the indoor heat exchanger 760, heat is released from the refrigerant to the air, thereby condensing the refrigerant inside. That is, when the interior of the passenger compartment IR is heated, the indoor heat exchanger 760 functions as a “condenser” for the refrigeration cycle. After the temperature of the air is increased by heat exchange in the indoor heat exchanger 760, the air is blown into the passenger compartment IR as conditioned air.
  • the refrigerant that has passed through the indoor heat exchanger 760 passes through the refrigerant flow path 710 and reaches the electric expansion valve 730 again.
  • coolant circulates as mentioned above when the inside of vehicle interior IR is performed is shown by the some arrow.
  • the electromagnetic on-off valve 732 When the vehicle interior IR is cooled by the vehicle air conditioner 70, the electromagnetic on-off valve 732 is switched to the open state, and the electromagnetic on-off valve 752 is switched to the closed state. In this state, the refrigerant circulating in the refrigerant flow path 710 flows through the electric expansion valve 730 while passing through the electric expansion valve 750. The refrigerant reduces its temperature and pressure when passing through the electric expansion valve 750. In other words, when the passenger compartment IR is cooled, the electric expansion valve 750 functions as an “expansion valve” of the refrigeration cycle.
  • the low-temperature and low-pressure refrigerant that has passed through the electric expansion valve 730 is supplied to the indoor heat exchanger 760.
  • the indoor heat exchanger 760 heat is absorbed from the air by the low-temperature refrigerant, whereby the refrigerant evaporates inside. That is, when the passenger compartment IR is cooled, the indoor heat exchanger 760 functions as an “evaporator” of the refrigeration cycle.
  • the outdoor heat exchanger 740 heat is radiated from the refrigerant to the air, thereby condensing the refrigerant inside. That is, when the passenger compartment IR is heated, the outdoor heat exchanger 740 functions as a “condenser” for the refrigeration cycle. At this time, the refrigerant flow path is changed in advance by a pipe, a switching valve, or the like (not shown) so that the refrigerant is compressed by the compressor 720 not on the downstream side of the outdoor heat exchanger 740 but on the upstream side. It is good also as a structure.
  • the outdoor heat exchanger 740 includes a pair of tanks 741 and 742 and a core portion 743 disposed therebetween.
  • Each of the tanks 741 and 742 is an elongated container formed to extend in the vertical direction.
  • the refrigerant circulating in the refrigerant flow path 710 is temporarily stored.
  • the core part 743 is a part where heat is exchanged between the refrigerant and air in the outdoor heat exchanger 740.
  • a plurality of tubes and fins are arranged in the core portion 743.
  • the tube is, for example, a tube having a flat cross section, and a flow path through which the refrigerant passes is formed in the tube.
  • Each of the plurality of tubes connects between the tank 741 and the tank 742, and is stacked up and down with the main surfaces facing each other.
  • the fins are formed by bending a metal plate into a wave shape, and are arranged between the stacked tubes.
  • the top of each of the undulating fins is in contact with the outer surface of the tube and brazed. For this reason, the heat of the air passing through the outdoor heat exchanger 740 during heating is not only transmitted to the refrigerant via the tube, but also transmitted to the refrigerant via the fins and the tube. That is, the contact area with the air is increased by the fins, and heat exchange between the refrigerant and the air is performed efficiently.
  • adopted as a structure of the core part 743 which has the above fins and tubes it abbreviate
  • the internal spaces of the tank 741 and the tank 742 are partitioned so as to be divided up and down by a separator (not shown).
  • the refrigerant passing through the outdoor heat exchanger 740 is used for heat exchange in the core portion 743 while going back and forth between the tank 741 and the tank 742 a plurality of times.
  • a modulator tank 770 is provided on the side of the tank 741 (the side opposite to the core portion 743).
  • the modulator tank 770 is an elongated container formed so as to extend in the vertical direction, and is arranged in parallel with the tank 741.
  • the modulator tank 770 and the tank 741 are connected by connection pipes 771, 772, and 773.
  • the refrigerant passing through the outdoor heat exchanger 740 goes back and forth between the tank 741 and the tank 742 a plurality of times through the modulator tank 770 from the connection pipes 771, 772, and 773.
  • the modulator tank 770 stores a liquid phase refrigerant.
  • the refrigerant flowing in the gas-liquid mixed state is in a state where the gas and liquid are separated when passing through the modulator tank 770.
  • the electric actuator 730M of the electric expansion valve 730 is attached to the upper end of the modulator tank 770. Thereby, the electric expansion valve 730 and the modulator tank 770 are integrated.
  • a valve body (not shown) for reducing the cross-sectional area of the flow path in the electric expansion valve 730 is provided at a position directly below the electric actuator 730M, and is disposed inside the modulator tank 770.
  • the electric actuator 730M is provided with a circuit board BD1 for operating the electric actuator 730M.
  • the components of the control module 100 are also arranged on the circuit board BD1. That is, the control module 100 according to the present embodiment is configured integrally with the electric expansion valve 730 that is a refrigerant control device.
  • the heat exchange unit 10 including the control module 100 and the surrounding configuration will be described with reference to FIG. As already described, the heat exchange unit 10 is entirely disposed in the engine room ER of the vehicle 50.
