JP6341021B2 - Air conditioner for vehicles - Google Patents

Description

  The present invention relates to a vehicle air conditioner capable of heating air cooled by an evaporator provided in an air conditioning duct with a heater core provided on the downstream side of the air flow.

  Conventionally, an air conditioner for a vehicle that cools air with an evaporator provided in an air conditioning duct and adjusts the temperature of the conditioned air by heating the air flowing out of the evaporator with a heater core provided on the downstream side of the air flow of the evaporator. (See, for example, Patent Document 1 below). In this vehicle air conditioner, a bypass passage for taking cooling air from the evaporator into the air conditioning duct is provided in parallel to the air passage to the heater core and the cold air bypass passage, and the heat exchanger for supercooling is provided in the bypass passage Is arranged. When the air mix door opens the ventilation path to the heater core, the cooling air is blown also to the bypass passage so that the refrigerant condensed by the condenser is further cooled by the supercooling heat exchanger. Yes.

JP-A-5-8631

  In the above-described conventional vehicle air conditioner, the refrigerant condensed in the condenser is further cooled by the supercooling heat exchanger, so that the refrigerant flowing into the evaporator and the refrigerant flowing out from the evaporator A large difference in enthalpy can be secured.

  However, since the vehicle air conditioner has a configuration in which the subcooling heat exchanger, which is an auxiliary heat exchanger, is arranged in the bypass passage, there is a problem that the air conditioning duct becomes large.

  The present invention has been made in view of the above problems, and aims to ensure a large enthalpy difference between the refrigerant flowing into the evaporator and the refrigerant flowing out of the evaporator without providing an auxiliary heat exchanger in the air conditioning duct. To do.

In order to achieve the above object, the invention described in claim 1 includes an air-conditioning duct (10) for circulating air blown into the passenger compartment, a compressor (2) for compressing and discharging the sucked refrigerant, and a compressor A condenser (3) for condensing the refrigerant discharged by the heat exchange with the outside air, a decompression device (5) for decompressing the refrigerant condensed in the condenser, and an evaporator (6) for cooling the air flowing in the air conditioning duct The refrigerant is cooled by the evaporator by heat exchange between the refrigeration cycle apparatus (1) and the cooling liquid that is disposed on the downstream side of the air flow from the evaporator in the air conditioning duct and cools the heat generating device (30) mounted on the vehicle The refrigerant that has flowed out of the condenser by heat exchange between the heater core (34) that heats the heated air and the refrigerant that flows out of the condenser and flows into the decompression device and the cooling liquid cooled by the heater core outside the air conditioning duct. Auxiliary heat exchange for cooling (4) and the cooling fluid flowing out from the auxiliary heat exchanger, a flow path that flows through the heater core to the auxiliary heat exchanger without passing through a heating device, the auxiliary heat exchanger via a heat-generating equipment and the heater core A first channel switching device (33) that switches between channels that flow into the vessel, a heating determination unit (S106) that determines whether or not heating of the coolant is necessary based on the target blowing temperature, and heating When it is determined by the determining means that heating of the coolant is not necessary, the coolant that has flowed out of the auxiliary heat exchanger becomes a flow path that flows into the auxiliary heat exchanger via the heater core without passing through the heating device. In this way, when it is determined by the first flow path control means (S107) that controls the first flow path switching device and the heating determination means that heating of the coolant is necessary, the coolant that has flowed out of the auxiliary heat exchanger , Heating devices and heaters A second flow path control means (S108) for controlling the first flow path switching unit such that the flow path that flows into the auxiliary heat exchanger via the A, is characterized by comprising a.

According to such a structure, the auxiliary | assistant which cools the refrigerant | coolant which flowed out from the condenser by heat exchange with the cooling fluid which flowed out of the condenser and flowed out of the condenser into the decompression device, and the cooling liquid cooled by the heater core outside the air conditioning duct. Since the heat exchanger (4) is provided, the refrigerant flowing out of the condenser and flowing into the decompression device can be further cooled by the auxiliary heat exchanger. Thereby, a large enthalpy difference between the refrigerant flowing into the evaporator and the refrigerant flowing out of the evaporator can be ensured.
In order to achieve the above object, the invention described in claim 2 includes an air conditioning duct (10) for circulating air blown into the vehicle interior, a compressor (2) for compressing and discharging the sucked refrigerant, A condenser (3) that condenses the refrigerant discharged from the compressor by heat exchange with the outside air, a decompression device (5) that decompresses the refrigerant condensed in the condenser, and an evaporator (6) that cools the air flowing in the air conditioning duct The refrigeration cycle apparatus (1) having a) and an evaporator by heat exchange with a cooling liquid that is disposed downstream of the evaporator in the air conditioning duct and cools the heat generating device (30) mounted on the vehicle. Heater core (34) that heats the cooled air and out of the air-conditioning duct, the refrigerant flows out of the condenser and flows out of the condenser by heat exchange between the refrigerant that flows into the decompression device and the coolant cooled by the heater core. Auxiliary cooling refrigerant The exchanger (4), the flow path through which the coolant flowing out of the heater core flows into the heater core via the auxiliary heat exchanger and the heat generating device, and the heater core via the heat generating device without passing through the auxiliary heat exchanger A second flow path switching device (33a, 33b) that switches between the flow path that flows into the flow path, a heating determination means (S106) that determines whether or not heating of the coolant is necessary based on the target blowing temperature, When the heating determination means determines that heating of the coolant is not necessary, the second flow path is such that the coolant that has flowed out of the heater core becomes a flow path that flows into the heater core via the auxiliary heat exchanger and the heating device. When it is determined by the third flow path control means (S207) that controls the switching device and the heating determination means that heating of the coolant is necessary, the coolant that has flowed out of the heater core passes through the auxiliary heat exchanger. It is characterized by having a the fourth channel control means for controlling the second flow path switching unit (S208), so that the flow path flowing to the heater core via a heat-generating device without the.
According to such a structure, the auxiliary | assistant which cools the refrigerant | coolant which flowed out from the condenser by heat exchange with the cooling fluid which flowed out of the condenser and flowed out of the condenser into the decompression device, and the cooling liquid cooled by the heater core outside the air conditioning duct. Since the heat exchanger (4) is provided, the refrigerant flowing out of the condenser and flowing into the decompression device can be further cooled by the auxiliary heat exchanger. Thereby, a large enthalpy difference between the refrigerant flowing into the evaporator and the refrigerant flowing out of the evaporator can be ensured.

  In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

It is a mimetic diagram showing a schematic structure of an air-conditioner for vehicles in a 1st embodiment of the present invention. It is a block diagram which shows the control system of the vehicle air conditioner of 1st Embodiment. It is a 1st flowchart which shows the control processing of air-conditioner ECU50 in 1st Embodiment. It is a 2nd flowchart which shows the control processing of air-conditioner ECU50 in 1st Embodiment. It is a pressure-enthalpy diagram which shows an example of the state of the refrigerant | coolant which circulates through the refrigerating-cycle apparatus 1 of 1st Embodiment. It is the figure which showed the structural example which provided the supercooling heat exchanger in the air conditioning duct 10 in 1st Embodiment. It is the figure which showed the relationship between the thermal radiation amount from the refrigerant | coolant to the air in the heat exchanger 4 for supercooling of 1st Embodiment, and the power saving effect of the refrigerating-cycle apparatus 1. FIG. It is a schematic diagram which shows schematic structure of the vehicle air conditioner in 2nd Embodiment of this invention. It is a 2nd flowchart which shows the control processing of air-conditioner ECU50 in 2nd Embodiment, Comprising: It is the flowchart which showed the subroutine performed by step S03 of FIG. It is a schematic diagram which shows schematic structure of the vehicle air conditioner in 3rd Embodiment of this invention. It is a 2nd flowchart which shows the control processing of air-conditioner ECU50 in 3rd Embodiment, Comprising: It is the flowchart which showed the subroutine performed by step S03 of FIG. It is a schematic diagram which shows schematic structure of the vehicle air conditioner 100 in 4th Embodiment, Comprising: It is a figure equivalent to FIG. It is a 1st flowchart which shows the control processing of air-conditioner ECU50 in 4th Embodiment. 14 is a second flowchart showing a control process of the air conditioner ECU 50 in the fourth embodiment, and is a flowchart showing a subroutine executed in step S15 of FIG. It is the figure which showed the relationship between the target engine cooling water temperature TWn required in order to achieve the target blowing temperature TAO and the target blowing temperature TAO in the heating operation in 4th Embodiment. FIG. 10 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the fifth embodiment, in which the refrigerant flow path constituting the first refrigerant circuit 60 is represented by a solid line, and the refrigerant flow separated from the first refrigerant circuit 60 It is the figure which represented the path | route with the broken line. FIG. 10 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the fifth embodiment, in which a refrigerant flow path constituting the second refrigerant circuit 62 is represented by a solid line, and a refrigerant flow separated from the second refrigerant circuit 62 It is the figure which represented the path | route with the broken line. FIG. 10 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the sixth embodiment, in which the refrigerant flow path constituting the first refrigerant circuit 60 is represented by a solid line, and the refrigerant flow separated from the first refrigerant circuit 60 It is the figure which represented the path | route with the broken line. FIG. 14 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the sixth embodiment, in which the refrigerant flow path constituting the second refrigerant circuit 62 is represented by a solid line, and the refrigerant flow deviated from the second refrigerant circuit 62 It is the figure which represented the path | route with the broken line. FIG. 14 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the seventh embodiment, in which the refrigerant flow path constituting the first refrigerant circuit 60 is represented by a solid line and the refrigerant flow separated from the first refrigerant circuit 60 It is the figure which represented the path | route with the broken line. FIG. 14 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the seventh embodiment, in which a refrigerant flow path constituting the second refrigerant circuit 62 is represented by a solid line, and a refrigerant flow separated from the second refrigerant circuit 62 It is the figure which represented the path | route with the broken line. FIG. 14 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the eighth embodiment, in which the refrigerant flow path constituting the first refrigerant circuit 60 is represented by a solid line and the refrigerant flow separated from the first refrigerant circuit 60 It is the figure which represented the path | route with the broken line. FIG. 14 is a diagram showing a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the eighth embodiment, in which the refrigerant flow path constituting the second refrigerant circuit 62 is represented by a solid line and the refrigerant flow separated from the second refrigerant circuit 62 It is the figure which represented the path | route with the broken line. FIG. 20 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the ninth embodiment, in which the refrigerant flow path constituting the first refrigerant circuit 60 is represented by a solid line, and the refrigerant flow deviated from the first refrigerant circuit 60 It is the figure which represented the path | route with the broken line. FIG. 20 is a diagram illustrating a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the ninth embodiment, in which the refrigerant flow path constituting the second refrigerant circuit 62 is represented by a solid line, and the refrigerant flow deviated from the second refrigerant circuit 62 It is the figure which represented the path | route with the broken line.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. In the following embodiments, the same or equivalent parts are denoted by the same reference numerals in the drawings.