  • a plurality of sensors necessary for controlling the flow of the three fluids (refrigerant, cooling water, air) in the heat exchange unit 10 are arranged.
  • a sensor include an opening sensor that measures the opening of the shutter device 20 in addition to the pressure sensor 61 and the temperature sensor 62 described above.
  • the value measured by each sensor is input to the control module 100 as an electrical signal (detection signal).
  • these multiple sensors are depicted as a single block labeled 60.
  • the plurality of sensors are collectively referred to as “sensor 60”.
  • an engine ECU 200 and an air conditioning ECU 300 are arranged in the passenger compartment IR of the vehicle 50. These are all configured as a computer system having a CPU, a ROM, a RAM, a communication interface, and the like.
  • the engine ECU 200 is a control device for controlling the engine 51.
  • the engine ECU 200 adjusts the flow rate of the cooling water circulated between the engine 51 and the radiator 31, controls the operation of the hot water valve 32, adjusts the opening degree of the shutter device 20, and adjusts the rotational speed of the electric fan 40. Do.
  • a part of the control performed by the engine ECU 200 (for example, the operation control of the shutter actuator 22) is performed via the control module 100.
  • the control module 100 receives a control signal transmitted from the engine ECU 200, and controls operations of various devices (such as the shutter actuator 22) based on the control signal.
  • various devices such as the shutter actuator 22
  • the control module 100 does not always control the operation of various devices according to the control signal, but may control the operation of various devices according to its own judgment.
  • the air conditioning ECU 300 is a control device for controlling the vehicle air conditioner 70.
  • the air conditioning ECU 300 appropriately performs air conditioning in the passenger compartment IR by controlling the operations of various devices (such as the electric expansion valve 730) that constitute the vehicle air conditioner 70.
  • a part of the control performed by the air conditioning ECU 300 (for example, operation control of the electric expansion valve 730) is performed via the control module 100.
  • the control module 100 receives a control signal transmitted from the air conditioning ECU 300, and performs operation control of various devices (such as the electric expansion valve 730) based on the control signal.
  • various devices such as the electric expansion valve 730
  • the control module 100 does not always control the operation of various devices according to the control signal, but may control the operation of various devices according to its own judgment.
  • the vehicle 50 is provided with a plurality of power supply systems for supplying power to various devices. As shown in FIG. 5, the control module 100 is supplied with power from the power supply system PL1, the engine ECU 200 is supplied with power from the power supply system PL2, and the air conditioning ECU 300 is supplied with power from the power supply system PL3. Power is being supplied.
  • the power supply system PL1 is a power supply system to which power from a battery (not shown) provided in the vehicle 50 is directly supplied. Therefore, regardless of whether an ignition switch (not shown) of the vehicle 50 is on or off, the control module 100 is always supplied with power from the power supply system PL1.
  • the power supply system PL2 is a power supply system to which power from an alternator (not shown) provided in the vehicle 50 is supplied. For this reason, when the ignition switch of vehicle 50 is turned on and engine 51 is operating, electric power from power supply system PL2 is supplied to engine ECU 200. On the other hand, when the ignition switch of vehicle 50 is turned off and engine 51 is stopped, electric power from power supply system PL2 is not supplied to engine ECU 200.
  • the power supply system PL3 is a power supply system to which power from a battery provided in the vehicle 50 is directly supplied, like the power supply system PL1. Therefore, regardless of whether the ignition switch of the vehicle 50 is on or off, the air conditioning ECU 300 is always supplied with power from the power supply system PL3.
  • the configuration of the control module 100 will be described with reference to FIG.
  • the control module 100 includes a reception unit 110, an input unit 120, an acquisition unit 125, a control unit 130, drivers 141 and 142, and a HUB 143.
  • the receiving unit 110 is a part that receives control signals for controlling the operation of various devices from the engine ECU 200 and the air conditioning ECU 300.
  • the control signal is a signal for controlling operations of the shutter device 20 and the electric expansion valve 730 described so far.
  • control signals are transmitted from two ECUs including the engine ECU 200 and the air conditioning ECU 300, and the control signals are received by the receiving unit 110.
  • a mode in which a control signal from a single ECU is received by the receiving unit 110 may be employed.
  • a control signal for controlling the operation of the shutter device 20 and a control signal for controlling the operation of the hot water valve 32 are transmitted from the engine ECU 200 and received by the receiving unit 110. Further, a control signal for controlling the operation of the electric expansion valve 730 is transmitted from the air conditioning ECU 300 and received by the receiving unit 110. That is, a control signal for controlling operations of a plurality of devices is received by the receiving unit 110. Instead of such an aspect, the control signal received by the receiving unit may be for controlling the operation of a single device.
  • the input unit 120 is a part to which each detection signal from the sensor 60 is input.
  • the detection signal from the sensor 60 is directly input to the control module 100 from each sensor included in the sensor 60 without passing through another ECU (electronic control unit). Since a time lag due to communication via other ECUs does not occur, the control module 100 can instantly grasp the measured values of various sensors.