(First embodiment)
FIG. 1 is a schematic diagram showing a schematic configuration of a vehicle air conditioner 100 according to the first embodiment of the present invention. A vehicle air conditioner 100 shown in FIG. 1 is mounted on, for example, a vehicle including an engine 30 that is a traveling internal combustion engine, and air-conditions a vehicle interior, that is, a vehicle interior. The engine 30 also functions as a heat generating device mounted on the vehicle.

  As shown in FIG. 1, the vehicle air conditioner 100 includes an air conditioning duct 10, a refrigeration cycle device 1, a cooling water circuit 31, a heater core 34, an air mix door device 17, blowing mode doors 21 to 23, and the control shown in FIG. 2. An air conditioner electronic control device 50 (hereinafter also referred to as an air conditioner ECU 50), an inside / outside air switching door 13 (see FIG. 2), a blower 14 (see FIG. 2), and the like are provided.

  The air conditioning duct 10 forms an air passage 10a for guiding conditioned air blown into the vehicle interior. The air conditioning duct 10 is provided in the vicinity of the front in the vehicle interior. The most upstream side of the air conditioning duct 10 is a portion constituting an inside / outside air switching box, an inside air inlet for taking in air in the vehicle interior (hereinafter also referred to as inside air), and air outside the vehicle compartment (hereinafter also referred to as outside air). An inside / outside air switching box (not shown) in which an outside air suction port for taking in is formed is provided.

  The inside air / outside air switching port of the inside / outside air switching box is opened and closed by an inside / outside air switching door 13 (see FIG. 2) driven by an actuator such as a servo motor, and the air inlet mode of the vehicle air conditioner 100 is The operation of the air switching door 13 is switched to the inside air circulation mode or the outside air introduction mode. Then, outside air or inside air, which is air from the inside / outside air switching box, is caused to flow into the air passage 10a as indicated by an arrow FLin by the blower 14 (see FIG. 2).

  The most downstream side of the air-conditioning duct 10 is a portion constituting the blowout outlet switching box, and a defroster opening, a face opening, and a foot opening are formed. A defroster duct is connected to the defroster opening, and a defroster outlet 18 for blowing hot air mainly toward the inner surface of the front window glass of the vehicle is opened at the most downstream end of the defroster duct. A face duct is connected to the face opening, and a face air outlet 19 that blows mainly cool air toward the occupant's head and chest is opened at the most downstream end of the face duct. Furthermore, a foot duct is connected to the foot opening, and a foot outlet 20 that mainly blows warm air toward the feet of the occupant is opened at the most downstream end of the foot duct.

  Defroster doors 21, face doors 22, and foot doors 23 that open and close the respective openings are rotatably mounted inside the air outlets 18, 19, and 20. These doors 21, 22 and 23 are driven by actuators such as servo motors, respectively, and the outlet mode can be switched to the face mode, the bi-level mode, the foot mode, the foot defroster mode, or the defroster mode. It has become. The defroster door 21, the face door 22, and the foot door 23 are blowing mode switching devices.

  The blower 14 (see FIG. 2) is an electric blower that generates an air flow in the air conditioning duct 10, and the rotational speed of the electric motor that rotationally drives the impeller is determined according to the voltage applied to the electric motor. . And the applied voltage to the electric motor is controlled based on the control signal from air-conditioner ECU50 (refer FIG. 2), and the ventilation volume of the blower 14 is controlled by control of the applied voltage.

  As shown in FIG. 1, the refrigeration cycle apparatus 1 includes a compressor 2, a condenser 3, a supercooling heat exchanger 4 as an auxiliary heat exchanger 4, a decompression device 5, and an evaporator 6 in order through a refrigerant pipe 9. It is configured to be connected in a ring shape. Thus, a refrigerant circuit is constructed in which the refrigerant discharged from the compressor 2 returns to the compressor 2 through the condenser 3, the supercooling heat exchanger 4, the decompression device 5, and the evaporator 6 in order. In addition, an auxiliary heat exchanger is not limited to what supplements the amount of heat exchange smaller than another heat exchanger. For example, the heat exchange amount of the supercooling heat exchanger 4 may be larger than the heat exchange amount of the condenser 3.

  The compressor 2 has a refrigerant suction port 2a and a refrigerant discharge port 2b, compresses the refrigerant sucked from the refrigerant suction port 2a, and discharges the compressed refrigerant from the refrigerant discharge port 2b. The condenser 3 condenses the refrigerant discharged from the compressor 2 through heat exchange with the outside air. The supercooling heat exchanger 4 further cools the refrigerant condensed in the condenser 3. Specifically, the supercooling heat exchanger 4 further cools the refrigerant flowing out of the condenser 3 by heat exchange with the cooling water flowing out from the heater core 34 disposed on the downstream side of the air flow of the evaporator 6. . The decompression device 5 decompresses and expands the refrigerant cooled by the supercooling heat exchanger 4. The evaporator 6 evaporates the refrigerant decompressed by the decompression device 5.

  The compressor 2 is provided, for example, in the engine room of the vehicle. The compressor 2 is connected to the engine 30 and is driven by the driving force of the engine 30. Further, the compressor 2 has an electromagnetic clutch 2c, and transmission of driving force from the engine 30 is interrupted by the electromagnetic clutch 2c. The intermittent operation of the electromagnetic clutch 2c is controlled by the air conditioner ECU 50.

  For example, the condenser 3 is provided in a place where it is easy to receive traveling wind generated when the vehicle travels, such as in front of the engine room of the vehicle, and exchanges heat between the refrigerant flowing in the interior, the outside air blown by the outdoor fan, and the traveling wind. It is an outdoor heat exchanger.

  In the refrigeration cycle apparatus 1, for example, a gas-liquid separator can be provided between the condenser 3 and the supercooling heat exchanger 4. This gas-liquid separator gas-liquid separates the refrigerant that has flowed out of the condenser 3 to flow only the liquid-phase refrigerant downstream, and stores excess refrigerant therein. When the condenser 3 is a so-called subcool condenser having a condensing part and a supercooling part, a gas-liquid separator can be provided between the condensing part and the supercooling part of the condenser 3.

  The cooling water circuit 31 is a heat medium circuit that connects the engine 30, the heater core 34, and the supercooling heat exchanger 4. The cooling water circuit 31 is provided with a water pump 32 and a flow path switching valve 33 as a first flow path switching device.

  The water pump 32 circulates cooling water for cooling the engine 30 in the cooling water circuit 31.

  In response to an instruction from the air conditioner ECU 50, the flow path switching valve 33 is a flow path (closed) in which the cooling water flowing out from the supercooling heat exchanger 4 flows into the heater core 34 via the water pump 32 without passing through the engine 30. Circuit) and the flow path (open circuit) through which the cooling water flowing out from the supercooling heat exchanger 4 flows into the heater core 34 via the engine 30 and the water pump 32 is switched.

  In the heater core 34, cooling water which is a heat medium that receives heat from the engine 30 and cools the engine 30 flows inside. The heater core 34 is a heating device that heats the air cooled by the evaporator 6 by heat exchange with cooling water that cools the engine 30 mounted on the vehicle.

  The evaporator 6 is arrange | positioned in the air flow path 10a in the air-conditioning duct 10 in the air flow downstream rather than the blower 14 (refer FIG. 2). In detail, the evaporator 6 is arrange | positioned so that the whole channel | path immediately after the blower 14 may be traversed. Therefore, all the air blown out from the blower 14 passes through the evaporator 6. And the evaporator 6 cools the air which flows through the air path 10a by heat exchange with the refrigerant decompressed by the decompression device 5. That is, the evaporator 6 performs heat exchange between the refrigerant flowing inside and the air flowing through the air passage 10a to perform an air cooling action for cooling the air and an air dehumidifying action for dehumidifying the air passing through the evaporator 6. It is an indoor heat exchanger.

  On the downstream side of the air flow of the evaporator 6, the air passage 10a is branched into two at a branch point 10c. On the downstream side of the air flow from the branch point 10 c, the air passage 10 a is a heating passage 15 and a cold air bypass passage 16. A heater core 34 is disposed in the heating passage 15. The heater core 34 is disposed so as to cross the entire heating passage.

  The supercooling heat exchanger 4 is a heat exchanger that cools the refrigerant that flows out of the condenser 3 and flows into the decompression device 5 by heat exchange with the cooling water that flows out of the heater core 34. The supercooling heat exchanger 4 is installed outside the air conditioning duct 10 or the vehicle air conditioning unit (HVAC), for example, in an engine room of the vehicle.

  Since the heater core 34 is disposed on the downstream side of the air flow of the evaporator 6 in the air conditioning duct 10, the cooling water flowing out of the heater core 34 is cooled to a temperature lower than the outside air temperature (for example, 5 ° C.) during the cooling operation. . The supercooling heat exchanger 4 further cools the refrigerant flowing out of the condenser 3 and flowing into the decompression device 5 by heat exchange with the cooling water cooled by the heater core 34.

  The cold air bypass passage 16 is a passage that bypasses the heater core 34 and distributes air. An air mix door 17 is disposed in the vicinity of the branch point 10 c between the heating passage 15 and the cold air bypass passage 16.

  The air mix door 17 is an air volume ratio adjusting device that adjusts the air volume ratio between the air passing through the heating passage 15 and the air passing through the cold air bypass passage 16. The air mix door 17 changes the position of the door body by an actuator or the like, for example, and adjusts the air distribution downstream of the evaporator 6 in the air conditioning duct 10 to adjust the temperature of air blown out into the vehicle interior. .

  On the downstream side of the air flow of the heating passage 15 and the cold air bypass passage 16, a cold / hot air mixing space capable of mixing the hot air from the heating passage 15 and the cold air from the cold air bypass passage 16 is formed. The above-described defroster opening, face opening, and foot opening are formed so as to face the cold / hot air mixing space, and air from the cold / hot air mixing space can flow into each opening.

  Next, the configuration of the control system of the present embodiment will be described with reference to FIG. The air conditioner ECU 50 receives switch signals from switches such as a temperature setting switch on the operation panel 51 provided on the front surface of the vehicle interior, and sensor signals from the sensors.

  An air conditioning activation switch 52 is provided on the front surface of the vehicle interior together with the operation panel 51. The air conditioning activation switch 52 is an air conditioning switch that is operated by the occupant in order to switch between activation (on) and stop (off) of the air conditioning operation. The air conditioner start switch 52 is switched to one of two operation positions: an air conditioner on position that activates the air conditioner operation, and an air conditioner off position that stops the air conditioner operation. A signal indicating the operation position of the air conditioning activation switch 52 is also input to the air conditioner ECU 50. The air conditioner operation is, for example, a cooling operation or a dehumidifying operation, and is an air conditioning operation in which conditioned air is cooled at least by the evaporator 6.

  Here, as each sensor described above, for example, as shown in FIG. 2, an inside air temperature sensor 40, an outside air temperature sensor 41, a solar radiation sensor 42, an evaporation temperature sensor 43, a water temperature sensor 44, a supercooling temperature sensor 45, etc. is there. The inside air temperature sensor 40 detects an air temperature TR in the vehicle interior (hereinafter sometimes referred to as an inside air temperature TR). The outside air temperature sensor 41 detects an air temperature TAM outside the passenger compartment (hereinafter sometimes referred to as an outside air temperature TAM). The solar radiation sensor 42 detects the solar radiation amount TS irradiated into the vehicle interior. The evaporator temperature sensor 43 detects the outer surface temperature of the evaporator 6 or the air temperature TE cooled by the evaporator 6 as the temperature of the evaporator 6. The water temperature sensor 44 detects the temperature TW of the cooling water flowing into the heater core 34, that is, the cooling water temperature TW. The supercooling temperature sensor 45 detects the outer surface temperature of the supercooling heat exchanger 4 or the air temperature TSC heated by the supercooling heat exchanger 4.

  The air conditioner ECU 50 is provided with a micro computer including a CPU, ROM, RAM, etc. (not shown), and sensor signals from the sensors 40 to 45 are A / D converted by an input circuit (not shown) in the air conditioner ECU 50. It is configured to be input to a microcomputer.

  The air conditioner ECU 50 as a control unit for controlling the vehicle air conditioner 100 operates the target device according to a procedure described later based on input signals from the switches of the operation panel 51, input signals from the sensors 40 to 45, and the like. It comes to perform control. Examples of the target device include an inside / outside air switching door 13, a blower 14, an air mix door device 17, blow-out mode doors 21 to 23, a compressor 2, and a decompression device 5. When the decompression device 5 is, for example, a refrigerant temperature temperature-sensing expansion valve device, the air conditioner ECU 50 does not control the operation of the decompression device 5.

  Next, based on the said structure, the action | operation of the vehicle air conditioner 100 of this embodiment is demonstrated. The air conditioner ECU 50 enters an operating state when the ignition switch of the vehicle is turned on, instructs the water pump 32 to start the operation, and periodically and repeatedly executes the control processing shown in the flowchart of FIG. FIG. 3 is a first flowchart showing a control process of the air conditioner ECU 50. In addition, each control step in the flowchart of each drawing comprises the various function implementation | achievement means which this vehicle air conditioner 100 has.

  As shown in FIG. 3, the air conditioner ECU 50 first initializes various settings in step S01. Next, in step S02, it is determined whether or not the operation position of the air conditioning activation switch 52 is the air conditioner on position. If it is determined in step S02 that the operation position of the air conditioning activation switch 52 is the air conditioner ON position, the process proceeds to step S03. On the other hand, if it is determined that the operation position of the air conditioning activation switch 52 is not the air conditioner ON position, the process proceeds to step S04.

  In step S03, the air conditioner operation is executed. And as one of the control processing performed by an air-conditioner driving | operation, the control processing shown in the flowchart of below-mentioned FIG. 4 is performed. When the flowchart of FIG. 4 ends, the execution step of the flowchart of FIG. 3 returns to step S02.

  In step S04 in FIG. 3, the air conditioner ECU 50 turns off the compressor 2, for example, and stops the air conditioner operation. When step S04 ends, the flowchart of FIG. 3 ends and starts again from step S01.

  FIG. 4 is a second flowchart showing a control process of the air conditioner ECU 50, and is a flowchart showing a subroutine executed in step S03 of FIG. In the flowchart of FIG. 4, the air conditioner ECU 50 first reads a switch signal from each switch of the operation panel 51 and also reads a sensor signal from each sensor 40 to 45 in step S101. Next, in step S102, a target blowing temperature TAO, which is a temperature target value of the air blown into the passenger compartment, is calculated based on an arithmetic expression stored in advance in the ROM. The target blowing temperature TAO is calculated based on, for example, the inside air temperature TR, the outside air temperature TAM, the solar radiation amount TS, and the vehicle interior set temperature Tset.

  When the target blowing temperature TAO is calculated in step S102, it is determined in step 103 whether or not it is necessary to increase the warm air ratio in order to set the blowing temperature into the vehicle interior to TAO. For example, the air conditioner ECU 50 compares the target blowing temperature TAO with the air temperature TE detected by the evaporation temperature sensor 43. If the target blowing temperature TAO is higher than the air temperature TE (TAO> TE), the warm air Judge that it is necessary to increase the air volume.

  If it is determined that the warm air ratio needs to be increased, the process proceeds to step S104, and the door 17 is controlled in the opening direction so that the opening degree of the heating passage 15 is increased.

  Further, when it is determined that the increase in the warm air ratio is not necessary, the process proceeds to step S105, and the door 17 is controlled in the closing direction so that the opening degree of the heating passage 15 is decreased.