  • the control module 100 can also receive a detection signal indicating the vehicle speed (the traveling speed of the vehicle 50) from a vehicle speed sensor 201 provided in the vehicle 50.
  • the detection signal transmitted from the vehicle speed sensor 201 is not directly input to the input unit 120 but is input to the control module 100 via the engine ECU 200. That is, the control module 100 can acquire the traveling speed of the vehicle 50 through communication with the engine ECU 200.
  • a mode in which a detection signal from the vehicle speed sensor 201 is directly input to the input unit 120 may be used.
  • the acquisition unit 125 is a part that acquires the degree of superheat of the refrigerant discharged from the outdoor heat exchanger 740.
  • the acquisition unit 125 acquires the refrigerant pressure measured by the pressure sensor 61 and the refrigerant temperature measured by the temperature sensor 62, and based on these, the refrigerant immediately after being discharged from the outdoor heat exchanger 740 is acquired.
  • the “superheat degree” is a temperature difference between the temperature of the refrigerant (superheated steam) discharged from the outdoor heat exchanger 740 and the saturation temperature of the refrigerant at the same pressure as the refrigerant, so-called “superheat”. It is also called.
  • the degree of superheat acquired by the acquisition unit 125 is input to the control unit 130.
  • the relationship between the refrigerant pressure and temperature and the degree of superheat is stored in advance as a map.
  • the acquisition unit 125 calculates and acquires the degree of superheat of the refrigerant by referring to the measured values of the pressure sensor 61 and the temperature sensor 62 and the map.
  • the control unit 130 is a part that controls the operation of various devices included in the heat exchange unit 10 such as the shutter device 20 and the electric expansion valve 730 via a driver 141 described later.
  • Control signals received from engine ECU 200 and air conditioning ECU 300 are input from receiving unit 110 to control unit 130.
  • Various detection signals input from the sensor 60 are input from the input unit 120 to the control unit 130.
  • the control unit 130 controls the operation of the shutter device 20 and the like based on the input control signal and detection signal.
  • the driver 141 is a part for supplying a driving current to the shutter device 20.
  • the driver 141 is supplied with power from the power supply system PL1 as power for operation.
  • the driver 141 is formed with a circuit for supplying a drive current to the shutter actuator 22.
  • the supply of driving current from the driver 141 to the shutter actuator 22 is controlled by a signal from the control unit 130. Thereby, the operation of the shutter actuator 22 is controlled, and the opening degree of the shutter device 20 is adjusted to be a predetermined opening degree.
  • the driver 142 is a part for supplying a driving current to the electric actuator 730M of the electric expansion valve 730.
  • the driver 142 is supplied with power from the power supply system PL1 as power for operation.
  • the driver 142 is formed with a circuit for adjusting the magnitude of the drive current supplied to the electric actuator 730M.
  • the magnitude of the driving current supplied to the electric actuator 730M is adjusted by a signal from the control unit 130.
  • HUB 143 is a so-called concentrator.
  • the HUB 143 is connected to signal lines connected to some of the various devices included in the heat exchange unit 10.
  • a signal line connected to the hot water valve 32 is connected to the HUB 143.
  • the HUB 143 is supplied with power from the power supply system PL1 as power for operation.
  • the control unit 130 is configured to control the operation of the hot water valve 32 by transmitting only a control signal (not a driving current) to the hot water valve 32.
  • the hot water valve 32 has a built-in driver (not shown) for controlling its operation. The driver operates based on a control signal transmitted from the control unit 130 via the HUB 143 and switches between opening and closing of the hot water valve 32.
  • the hot water valve 32 is in an open state, supply of cooling water to the radiator 31 is started.
  • the hot water valve 32 is closed, the supply of cooling water to the radiator 31 is stopped.
  • the number of devices connected to the HUB 143 may be one as in the present embodiment, or may be two or more. Further, the HUB 143 is not provided, and all the devices included in the heat exchange unit 10 are connected to the control unit 130 via a driver like the shutter device 20 in the present embodiment. May be. Such a configuration is preferable when the time lag of communication between the control unit 130 and various devices becomes a problem.
  • all the devices included in the heat exchange unit 10 may be connected to the control unit 130 via the HUB 143 like the hot water valve 32 in the present embodiment.
  • the control module 100 and the heat exchange unit 10 such a configuration is preferable.
  • the degree of superheat of the refrigerant discharged from the outdoor heat exchanger 740 which is an evaporator
  • the liquid phase is transferred to the compressor 720 on the downstream side.
  • the refrigerant may reach and the operation of the compressor 720 may be hindered.
  • the degree of superheat becomes too large, the flow path resistance of the refrigerant passing through the electric expansion valve 730 increases, and the operating efficiency of the refrigeration cycle decreases.
  • the control for matching the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 (that is, the superheat degree acquired by the acquisition unit 125) with a predetermined target value Need to do.
  • this control is also referred to as “superheat degree adjustment control”.
  • the control module 100 controls the operation of the shutter device 20 and the electric expansion valve 730 in a mode different from the mode indicated by the control signal transmitted from the host ECU (engine ECU 200 or air conditioning ECU 300). To do. A specific aspect of the superheat degree adjustment control in the present embodiment will be described with reference to FIG.