  If control of step S105 or step S104 is implemented, it will be determined in step S106 whether heating of a cooling water is required.

  In this embodiment, when the target blowing temperature TAO is equal to or higher than the outside air temperature TAM detected by the outside air temperature sensor 41, it is determined that heating of the cooling water is necessary, and when the target blowing temperature TAO is less than the outside air temperature TAM, It is determined that heating of the cooling water is not necessary.

  Here, when the target blowing temperature TAO is lower than the outside air temperature TAM, the process proceeds to step S107, and the cooling water flowing out from the supercooling heat exchanger 4 passes through the heater core 34 without passing through the engine 30. The flow path switching valve 33 is controlled to be a closed circuit that flows into the cooling heat exchanger 4. As a result, the cooling water flowing out from the supercooling heat exchanger 4 flows into the heater core 34 through the water pump 32 without passing through the engine 30.

  In the configuration in which the cooling water flowing out from the supercooling heat exchanger 4 passes through the engine 30, the temperature of the cooling water becomes high due to the heat of the engine 30, and the temperature of the cooling water flowing out from the heater core 34 is output from the condenser 3. It may become higher than the temperature of the refrigerant. In this case, the cooling capacity and operating efficiency of the refrigeration cycle apparatus 1 are reduced.

  Here, since the cooling water flowing out from the supercooling heat exchanger 4 flows into the heater core 34 through the water pump 32 without passing through the engine 30, the cooling capacity and operating efficiency of the refrigeration cycle apparatus 1 are rather improved. It can prevent that it falls.

  When the target blowout temperature TAO is equal to or higher than the reference temperature, the process proceeds to step S108, and the cooling water that has flowed out of the supercooling heat exchanger 4 passes through the engine 30 and the heater core 34, and the supercooling heat exchanger. The flow path switching valve 33 is controlled so as to be an open circuit flowing into the circuit 4. As a result, the cooling water that has flowed out of the supercooling heat exchanger 4 is further warmed by the engine 30 and flows into the heater core 34, and the blowing temperature is quickly raised to the target blowing temperature TAO.

  According to the configuration described above, the refrigerant flows out of the condenser 3 by heat exchange between the refrigerant that is arranged outside the air conditioning duct 10, flows out of the condenser 3 and flows into the decompression device 5, and the coolant cooled by the heater core 34. Since the supercooling heat exchanger 4 that cools the refrigerant is provided, the refrigerant that flows out of the condenser 3 and flows into the decompression device 5 can be further cooled by the supercooling heat exchanger 4. Thereby, a large enthalpy difference between the refrigerant flowing into the evaporator 6 and the refrigerant flowing out of the evaporator 6 can be ensured.

  Further, the flow path switching valve 33 is controlled so that the coolant flowing out from the supercooling heat exchanger 4 flows into the supercooling heat exchanger 4 via the heater core 34 without passing through the engine 30. The flow path flowing into the subcooling heat exchanger 4 via the engine 30 and the heater core 34 can be switched.

  Further, as described above, it is determined whether or not the cooling water needs to be heated based on the target blowing temperature, and when it is determined that the cooling water does not need to be heated, the cooling water flows out from the supercooling heat exchanger 4. For example, the heat of the engine 30 is controlled by controlling the flow path switching valve 33 so that the cooled liquid becomes a flow path that flows into the supercooling heat exchanger 4 via the heater core 34 without passing through the engine 30. Thus, the temperature of the cooling water becomes high and the temperature of the cooling water flowing out of the heater core 34 becomes higher than the temperature of the refrigerant output from the condenser 3, and the cooling of the refrigeration cycle apparatus 1 is instead performed by the supercooling heat exchanger 4. It can prevent that capability and driving | operation efficiency fall.

  In addition, when it is determined that the cooling water needs to be heated, the coolant that has flowed out of the supercooling heat exchanger 4 flows into the supercooling heat exchanger 4 via the engine 30 and the heater core 34, and By controlling the flow path switching valve 33 so that the cooling water flows out from the supercooling heat exchanger 4, the cooling water is further warmed by the engine 30 and flows into the heater core 34. Raised.

  Here, the state change of the refrigerant circulating in the refrigeration cycle apparatus 1, the enthalpy difference between the refrigerant flowing into the evaporator 6 and the refrigerant flowing out of the evaporator 6, the temperature change of the conditioned air flowing in the air conditioning duct 10, etc. This will be described with reference to FIGS. FIG. 5 is a pressure-enthalpy diagram showing an example of the state of the refrigerant circulating in the refrigeration cycle apparatus 1.

  As shown in the refrigerant state in the refrigeration cycle apparatus 1 in FIG. 5, the gas-phase refrigerant whose pressure and enthalpy are increased from the PA point to the PB point due to the compression by the compressor 2 is radiated and condensed by the condenser 3. To do. Assuming that the refrigerant flowing out of the condenser 3 is in the state indicated by the PC point, if the supercooling heat exchanger 4 is ventilated through the supercooling heat exchanger 4 and heat exchange is possible, the excess The refrigerant that has flowed out of the cooling heat exchanger 4 is in a state indicated by the PD point. That is, before the pressure is reduced by the pressure reducing device 5, the enthalpy of the refrigerant is greatly reduced in the supercooling heat exchanger 4.

  Thereby, a large enthalpy difference between the refrigerant flowing into the evaporator 6 and the refrigerant flowing out of the evaporator 6, that is, the enthalpy difference between the PE point and the PA point in FIG. The cooling capacity and operation efficiency COP can be greatly improved. That is, a power saving effect can be obtained by the heat exchanger 4 for supercooling.

  For example, the cycle partially shown by the broken line L1 in FIG. 5 is the conventional example that does not include the supercooling heat exchanger 4, but the supercooling heat in this embodiment is different from the conventional example. As a result of heat exchange in the exchanger 4, the broken line L1 moves to the solid line L2, and the enthalpy difference is increased, resulting in a power saving effect.

  The refrigerant condensing temperature of the condenser 3 is, for example, 10 to 20 ° C. higher than the outside air temperature, and is about 45 to 55 ° C. when the outside air temperature is 35 ° C. When the condenser 3 is a so-called subcool condenser, the outlet refrigerant of the condenser 3 is lowered by about 10 ° C. with respect to the condensation temperature, and the refrigerant temperature at the PC point is 35 to 45 ° C. On the Mollier diagram, the condensation temperature is 50 ° C., the subcooling by the supercooling part of the condenser 3 is 10 ° C., the temperature on the evaporator 6 side is 0 ° C., and the refrigerant temperature is increased to 10 ° C. by the supercooling heat exchanger 4. When lowered, the efficiency COP of the refrigeration cycle apparatus 1 of the present embodiment is 5.99.

  On the other hand, in the above-described conventional refrigeration cycle apparatus that does not have the supercooling heat exchanger 4, the temperature of the refrigerant flowing into the decompression apparatus 5 does not become lower than the outside air temperature, so the efficiency COP of the refrigeration cycle apparatus Is 4.43. Thus, according to the refrigeration cycle apparatus 1 of the present embodiment, significant efficiency improvement is achieved. In short, in the present embodiment, the temperature of the refrigerant flowing into the decompression device 5 can be made lower than the outside air temperature by cooling the refrigerant in the supercooling heat exchanger 4, and accordingly, the refrigerant is converted into the refrigerant in the evaporator 6. The enthalpy given is increased. As a result, significant efficiency improvement of the refrigeration cycle apparatus 1 is achieved. In addition, the result regarding the above-mentioned efficiency COP is the theoretical efficiency when the refrigerant is R1234yf, the compression efficiency, and the volumetric efficiency is 1.

  FIG. 6 shows a configuration in which the supercooling heat exchanger 4 is provided in the air conditioning duct 810 as a comparative example. In the comparative example of FIG. 6, a supercooling heat exchanger 84 and a heater core 834 are arranged in a heating passage 815 provided in the air conditioning duct 810. Further, the heater core 834 is disposed on the downstream side of the air flow of the supercooling heat exchanger 84.

  In the configuration as shown in FIG. 6, the air mix door 817 is controlled so that the opening degree of the heating passage 15 decreases when the heat dissipation amount of the engine is high and the temperature of the cooling water for cooling the engine becomes high. For this reason, the air volume of the air which flows into the supercooling heat exchanger 4 decreases. As a result, the flow rate of the air heat exchanged in the supercooling heat exchanger 4 is also reduced, and the power saving effect by the supercooling heat exchanger 4 is reduced.

  On the other hand, the vehicle air conditioner 100 according to this embodiment shown in FIG. 1 flows out from the condenser 3 and flows into the decompression device 5 by the supercooling heat exchanger 4 arranged outside the air conditioning duct. Since the refrigerant is further cooled, the maximum power saving effect by the supercooling heat exchanger 4 can be obtained regardless of the amount of air flowing through the heating passage 15.

  FIG. 7 is a diagram showing the relationship between the amount of heat released from the refrigerant to the air in the supercooling heat exchanger 4 and the power saving effect of the refrigeration cycle apparatus 1. As shown in the figure, the power saving effect obtained by the supercooling heat exchanger 4 is proportional to the amount of heat released by the supercooling heat exchanger 4. That is, the greater the amount of heat dissipated in the supercooling heat exchanger 4, the greater the power saving effect obtained by the supercooling heat exchanger 4.

  Incidentally, as a temperature control device for adjusting the temperature of the cabin of an automobile, there is one described in Japanese Patent No. 4889906. This temperature control device includes a heat pump. The heat pump includes a low-temperature source including a first refrigerant / coolant heat exchanger provided in a first secondary circuit in which a liquid coolant circulates, and a second secondary circuit in which another liquid coolant circulates. A high temperature source including the second refrigerant / coolant heat exchanger provided in the compressor, a compressor that compresses the refrigerant vaporized in the low temperature source and sends the refrigerant to the high temperature source, and depressurizes the refrigerant cooled in the high temperature source, And an expansion valve that sends the refrigerant in a liquid state to a low-temperature source. And this heat pump heats the cooling water which flows through a 2nd secondary circuit using the heat of high temperature source itself containing a 2nd refrigerant | coolant / coolant heat exchanger, and performs heating.

  However, this heat pump uses the heat of the high-temperature source itself corresponding to the condenser to heat the cooling water flowing through the second secondary circuit, and the refrigerant flowing from the high-temperature source is used as the outlet temperature of the evaporator 6. Since it is not the structure which cools to the extent, the power saving effect like the vehicle air conditioner 100 in this embodiment cannot be acquired.

  On the other hand, in the vehicle air conditioner 100 according to the present embodiment, the refrigerant that flows out from the condenser 3 and flows into the pressure reducing device 5 is further cooled to about the blowing temperature of the evaporator 6 by the supercooling heat exchanger 4. Therefore, a large power saving effect can be obtained.

(Second Embodiment)
Next, a second embodiment of the present invention will be described. In the present embodiment, differences from the first embodiment will be mainly described. Further, the same or equivalent parts as those of the above-described embodiment will be described by omitting or simplifying them. The same applies to third and later embodiments described later.

  FIG. 8 is a schematic diagram showing a schematic configuration of the vehicle air conditioner 100 according to the second embodiment of the present invention. In the first embodiment, the flow path switching valve 33 is provided in the cooling water circuit 31, and the flow path switching valve 33 is controlled to switch the flow path. However, in this embodiment, the flow path switching is performed. In place of the valve 33, the cooling water circuit 31 is provided with flow path switching valves 33a and 33b as second flow path switching devices, and the flow path switching valves 33a and 33b are controlled to switch the flow paths.

  Each flow path switching valve 33a, 33b allows the cooling water flowing out from the heater core 34 to flow through the first flow path 65a passing through the supercooling heat exchanger 4 or bypassing the supercooling heat exchanger 4. Switching between the two flow paths 65b is performed. Each flow path switching valve 33a, 33b is controlled by the air conditioner ECU 50.

  The first flow path 65a is established by the flow path switching valve 33a closing the second flow path 65b and the flow path switching valve 33b closing the second flow path 65b. The second flow path 65b is a flow path switching valve. It is established when 33a closes the first flow path 65a and the flow path switching valve 33b closes the first flow path 65a. That is, the first and second flow paths 65a and 65b can be alternatively easily established by controlling the opening and closing of the flow path switching valves 33a and 33b.

  FIG. 9 shows a flowchart of the air conditioner ECU 50 according to the second embodiment of the present invention. In the present embodiment, the flowchart executed by the air conditioner ECU 50 is different from FIG. 4 which is the flowchart of the first embodiment in steps after S106. That is, in the flowchart shown in FIG. 9, steps S207 and S208 are performed instead of steps S107 and S108 in the flowchart shown in FIG.

  In the present embodiment, the air conditioner ECU 50 determines whether or not the cooling water needs to be heated in step S106. Specifically, when the target blowing temperature TAO is equal to or higher than the outside air temperature TAM detected by the outside air temperature sensor 41, it is determined that heating of the cooling water is necessary, and when the target blowing temperature TAO is less than the outside air temperature TAM, It is determined that heating of the cooling water is not necessary.

  Here, when the target blowing temperature TAO is less than the outside air temperature TAM, the flow proceeds to step S207, and each flow path switching valve 33a, 33b is caused to pass the cooling water flowing out from the heater core 34 to the supercooling heat exchanger 4. To control. Thereby, the cooling water that has flowed out of the heater core 34 flows through the first flow path 65 a that flows into the heater core 34 via the supercooling heat exchanger 4, the engine 30, and the water pump 32.

  Therefore, the supercooling heat exchanger 4 can reduce the temperature of the refrigerant flowing out of the condenser 3 below the outside air temperature, and can improve the cooling capacity and the operating efficiency of the refrigeration cycle apparatus 1.

  Further, when the target outlet temperature TAO is equal to or higher than the outside air temperature TAM, the flow proceeds to step S208, and each flow path switching valve 33a, so that the cooling water flowing out from the heater core 34 does not pass through the supercooling heat exchanger 4. 33b is controlled. Thereby, the cooling water flowing out from the heater core 34 flows through the second flow path 65b flowing into the heater core 34 via the engine 30 and the water pump 32 without passing through the supercooling heat exchanger 4. Therefore, it is possible to prevent the high-temperature cooling water from flowing into the supercooling heat exchanger 4.

  As described above, the flow path switching valves 33a and 33b are controlled so that the coolant flowing out of the heater core 34 flows into the heater core 34 via the supercooling heat exchanger 4 and the engine 30. The second flow path 65b flowing into the heater core 34 via the engine 30 without going through the supercooling heat exchanger 4 can be switched.

  Further, as described above, it is determined whether or not the cooling water needs to be heated based on the target blowing temperature, and when it is determined that the cooling water does not need to be heated, the coolant that has flowed out of the heater core 34 By controlling the flow path switching valves 33a and 33b so as to be the first flow path 65a flowing into the heater core via the supercooling heat exchanger 4 and the engine 30, for example, the cooling water is cooled by the heat of the engine 30. The temperature of the cooling water flowing out of the heater core 34 becomes higher than the temperature of the refrigerant output from the condenser 3, and the cooling capacity and operating efficiency of the refrigeration cycle apparatus 1 are instead changed by the supercooling heat exchanger 4. Can be prevented from decreasing.

  Further, when it is determined that the cooling water needs to be heated, the second flow in which the coolant flowing out from the heater core 34 flows into the heater core 34 via the engine 30 without passing through the supercooling heat exchanger 4. By controlling the flow path switching valves 33a and 33b so as to become the path 65b, the cooling water flowing out from the supercooling heat exchanger 4 is further warmed by the engine 30 and flows into the heater core 34. The temperature in the passenger compartment can be raised.

(Third embodiment)
Next, a third embodiment of the present invention will be described. FIG. 8 is a schematic diagram showing a schematic configuration of the vehicle air conditioner 100 according to the third embodiment of the present invention.

  Compared with the vehicle air conditioner 100 according to the first embodiment, the vehicle air conditioner 100 according to the third embodiment of the present invention further adjusts the flow rate of the coolant in the coolant circuit 31. And a point provided with a cooling water temperature sensor (not shown) for detecting the temperature of the cooling water flowing out from the heater core 34 and flowing into the supercooling heat exchanger 4. Different.

  The flow rate adjustment valve 35 adjusts the flow rate of the cooling water flowing in the cooling water circuit 31. The flow rate adjustment valve 35 is controlled by the air conditioner ECU 50.

  FIG. 11 shows a flowchart of the air conditioner ECU 50 according to the third embodiment of the present invention. In the present embodiment, the flowchart executed by the air conditioner ECU 50 is different from the flowchart of FIG. 4 of the first embodiment in steps after S306. That is, the flowchart shown in FIG. 11 is obtained by adding S306 to S308 after step S106 of the flowchart shown in FIG.

  In this embodiment, when the air conditioner ECU 50 controls the flow path switching valve 33 so that the switching control valve 33 becomes an open circuit in S108, the air conditioner ECU 50 flows out of the heater core 34 and flows into the supercooling heat exchanger 4 in step S306. It is determined whether or not the temperature of the cooling water to be performed is higher than the temperature of the refrigerant flowing into the supercooling heat exchanger 4. The temperature of the cooling water flowing out of the heater core 34 and flowing into the supercooling heat exchanger 4 can be detected using the above-described cooling water temperature sensor. The temperature of the refrigerant flowing into the supercooling heat exchanger 4 can be the outside air temperature TAM detected by the outside air temperature sensor.