  • control 7 is a process repeatedly executed by the control module 100 every time a predetermined control cycle elapses.
  • step S01 the temperature measured by the temperature sensor 62, that is, the temperature of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S02 following step S01 the pressure measured by the pressure sensor 61, that is, the pressure of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S03 the superheat degree of the refrigerant is acquired (calculated) based on the refrigerant temperature acquired in step S01 and the refrigerant pressure acquired in step S02. This processing is performed by the acquisition unit 125 as described above.
  • step S04 it is determined whether or not the deviation amount is smaller than a predetermined value for the degree of superheat acquired in step S03.
  • the “deviation amount” here is an absolute value of a difference between the degree of superheat acquired by the acquisition unit 125 and a target value set for the degree of superheat.
  • the calculation of the deviation amount is performed by the control unit 130.
  • the target value is determined in advance by the air conditioning ECU 300 and transmitted to the control module 100.
  • step S05 the target opening degree of the electric expansion valve 730 is calculated.
  • This target opening is the opening of the electric expansion valve 730 that is necessary to bring the deviation amount close to zero.
  • the target opening is calculated by the control unit 130.
  • Such a target opening can be calculated, for example, by referring to a map prepared in advance. Further, the target opening degree may be calculated by adding a correction value determined based on the map to the target value of the opening degree of the electric expansion valve 730 transmitted from the air conditioning ECU 300.
  • step S06 a process of driving the electric expansion valve 730 (specifically, the electric actuator 730M) is performed so that the opening degree of the electric expansion valve 730 matches the target opening degree calculated in step S05. Is called.
  • This process is performed by the control unit 130.
  • the opening degree of the electric expansion valve 730 becomes equal to the target opening degree, and the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 approaches the target value.
  • step S04 when the degree of deviation of the superheat degree is equal to or greater than a predetermined value, the process proceeds to step S07.
  • step S07 the target opening degree of the shutter device 20 is calculated. This target opening is the opening of the shutter device 20 that is necessary to bring the deviation amount close to zero. The target opening is calculated by the control unit 130.
  • Such a target opening can be calculated, for example, by referring to a map prepared in advance. Further, the target opening degree may be calculated by adding a correction value determined based on the map to the target value of the opening degree of the shutter device 20 transmitted from the engine ECU 200.
  • step S08 processing for driving the shutter device 20 (specifically, the shutter actuator 22) is performed so that the opening degree of the shutter device 20 matches the target opening degree calculated in step S07. Thereby, the opening degree of the shutter device 20 matches the target opening degree, and the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 approaches the target value.
  • the control unit 130 controls the operation of the shutter device 20 (air control device) based on the degree of superheat acquired by the acquisition unit 125, and thereby the degree of superheat. It is possible to adjust. Specifically, the operation of the shutter device 20 can be controlled so that the degree of superheat acquired by the acquisition unit 125 matches the target value (steps S07 and S08).
  • control unit 130 can control the operation of the electric expansion valve 730 (refrigerant control device) based on the degree of superheat acquired by the acquisition unit 125, and thereby adjust the degree of superheat. It has become. Specifically, the operation of the electric expansion valve 730 can be controlled so that the degree of superheat acquired by the acquisition unit 125 matches the target value (steps S05 and S06).
  • the control module 100 it is possible to perform two types of control as the superheat degree adjustment control for adjusting the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740.
  • the degree of superheat is adjusted by controlling the operation of the shutter device 20 which is an air control device (steps S07 and S08).
  • the superheat degree adjustment control in this manner is also referred to as “first control”.
  • the other is to adjust the degree of superheat by controlling the operation of the electric expansion valve 730, which is a refrigerant control device (steps S05, S06).
  • the superheat degree adjustment control in this manner is also referred to as “second control”.
  • the degree of superheat of the refrigerant is adjusted by changing the opening degree of the electric expansion valve 730, that is, by performing the second control, the rate of change of the degree of superheat is relatively small.
  • the degree of superheat of the refrigerant is adjusted by changing the flow rate of the air passing through the outdoor heat exchanger 740, that is, by performing the first control, the change rate of the degree of superheat is relatively large.
  • the superheat degree is adjusted by the second control with a relatively low response speed. I do.
  • the superheat degree is adjusted by the first control having a relatively high response speed.
  • FIG. 8A shows an example of a temporal change in the degree of superheat of the refrigerant discharged from the outdoor heat exchanger 74 in the heat exchange unit 10 according to the comparative example.
  • the control for adjusting the degree of superheat to the target value SV is performed only by the control for adjusting the opening degree of the electric expansion valve 730.
  • the process for acquiring and adjusting the degree of superheat is performed by the air conditioning ECU 300 instead of the control module 100.
  • the air conditioning ECU 300 performs a process of operating the electric expansion valve 730 so that the opening degree of the electric expansion valve 730 is reduced so that the degree of superheat returns from the value MV to the target value SV.
  • a communication time lag occurs until the control signal from the air conditioning ECU 300 reaches the control module 100 and the opening of the electric expansion valve 730 starts to change. Therefore, in the example of FIG. 8A, the opening degree of the electric expansion valve 730 starts to change at time t10 after time t0.