  Here, when the temperature of the cooling water flowing out of the heater core 34 and flowing into the supercooling heat exchanger 4 is equal to or lower than the temperature of the refrigerant flowing into the supercooling heat exchanger 4, the process proceeds to S308 and the flow rate adjustment valve 35 is reached. The flow rate adjustment valve 35 is controlled so that the throttle opening is fully opened. Thereby, it is possible to circulate the cooling water having a sufficient flow rate in the cooling water circuit 31.

  On the other hand, when the temperature of the cooling water flowing out of the heater core 34 and flowing into the supercooling heat exchanger 4 is higher than the temperature of the refrigerant flowing into the supercooling heat exchanger 4, the process proceeds to S307 and the flow control valve 35 is throttled. The flow rate adjustment valve 35 is controlled so as to decrease the opening degree.

  Thereby, the speed of the cooling water moving in the heater core 34 is decreased. Then, the cooling water moving in the heater core 34 is cooled by the evaporator 6 over a relatively long time. Therefore, the temperature of the cooling water flowing out from the heater core 34 can be further lowered, and the cooling effect of the refrigerant by the supercooling heat exchanger 4 can be increased.

  As described above, the flow rate of the coolant flowing out of the heater core 34 can be adjusted by controlling the flow rate adjustment valve 35.

  Further, as described above, it is determined whether the temperature of the coolant flowing out of the heater core 34 and flowing into the supercooling heat exchanger 4 is higher than the temperature of the refrigerant flowing into the supercooling heat exchanger 4, and the heater core 34, when it is determined that the temperature of the coolant flowing out from the refrigerant 34 and flowing into the supercooling heat exchanger 4 is higher than the temperature of the refrigerant flowing into the supercooling heat exchanger 4, the flow rate of the coolant flowing out from the heater core 34 is By controlling the flow rate adjustment valve 35 so as to decrease, the speed of the cooling water moving in the heater core 34 can be decreased, and the temperature of the cooling water flowing out of the heater core 34 can be further decreased, and the supercooling heat exchanger The cooling effect of the refrigerant by 4 can be increased.

(Fourth embodiment)
Next, a fourth embodiment of the present invention will be described. In the present embodiment, differences from the first embodiment will be mainly described.

  FIG. 12 is a schematic diagram illustrating a schematic configuration of the vehicle air conditioner 100 according to the present embodiment, and corresponds to FIG. 1. As shown in FIG. 12, the configuration of the refrigerant circuit included in the refrigeration cycle apparatus 1 is different from that of the first embodiment.

  Specifically, the refrigeration cycle apparatus 1 includes a circuit switching device 54 including a first on-off valve 56 and a second on-off valve 58, and two refrigerant circuits 60 and 62 that are alternatively established by the circuit switching device 54. And have. The two refrigerant circuits 60 and 62 are a first refrigerant circuit 60 and a second refrigerant circuit 62, and the first refrigerant circuit 60 is configured to exchange heat between the refrigerant discharged from the compressor 2 and the condenser 3. It is a refrigerant circuit which returns to the compressor 2 through the compressor 4, the decompression device 5, and the evaporator 6 in order. That is, it is the same as the refrigerant circuit configured by the refrigeration cycle apparatus 1 of the first embodiment. In FIG. 12, the refrigerant flow in the first refrigerant circuit 60 is indicated by a solid line arrow FL1, and the refrigerant flow in the second refrigerant circuit 62 is indicated by a broken line arrow FL2.

  The second refrigerant circuit 62 is a refrigerant circuit in which the high-temperature and high-pressure refrigerant discharged from the compressor 2 is introduced into the supercooling heat exchanger 4 without passing through the condenser 3. Specifically, the second refrigerant circuit 62 includes a first bypass refrigerant passage 63 and a second bypass refrigerant passage 64 branched from the refrigerant pipe 9. The first bypass refrigerant passage 63 is a refrigerant passage through which the refrigerant discharged from the compressor 2 bypasses the condenser 3 and flows to the supercooling heat exchanger 4. The second bypass refrigerant passage 64 is a refrigerant passage through which the refrigerant flowing out from the supercooling heat exchanger 4 flows to the compressor 2 bypassing the decompression device 5 and the evaporator 6.

  And the refrigerating-cycle apparatus 1 of this embodiment has the decompression device 66 for heating, and the gas-liquid separator 68 further compared with 1st Embodiment. The heating decompression device 66 is an electric expansion valve controlled by the air conditioner ECU 50, and is provided in the second bypass refrigerant passage 64 and decompresses the refrigerant that has flowed out of the supercooling heat exchanger 4. The gas-liquid separator 68 is provided in the second bypass refrigerant passage 64 and separates the refrigerant flowing out from the heating decompression device 66 into a gas phase and a liquid phase, and stores the liquid phase refrigerant therein to store the gas phase The refrigerant flows into the compressor 2.

  The first on-off valve 56 and the second on-off valve 58 included in the circuit switching device 54 are both electromagnetic on-off valves that are controlled to open and close by the air conditioner ECU 50. The first on-off valve 56 is provided in the first bypass refrigerant passage 63 and opens and closes the first bypass refrigerant passage 63. The second on-off valve 58 is provided in the second bypass refrigerant passage 64 and opens and closes the second bypass refrigerant passage 64.

  The first refrigerant circuit 60 is established when the first on-off valve 56 closes the first bypass refrigerant passage 63 and the second on-off valve 58 closes the second bypass refrigerant passage 64. On the other hand, the second refrigerant circuit 62 is established when the first on-off valve 56 opens the first bypass refrigerant passage 63 and the second on-off valve 58 opens the second bypass refrigerant passage 64. As described above, the circuit switching device 54 alternatively establishes the first refrigerant circuit 60 and the second refrigerant circuit 62.

  Note that when the second refrigerant circuit 62 is established, the flow resistance of the refrigerant flowing through the first bypass refrigerant passage 63 is much smaller than the flow resistance of the condenser 3, so that the condenser 3 is not actively blocked. However, the refrigerant discharged from the compressor 2 does not flow to the condenser 3 but flows exclusively to the first bypass refrigerant passage 63. Similarly, the refrigerant that has flowed out of the supercooling heat exchanger 4 does not flow to the evaporator 6 having a flow resistance higher than that of the second bypass refrigerant passage 64, but flows exclusively to the second bypass refrigerant passage 64.

  In the second refrigerant circuit 62, the refrigerant discharged from the compressor 2 passes through the first on-off valve 56, the supercooling heat exchanger 4, the second on-off valve 58, the heating decompression device 66, and the gas-liquid separator 68. And the process returns to the compressor 2 in order.

  Although the air conditioning activation switch 52 shown in FIG. 2 is also provided in this embodiment, unlike the first embodiment, it can be switched to one of three operation positions. Specifically, the air conditioning activation switch 52 according to the present embodiment includes an air conditioner on position that activates the air conditioning operation, a heating on position that activates the heating operation, and an air conditioning off position that stops both the air conditioning operation and the heating operation. It can be switched to one of the two operation positions. The heating operation is an air-conditioning operation in which air-conditioned air is heated and blown out into the passenger compartment without cooling the air-conditioned air by the evaporator 6. Therefore, the refrigerant of the refrigeration cycle apparatus 1 does not flow to the evaporator 6 during the heating operation.

  Next, based on the said structure, the action | operation of the vehicle air conditioner 100 of this embodiment is demonstrated. The air conditioner ECU 50 enters an operating state when the ignition switch of the vehicle is turned on, instructs the water pump 32 to start the operation, and periodically and repeatedly executes the control processing shown in the flowchart of FIG. FIG. 13 is a first flowchart showing a control process of the air conditioner ECU 50 of the present embodiment. In FIG. 13, steps having the same contents as those in FIG. 3 are denoted by the same reference numerals and description thereof is omitted.

  As shown in the flowchart of FIG. 13, if the air conditioner ECU 50 determines in step S02 that the operation position of the air conditioner activation switch 52 is the air conditioner on position, the process proceeds to step S13. On the other hand, if it is determined that the operation position of the air conditioning activation switch 52 is not the air conditioner ON position, the process proceeds to step S14.

  In step S13, the first on-off valve 56 is closed and the second on-off valve 58 is also closed. Thereby, the 1st refrigerant circuit 60 which is a refrigerant circuit for air-conditioner operation is materialized. If the first on-off valve 56 and the second on-off valve 58 are already closed, the closed state is continued. After step S13, the process proceeds to step S03. In step S03, the air conditioner operation is executed as in the first embodiment, and the flowchart of FIG. 4 is executed.

  In step S14, it is determined whether or not the operating position of the air conditioning activation switch 52 is the heating on position. If it is determined in step S14 that the operation position of the air conditioning activation switch 52 is the heating on position, the process proceeds to step S15. On the other hand, if it is determined that the operation position of the air conditioning activation switch 52 is not the heating on position, the process proceeds to step S16.

  In step S15, the heating operation is executed. Therefore, the air conditioner ECU 50 operates the air mix door device 17 so that air flows to the heater core 34 in the air conditioning duct 10. Specifically, the heating passage 15 is fully opened. If the heating passage 15 is already fully open, the state is continued. As a result, the conditioned air is blown into the passenger compartment after passing through the heater core 34.

  And in step S15, air-conditioner ECU50 performs the control process shown to the below-mentioned flowchart of FIG. 14 as one of the control processes performed by heating operation. When the flowchart of FIG. 14 ends, the execution step of the flowchart of FIG. 13 returns to step S02.

  In step S16 of FIG. 13, the air conditioner ECU 50 stops the air conditioner operation and the heating operation. When step S16 ends, the flowchart of FIG. 13 ends and starts again from step S01.

  FIG. 14 is a second flowchart showing a control process of the air conditioner ECU 50 of the present embodiment, and is a flowchart showing a subroutine executed in step S15 of FIG. Further, in FIG. 14, steps having the same contents as those in FIG.

  In the flowchart of FIG. 14, the air conditioner ECU 50 sequentially executes steps S101 and S102 as in the first embodiment. After calculating the target blowout temperature TAO in step S102, the process proceeds to step S203.

  In step S203, it is determined whether or not it is necessary to further increase the amount of heating to the conditioned air in order to set the temperature of the air blown into the passenger compartment to the target air temperature TAO. For example, the air conditioner ECU 50 compares the target blowing temperature TAO with the cooling water temperature TW detected by the water temperature sensor 44 (see FIG. 2), and when the target blowing temperature TAO is higher than the cooling water temperature TW (TAO> TW). Determines that it is necessary to further increase the heating amount for the conditioned air.

  If it is determined in step S203 that the heating amount for the conditioned air needs to be further increased, that is, if the target outlet temperature TAO is higher than the cooling water temperature TW, the process proceeds to step S204. On the other hand, when it is determined that it is not necessary to further increase the heating amount for the conditioned air, that is, when the target blowing temperature TAO is equal to or lower than the cooling water temperature TW, the process proceeds to step S205.

  In step S204, the first on-off valve 56 is opened and the second on-off valve 58 is also opened. Thereby, the 2nd refrigerant circuit 62 which is a refrigerant circuit for heating operation is materialized. If the first on-off valve 56 and the second on-off valve 58 have already been opened, the opened state is continued.

  Then, the compressor 2 is turned on. That is, the compressor 2 is driven. Further, the flow path switching valve 33 is controlled so that the cooling water flowing out from the heater core 34 becomes an open circuit again flowing into the heater core 34 via the supercooling heat exchanger 4 and the engine 30. At this time, the high-temperature and high-pressure refrigerant compressed by the compressor 2 is introduced into the supercooling heat exchanger 4, and the cooling water flowing out from the heater core 34 is heated by the supercooling heat exchanger 4, and then the engine Heat at 30. Then, the air flowing through the heating passage 102 is quickly heated via the cooling water flowing into the heater core 34 and blown out into the passenger compartment.

  In this manner, the air conditioner ECU 50 operates the air mix door device 17 so that air flows to the heater core 34 in the air conditioning duct 10 (see step S15 in FIG. 13) and establishes the second refrigerant circuit 62 by the circuit switching device 54. By doing so, the vehicle interior is heated.

  In step S205, the air in the air conditioning duct 10 is heated by the heater core 34. Therefore, in step S205, the compressor 2 is turned off. That is, the compressor 2 is stopped. Further, the flow path switching valve 33 is controlled so that the cooling water flowing out from the heater core 34 becomes an open circuit again flowing into the heater core 34 via the supercooling heat exchanger 4 and the engine 30. Thereby, the heat exchanger 4 for supercooling stops functioning. That is, the air flowing through the heating passage 102 is heated by using the heat of the cooling water heated by the engine 30 and blown out into the passenger compartment.

  Further, in steps S204 and S205, the air conditioner ECU 50 causes the temperature of the air blown into the vehicle interior to approach the target air temperature TAO based on input information from the EVA temperature sensor 43, the water temperature sensor 44, and the supercooling temperature sensor 45. In addition, the first door 171 is operated to adjust the opening degree of the cold air bypass passage 101.

  When step S204 or S205 is executed, the control process executed by the air conditioner ECU 50 returns to the flowchart of FIG. 13 and starts again from step S02 of FIG. Further, during the heating operation in the control processing of FIGS. 13 and 14, the air conditioner ECU 50 performs the air volume of the blower 14, the inside / outside air inlet mode, and the outlet mode, as in the air conditioner operation in the first embodiment. Also decide. The air conditioner ECU 50 then converts the inside / outside air switching door 13, the blower 14, the air mix door device 17, the blowing mode doors 21 to 23, and the compression so that the control states calculated or determined during the execution of the control process described above are obtained. A control signal is output to the machine 2 or the like.

  In the present embodiment, the effects produced from the configuration common to the first embodiment described above can be obtained as in the first embodiment. Furthermore, according to the present embodiment, the refrigeration cycle apparatus 1 allows the refrigerant discharged from the compressor 2 to pass through the condenser 3, the supercooling heat exchanger 4, the decompression device 5, and the evaporator 6 in order to the compressor 2. The first refrigerant circuit 60 returning, the second refrigerant circuit 62 in which the refrigerant discharged from the compressor 2 is introduced into the supercooling heat exchanger 4 without passing through the condenser 3, the first refrigerant circuit 1 and the second refrigerant. A circuit switching device 54 that alternatively establishes the circuit 62 is provided. The air conditioner ECU 50 controls the circuit switching device 54 so as to establish the first refrigerant circuit 61 during the air conditioner operation and perform cooling, and during the heating operation establish the second refrigerant circuit 62 and perform heating, thereby controlling the vehicle. Heat the room. That is, not only the heat of the cooling water warmed by the engine 30 in the heating operation in which the conditioned air is not cooled by the evaporator 6 but also discharged from the compressor 2 and enters the supercooling heat exchanger 4 without passing through the condenser 3. The conditioned air can be heated using the heat of the refrigerant.

  Here, the relationship between the target blowing temperature TAO and the cooling water temperature TW of the engine 30 required to achieve the target blowing temperature TAO in the heating operation (hereinafter referred to as the required engine cooling water temperature TWn) is indicated by a solid line L5 in FIG. become that way. That is, as shown in FIG. 15, the required engine coolant temperature TWn becomes higher as the target outlet temperature TAO becomes higher. And when the target blowing temperature TAO becomes high until the required engine cooling water temperature TWn exceeds the cooling water temperature TW necessary for vehicle travel, if the conditioned air cannot be heated by the supercooling heat exchanger 4, for example, FIG. As shown in FIG. 15, it is necessary to cause the engine 30 to perform extra work and increase the cooling water temperature TW when the vehicle is running.

  On the other hand, in the present embodiment, as described above, not only the heat of the cooling water heated by the engine 30 but also the refrigerant discharged from the compressor 2 and entering the supercooling heat exchanger 4 without passing through the condenser 3. Therefore, the refrigeration cycle apparatus 1 can assist the amount of heat for heating the conditioned air and prevent the engine 30 from performing extra work. is there. As a result, it is possible to suppress deterioration in fuel consumption of the vehicle due to heating operation. That is, not only the power saving effect at the time of the reheat operation described in the first embodiment, but also the fuel saving effect is obtained by causing the supercooling heat exchanger 4 to function as an auxiliary heat source during the heating operation which is an air conditioning operation in winter. Therefore, the effect of the heat exchanger 4 for supercooling can be obtained throughout the year.

  In addition, although this embodiment is embodiment based on 1st Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3 embodiment.

(Fifth embodiment)
Next, a fifth embodiment of the present invention will be described. In the present embodiment, differences from the above-described fourth embodiment will be mainly described.

  16 and 17 are diagrams showing the refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the present embodiment. In FIG. 16, the flow path of the refrigerant constituting the first refrigerant circuit 60 is represented by a solid line, and the flow path of the refrigerant removed from the first refrigerant circuit 60 is represented by a broken line. On the other hand, in FIG. 17, the flow path of the refrigerant constituting the second refrigerant circuit 62 is represented by a solid line, and the flow path of the refrigerant removed from the second refrigerant circuit 62 is represented by a broken line.

  As shown in FIGS. 16 and 17, the present embodiment is different from the above-described fourth embodiment in that the refrigeration cycle apparatus 1 has a refrigerant heater 70. The refrigerant heater 70 is interposed between the heating decompressor 66 and the gas-liquid separator 68 in the second bypass refrigerant passage 64. Then, the refrigerant heater 70 heat-exchanges the refrigerant flowing out from the heating decompression device 66 with a heat medium having engine waste heat or exhaust heat of the engine 30, thereby heating the refrigerant.