  • a period TM10 from time t0 to time t10 corresponds to the above time lag.
  • the electric expansion valve 730 After time t10, the electric expansion valve 730 operates and its opening degree changes. Thereby, the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 gradually increases, and coincides with the target value SV at time t20. However, as already described, the change rate of the superheat degree when the opening degree of the electric expansion valve 730 changes is relatively small. For this reason, the period TM21 from time t10 when the electric expansion valve 730 starts to operate to time t20 when the superheat degree matches the target value SV is relatively long.
  • FIG. 8B shows an example of a temporal change in the degree of superheat of the refrigerant discharged from the outdoor heat exchanger 740 in the heat exchange unit 10 according to another comparative example.
  • control for adjusting the degree of superheat to the target value SV is performed only by control for adjusting the opening degree of the shutter device 20.
  • the process for acquiring and adjusting the degree of superheat is performed not by the control module 100 but by the air conditioning ECU 300.
  • the air conditioning ECU 300 performs a process of operating the shutter device 20 so that the opening degree of the shutter device 20 increases so that the degree of superheat returns from the value MV to the target value SV.
  • a communication time lag occurs until the control signal from the air conditioning ECU 300 reaches the control module 100 and the opening degree of the shutter device 20 starts to change. For this reason, the opening degree of the shutter device 20 also starts to change at time t10 after time t0.
  • a period TM10 from time t0 to time t10 corresponds to the above time lag.
  • the shutter device 20 After time t10, the shutter device 20 operates and its opening degree changes. Thereby, the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 gradually increases and matches the target value SV at time t15. As already described, the rate of change of the degree of superheat when the opening degree of the shutter device 20 changes is relatively large. For this reason, the period TM22 from time t10 when the shutter device 20 starts operating to time t15 when the superheat degree matches the target value SV is shorter than the period TM21 in FIG.
  • FIG. 8C shows an example of a temporal change in the degree of superheat of the refrigerant discharged from the outdoor heat exchanger 740 in the heat exchange unit 10 according to this embodiment.
  • the control for adjusting the superheat degree to the target value SV is performed only by the first control, that is, the control for adjusting the opening degree of the shutter device 20.
  • the control module 100 performs processing for acquiring and adjusting the degree of superheat. That is, a time lag due to communication with the air conditioning ECU 300 does not occur. Therefore, it is possible to start changing the opening degree of the shutter device 20 almost at the same time (time t0) as the degree of superheat changes suddenly and decreases to the value MV. Thereafter, at time t5 after time t0, the degree of superheat matches the target value SV.
  • a period TM23 from time t0 to time t5 is the same length as the period TM22 in FIG.
  • control module 100 may be in the form of a host ECU such as the engine ECU 200 or the air conditioning ECU 300. That is, the engine ECU 200 or the like may function as the control module 100.
  • a mode in which the control module 100 is configured as a dedicated device responsible for controlling the heat exchange unit 10 as in the present embodiment is preferable.
  • the second embodiment will be described. Below, only a different point from 1st Embodiment is demonstrated, and description is abbreviate
  • the contents of processing executed by the control module 100 are different from those in the first embodiment, and the other points are the same as those in the first embodiment.
  • a specific aspect of the superheat degree adjustment control in the present embodiment will be described with reference to FIG.
  • the series of processes shown in FIG. 9 is a process that is repeatedly executed by the control module 100 every time a predetermined control period elapses. This process is executed in place of the series of processes shown in FIG.
  • step S11 the temperature measured by the temperature sensor 62, that is, the temperature of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S12 the pressure measured by the pressure sensor 61, that is, the pressure of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S13 the superheat degree of the refrigerant is obtained (calculated) based on the refrigerant temperature obtained in step S11 and the refrigerant pressure obtained in step S12. This processing is performed by the acquisition unit 125 as described above.
  • step S14 the target opening of the electric expansion valve 730 is calculated.
  • This target opening is the opening of the electric expansion valve 730 that is necessary to bring the already described deviation amount close to zero.
  • the target opening is calculated by the control unit 130.
  • FIG. 10 shows a correspondence relationship between the degree of superheat (horizontal axis) acquired in step S13 and the target opening degree (vertical axis) calculated in step S14.
  • the correspondence relationship is created in advance as a map and stored in the storage device of the control module 100.
  • the target opening degree of the electric expansion valve 730 is calculated based on the correspondence relationship of FIG.
  • the target opening is set to be larger (open side) as the degree of superheat acquired by the acquisition unit 125 increases.
  • coolant in the outdoor heat exchanger 740 rises, and the heat absorption amount in the outdoor heat exchanger 740 becomes small.
  • the degree of superheat at the outlet portion of the outdoor heat exchanger 740 is reduced.
  • the target opening is set to be smaller (to the throttle side) as the degree of superheat acquired by the acquisition unit 125 becomes smaller.
  • coolant in the outdoor heat exchanger 740 falls, and the heat absorption amount in the outdoor heat exchanger 740 becomes large.
  • the degree of superheat at the outlet portion of the electric expansion valve 730 increases.
  • step S15 the target opening of the shutter device 20 is calculated.
  • This target opening is the opening of the shutter device 20 that is necessary to bring the already explained difference close to zero.
  • the target opening is calculated by the control unit 130.
  • FIG. 11 shows the correspondence between the degree of superheat (horizontal axis) acquired in step S13 and the target opening (vertical axis) calculated in step S15.
  • the correspondence is created in advance as a map and stored in the storage device of the control module.
  • step S15 the target opening degree of the shutter device 20 is calculated based on the correspondence relationship in FIG.
  • the target opening is set to be smaller (to the throttle side) as the degree of superheat acquired by the acquisition unit 125 increases.
  • the flow rate of the air passing through the outdoor heat exchanger 740 is reduced, and the heat absorption amount in the outdoor heat exchanger 740 is reduced.
  • the degree of superheat at the outlet portion of the outdoor heat exchanger 740 is reduced.
  • the target opening degree is set to be larger (open side) as the degree of superheat acquired by the acquisition unit 125 becomes smaller.
  • the flow rate of air passing through the outdoor heat exchanger 740 increases, and the amount of heat absorbed in the outdoor heat exchanger 740 increases.
  • the degree of superheat at the outlet portion of the electric expansion valve 730 increases.
  • step S16 a process of driving the electric expansion valve 730 (specifically, the electric actuator 730M) is performed so that the opening degree of the electric expansion valve 730 matches the target opening degree calculated in step S14. Is called.
  • This process is performed by the control unit 130.
  • the opening degree of the electric expansion valve 730 becomes equal to the target opening degree, and the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 approaches the target value.
  • step S17 following step S16 a process of driving the shutter device 20 (specifically, the shutter actuator 22) is performed so that the opening degree of the shutter device 20 matches the target opening degree calculated in step S15.
  • the opening degree of the shutter device 20 matches the target opening degree, and the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 approaches the target value.
  • the first control (step S17) for changing the flow rate of the air passing through the outdoor heat exchanger 740, and the first control for changing the opening degree of the electric expansion valve 730. 2 control (step S16) is performed in parallel. Even in such an aspect, the same effects as those described in the first embodiment can be obtained. Moreover, in this embodiment, since 1st control and 2nd control are performed simultaneously, it is possible to change a superheat degree in a wider range. For this reason, the degree of superheat during operation of the vehicle air conditioner 70 can be further stabilized.
  • the third embodiment will be described. Below, only a different point from 1st Embodiment is demonstrated, and description is abbreviate
  • the contents of processing executed by the control module 100 are different from those in the first embodiment, and the other points are the same as those in the first embodiment.
  • a specific aspect of the superheat degree adjustment control in the present embodiment will be described with reference to FIG.
  • step S21 the temperature measured by the temperature sensor 62, that is, the temperature of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S22 following step S21 the pressure measured by the pressure sensor 61, that is, the pressure of the refrigerant discharged from the outdoor heat exchanger 740 is acquired.
  • step S23 the superheat degree of the refrigerant is acquired (calculated) based on the refrigerant temperature acquired in step S21 and the refrigerant pressure acquired in step S22. This processing is performed by the acquisition unit 125 as described above.
  • step S24 following step S23 the air volume of the air passing through the outdoor heat exchanger 740 is calculated and acquired based on the wind speed measured by the wind speed sensor 63.
  • step S25 following step S24 the target opening degree of the shutter device 20 is calculated based on the degree of superheat acquired in step S23 and the air volume calculated in step S24.
  • This target opening is the opening of the shutter device 20 that is necessary to bring the degree of superheat close to the target value.
  • the target opening is calculated by the control unit 130.
  • step S26 following step S25, the shutter device 20 (specifically, the shutter actuator 20) is adjusted so that the opening degree of the shutter device 20 coincides with the target opening degree calculated in step S25 (that is, the deviation amount approaches 0). 22) is driven. This process is performed by the control unit 130. Thereby, the opening degree of the shutter device 20 matches the target opening degree, and the superheat degree of the refrigerant at the outlet portion of the outdoor heat exchanger 740 approaches the target value.
  • FIG. 13 shows the contents of the processing shown in FIG. 12 as a so-called block diagram.
  • Block B1 shows the target value of the degree of superheat at the outlet of the outdoor heat exchanger 740. As already described, the target value is determined in advance by the air conditioning ECU 300 and transmitted to the control module 100.
  • Block B2 is a so-called adder.
  • a deviation between a target value of the superheat degree input from block B1 and an actual superheat degree input from block B11 described later is calculated, and the deviation is output toward block B3.
  • a target value for the air volume of the air passing through the outdoor heat exchanger 740 is calculated based on the deviation.
  • the target value of the air volume necessary for setting the above deviation to 0 is calculated.
  • the calculated target value of the air volume is output toward the block B4.
  • Block B4 is an adder. In block B4, the deviation between the target value of the air volume input from block B3 and the actual air volume input from block B13, which will be described later, is calculated, and the deviation is output toward block B5.
  • the target opening degree of the shutter device 20 is calculated based on the above deviation.
  • the target opening is the target opening calculated in step S25 of FIG.
  • the target opening degree required to set the deviation input from block B4 to 0 is calculated by calculating a map created in advance.
  • the calculated target opening is output toward the block B7.
  • the target opening is corrected in advance based on the operating state of the electric fan 40 input from the block B6. This process is executed by the control unit 130.
  • the “operating state of the electric fan 40” is the number of rotations of the electric fan 40.
  • the target opening degree is corrected so that the opening degree of the shutter device 20 decreases as the rotational speed of the electric fan 40 increases. For this reason, for example, when the electric fan 40 is over-rotated, the amount of air passing through the outdoor heat exchanger 740 becomes too large, and the degree of superheat is prevented from deviating from the target value. Is done.
  • the parameter used as the “operating state of the electric fan 40” may be the rotational speed of the electric fan 40 as in the present embodiment, but indirectly indicates the rotational speed of the electric fan 40. May be.
  • the current value flowing through the fan motor 42 may be used as the “operating state of the electric fan 40”.
  • control is performed to change the opening degree of the shutter device 20 in accordance with the rotational speed of the electric fan 40 that sends air into the outdoor heat exchanger 740.
  • the control unit 130 performs a process of reducing the opening degree of the shutter device 20 as the rotational speed of the electric fan 40 increases.
  • the target opening degree of the shutter device 20 calculated in block B5 is input to block B7.
  • block B7 a process for matching the opening degree of the shutter device 20 with the target opening degree is performed. That is, the block B7 shows the process shown in step S26 of FIG.
  • Block B8 is a block showing such a change in air volume. Further, when the air volume passing through the outdoor heat exchanger 740 changes, the state (pressure and temperature) of the refrigerant discharged from the outdoor heat exchanger 740 also changes.
  • Block B9 is a block showing the refrigerant state changing in this way.
  • block B10 the refrigerant state changed as described above is acquired. Specifically, the pressure of the refrigerant is acquired by the pressure sensor 61, and the temperature of the refrigerant is acquired by the temperature sensor 62. In this way, the block B10 indicates the processing shown in steps S21 and S22 of FIG. The pressure and temperature of the refrigerant acquired in block B10 are input to block B11.
  • Block B11 based on the pressure and temperature of the refrigerant, the degree of superheat of the refrigerant at the outlet of the outdoor heat exchanger 740 is calculated and acquired.
  • Block B11 shows the processing shown in step S23 of FIG.
  • the degree of superheat calculated in block B11 is input to block B2, and is used for calculation of the deviation in superheat degree as already described.
  • the wind speed of the air passing through the outdoor heat exchanger 740 is acquired by the wind speed sensor 63.
  • the acquired wind speed is input to block B13.
  • the wind speed input from block B12 is converted into the “air volume” of the air passing through the outdoor heat exchanger 740.
  • the air volume is input to the block B4 and used for calculating the deviation of the air volume as already described.
  • the process shown in FIG. 13 is a process in which a feedback loop for matching the air volume with the target value is formed inside the feedback loop for matching the degree of superheat with the target value.
  • the degree of superheat can be controlled more accurately by adjusting the air volume.
  • the fourth embodiment will be described. Below, only a different point from 3rd Embodiment is demonstrated, and description is abbreviate
  • part of the processing executed by the control module 100 is different from that of the third embodiment, and the other points are the same as those of the third embodiment.
  • a specific aspect of the superheat degree adjustment control in the present embodiment will be described with reference to FIG.
  • step S24 is replaced with step S31 and replacing step S25 with step S32 in the series of processes shown in FIG.
  • steps common to those shown in FIG. 12 are denoted by the same reference numerals (S ⁇ b> 21 and the like) as those in FIG.
  • step S31 executed subsequent to step S23, the vehicle speed measured by the vehicle speed sensor 201, that is, the traveling speed of the vehicle 50 is acquired.
  • step S32 following step S31, the target opening of the shutter device 20 is calculated based on the degree of superheat acquired in step S23 and the travel speed acquired in step S31. This target opening is the opening of the shutter device 20 that is necessary to bring the degree of superheat close to the target value.
  • the target opening is calculated by the control unit 130.
  • FIG. 15 shows the contents of a series of processes shown in FIG. 14 as a so-called block diagram.
  • those common to the blocks shown in FIG. 13 are denoted by the same reference numerals (B1 etc.) as those in FIG. 13. Only the differences from FIG. 13 will be described below.
  • the block B3 in FIG. 13 is replaced with a block B31.
  • the target value for the air volume of the air passing through the outdoor heat exchanger 740 is calculated as in the block B3.
  • the target value of the air volume is calculated based on the vehicle speed measured by the vehicle speed sensor 201 in addition to the deviation input from block B4.
  • the vehicle speed measured by the vehicle speed sensor 201 is shown as a block B32. It can be said that the block B32 indicates the processing shown in step S31 of FIG.
  • the target value of the calculated air volume is corrected based on the vehicle speed input from block B32, that is, the traveling speed of the vehicle 50.
  • This process is executed by the control unit 130. Specifically, the correction is made so that the target value of the air volume decreases as the traveling speed of the vehicle 50 increases. Further, the target value of the air volume is corrected so as to decrease as the traveling speed of the vehicle 50 decreases.
  • the calculated target value of the air volume is input to the block B33.
  • the block B5 in FIG. 13 is replaced with a block B33.
  • there is no loop (block B12, block B13, and block B4 in FIG. 13) that feeds back the actual measurement value of the air volume.
  • the target opening of the shutter device 20 is calculated according to the target value of the air volume input from block B31. That is, in this embodiment, the target opening degree of the shutter device 20 is determined by feedforward.
  • the target opening degree of the shutter device 20 is calculated as a larger value (open side value). Further, the target opening degree of the shutter device 20 is calculated as a smaller value (a value on the aperture side) as the target value of the input air volume becomes smaller.
  • Such a correspondence relationship is created in advance as a map and stored in the storage device of the control module 100.
  • the calculated target opening is corrected based on the operating state of the electric fan 40 input from the block B6. A specific correction method is the same as that described in FIG.
  • control for changing the opening degree of the shutter device 20 according to the traveling speed of the vehicle 50 is performed. Specifically, the control unit 130 performs control such that the target value of the air volume is set lower as the traveling speed of the vehicle 50 increases (block B31), thereby reducing the opening of the shutter device 20 (block B33). Done. Further, the control unit 130 performs control such that the target value of the air volume is set lower as the traveling speed of the vehicle 50 increases (block B31), thereby reducing the opening of the shutter device 20 (block B33). Thereby, even when the air volume flowing from the front grill GR varies according to the traveling speed of the vehicle 50, the degree of superheat can be reliably brought close to the target value.
  • the shutter device 20 is used as an air control device whose operation is controlled in the superheat degree adjustment control. It may replace with such an aspect and the aspect that the electric fan 40 is used as a control object in superheat degree adjustment control may be sufficient.
  • control for reducing the rotational speed of the electric fan 40 is performed.
  • control for increasing the rotational speed of the electric fan 40 is performed.

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  • Cooling, Air Intake And Gas Exhaust, And Fuel Tank Arrangements In Propulsion Units (AREA)

Abstract

La présente invention concerne un module de commande (100) qui commande une unité d'échange de chaleur (10) qui est fournie sur un véhicule (50). L'unité d'échange de chaleur comprend : un échangeur de chaleur (740) qui échange de la chaleur entre l'air et un liquide de refroidissement de climatisation et évapore ainsi de manière interne le liquide de refroidissement ; et un dispositif de régulation d'air (20) qui ajuste le flux d'air qui circule à partir d'une grille avant (GR) du véhicule et passe à travers l'échangeur de chaleur. Le module de commande comprend : une unité de commande (130) qui commande le fonctionnement du dispositif de régulation d'air ; et une unité d'acquisition (125) qui acquiert le degré de surchauffe du liquide de refroidissement pendant son évacuation de l'échangeur de chaleur. L'unité de commande commande le fonctionnement du dispositif de régulation d'air sur la base du degré de surchauffe acquis par l'unité d'acquisition.
PCT/JP2017/040447 2016-12-26 2017-11-09 Module de commande WO2018123289A1 (fr)

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JP2016-250930 2016-12-26
JP2016250930A JP6673187B2 (ja) 2016-12-26 2016-12-26 制御モジュール

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WO2018123289A1 true WO2018123289A1 (fr) 2018-07-05

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CN113858910A (zh) * 2021-08-26 2021-12-31 智马达汽车有限公司 一种电池板式换热器的电子膨胀阀开度控制方法和系统

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JP7393289B2 (ja) 2020-04-13 2023-12-06 株式会社Subaru 車両
CN114454687A (zh) * 2022-02-08 2022-05-10 浙江吉利控股集团有限公司 空气电加热器保护方法、装置、设备及存储介质
WO2024009860A1 (fr) * 2022-07-05 2024-01-11 株式会社デンソー Dispositif à cycle de réfrigération

Citations (3)

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JPS62168915U (fr) * 1986-03-25 1987-10-27
JP2003182349A (ja) * 2001-12-14 2003-07-03 Denso Corp 冷凍サイクル装置
JP2004150277A (ja) * 2002-10-28 2004-05-27 Calsonic Kansei Corp 車両用熱交換器の通風装置およびその制御方法

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JP2008302721A (ja) 2007-06-05 2008-12-18 Calsonic Kansei Corp 車両用空調制御装置

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JPS62168915U (fr) * 1986-03-25 1987-10-27
JP2003182349A (ja) * 2001-12-14 2003-07-03 Denso Corp 冷凍サイクル装置
JP2004150277A (ja) * 2002-10-28 2004-05-27 Calsonic Kansei Corp 車両用熱交換器の通風装置およびその制御方法

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113858910A (zh) * 2021-08-26 2021-12-31 智马达汽车有限公司 一种电池板式换热器的电子膨胀阀开度控制方法和系统
CN113858910B (zh) * 2021-08-26 2023-08-29 浙江智马达智能科技有限公司 一种电池板式换热器的电子膨胀阀开度控制方法和系统

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JP2018103717A (ja) 2018-07-05
DE112017006541T5 (de) 2019-09-26

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