  Note that the decompression device 5 of the present embodiment decompresses and expands the refrigerant at the refrigerant inlet of the evaporator 6 as in the fourth embodiment. The decompression device 5 of the present embodiment may be the same as that of the fourth embodiment, but is a refrigerant temperature-sensitive expansion valve device that is not controlled by the air conditioner ECU 50. The same applies to the sixth to ninth embodiments described later.

  In this embodiment, the effect produced from the configuration common to the above-described fourth embodiment can be obtained in the same manner as in the fourth embodiment. Further, according to the present embodiment, the refrigeration cycle apparatus 1 has the refrigerant heater 70 interposed between the heating decompression device 66 and the gas-liquid separator 68 in the second bypass refrigerant passage 64. Therefore, it is possible to perform the heating operation with the refrigeration cycle apparatus 1 more efficiently than in the fourth embodiment.

  In addition, although this embodiment is embodiment based on 4th Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3 embodiment.

(Sixth embodiment)
Next, a sixth embodiment of the present invention will be described. In the present embodiment, differences from the fifth embodiment will be mainly described.

  18 and 19 are diagrams showing a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the present embodiment. In FIG. 18, the flow path of the refrigerant constituting the first refrigerant circuit 60 is represented by a solid line, and the flow path of the refrigerant removed from the first refrigerant circuit 60 is represented by a broken line. On the other hand, in FIG. 19, the flow path of the refrigerant constituting the second refrigerant circuit 62 is represented by a solid line, and the flow path of the refrigerant removed from the second refrigerant circuit 62 is represented by a broken line.

  As shown in FIGS. 18 and 19, in the present embodiment, the refrigerant circuit configuration of the refrigeration cycle apparatus 1 is different from that of the fifth embodiment described above. Specifically, the refrigerant pipe 9 of the refrigeration cycle apparatus 1 includes a first branch point 9 a provided between the refrigerant discharge port 2 b of the compressor 2 and the condenser 3, a supercooling heat exchanger 4, and a reduced pressure. It has a second branch point 9 b provided between the refrigerant inlet 5 a of the device 5 and a third branch point 9 c provided between the first branch point 9 a and the condenser 3.

  Further, the second refrigerant circuit 62 connects the first bypass refrigerant passage 71 that connects the first branch point 9a and the second branch point 9b to each other, the third branch point 9c, and the refrigerant inlet 2a of the compressor 2 to each other. And a second bypass refrigerant passage 72 to be connected. The first bypass refrigerant passage 71 of this embodiment is replaced with the first bypass refrigerant passage 63 of the fifth embodiment, and the second bypass refrigerant passage 72 of this embodiment is the second bypass refrigerant passage 64 of the fifth embodiment. Is an alternative.

  Further, the refrigeration cycle apparatus 1 of the present embodiment includes a heating decompression device 66 and a gas-liquid separator 68 as in the fifth embodiment. However, the heating decompression device 66 is provided between the condenser 3 and the supercooling heat exchanger 4 on the refrigerant pipe 9. The gas-liquid separator 68 is provided in the second bypass refrigerant passage 72, separates the refrigerant flowing out from the third branch point 9c into a gas phase and a liquid phase, and converts the gas phase refrigerant into the refrigerant inlet 2a of the compressor 2. To flow.

  The circuit switching device 54 has a first on-off valve 56 (hereinafter simply referred to as on-off valve 56 in the present embodiment), and has a switching valve 73 instead of the second on-off valve 58 of the fifth embodiment. doing. The on-off valve 56 of the present embodiment is provided in the first bypass refrigerant passage 71 and opens and closes the first bypass refrigerant passage 71. The switching valve 73 is an electromagnetic three-way valve that is switched and controlled by the air conditioner ECU 50, and is provided at the third branch point 9c. Then, the switching valve 73 selectively connects the condenser 3 to the second bypass refrigerant passage 72 and the first branch point 9a.

  With such a configuration of the refrigeration cycle apparatus 1, the first refrigerant circuit 60 is established when the on-off valve 56 closes the first bypass refrigerant passage 71 and the switching valve 73 communicates the condenser 3 with the first branch point 9 a. To do. In the first refrigerant circuit 60, the refrigerant discharged from the compressor 2 passes through the switching valve 73, the condenser 3, the heating decompression device 66, the supercooling heat exchanger 4, the decompression device 5, and the evaporator 6. To the compressor 2 in order. At this time, the heating decompression device 66 is fully opened, and the refrigerant flows into the supercooling heat exchanger 4 without decompressing. Further, the condenser 3 condenses the refrigerant when the first refrigerant circuit 60 is established.

  On the other hand, the second refrigerant circuit 62 is established when the on-off valve 56 opens the first bypass refrigerant passage 71 and the switching valve 73 communicates the condenser 3 with the second bypass refrigerant passage 72. In the second refrigerant circuit 62, the refrigerant discharged from the compressor 2 is supplied from the on-off valve 56, the supercooling heat exchanger 4, the heating decompression device 66, the condenser 3, the switching valve 73, and the gas-liquid separator. 68, and then returns to the compressor 2. At this time, the throttle opening degree of the heating decompression device 66 is controlled by the air conditioner ECU 50, and the heating decompression device 66 decompresses the refrigerant flowing from the supercooling heat exchanger 4 to the condenser 3. The condenser 3 functions as an evaporator when the second refrigerant circuit 62 is established, and evaporates the refrigerant.

  In the present embodiment, the same effects as those of the fifth embodiment described above can be obtained as in the fifth embodiment.

  In addition, although this embodiment is embodiment based on 6th Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3rd embodiment.

(Seventh embodiment)
Next, a seventh embodiment of the present invention will be described. In the present embodiment, differences from the above-described sixth embodiment will be mainly described.

  20 and 21 are diagrams showing a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the present embodiment. In FIG. 20, the flow path of the refrigerant constituting the first refrigerant circuit 60 is represented by a solid line, and the flow path of the refrigerant removed from the first refrigerant circuit 60 is represented by a broken line. On the other hand, in FIG. 21, the flow path of the refrigerant constituting the second refrigerant circuit 62 is represented by a solid line, and the flow path of the refrigerant removed from the second refrigerant circuit 62 is represented by a broken line.

  As shown in FIGS. 20 and 21, in the present embodiment, the refrigerant circuit configuration of the refrigeration cycle apparatus 1 is different from that of the sixth embodiment described above. Specifically, the refrigerant pipe 9 of the refrigeration cycle apparatus 1 includes a first branch point 9 a provided between the refrigerant discharge port 2 b of the compressor 2 and the condenser 3, and a refrigerant outlet 6 a of the evaporator 6. A second branch point 9d provided between the refrigerant inlet 2a of the compressor 2 and a third branch point 9c provided between the first branch point 9a and the condenser 3 are provided.

  Further, the second refrigerant circuit 62 connects the first bypass refrigerant passage 77 that connects the first branch point 9a and the second branch point 9d to each other, the third branch point 9c, and the refrigerant inlet 2a of the compressor 2 to each other. A second bypass refrigerant passage 72 to be connected and a third bypass refrigerant passage 78 that is connected in parallel to the decompression device 5 and the evaporator 6 and flows the refrigerant by bypassing the decompression device 5 and the evaporator 6 are configured. ing. The first bypass refrigerant passage 77 of the present embodiment is an alternative to the first bypass refrigerant passage 71 of the sixth embodiment.

  The circuit switching device 54 includes a first switching valve 791, a second switching valve 792, and an opening / closing valve 793, instead of the opening / closing valve 56 and the switching valve 73 of the sixth embodiment. The first switching valve 791 is an electromagnetic three-way valve that is switch-controlled by the air conditioner ECU 50, and is provided in the refrigerant suction port 2 a of the compressor 2. The first switching valve 791 selectively connects the refrigerant suction port 2a of the compressor 2 to the second bypass refrigerant passage 72 and the second branch point 9d.

  The second switching valve 792 is an electromagnetic three-way valve that is switch-controlled by the air conditioner ECU 50, and is provided at the first branch point 9a. The second switching valve 792 selectively connects the refrigerant discharge port 2b of the compressor 2 to the first bypass refrigerant passage 77 and the third branch point 9c.

  The on-off valve 793 is an electromagnetic on-off valve that is controlled to open and close by the air conditioner ECU 50. The on-off valve 793 is provided in the third bypass refrigerant passage 78 and opens and closes the third bypass refrigerant passage 78.

  With such a configuration of the refrigeration cycle apparatus 1, in the first refrigerant circuit 60, the first switching valve 791 connects the refrigerant suction port 2a of the compressor 2 to the second branch point 9d, and the second switching valve 792 is the compressor. The second refrigerant discharge port 2b communicates with the third branch point 9c, and the on-off valve 793 closes the third bypass refrigerant passage 78. In the first refrigerant circuit 60, the refrigerant discharged from the compressor 2 is the second switching valve 792, the condenser 3, the heating decompression device 66, the supercooling heat exchanger 4, the decompression device 5, and the evaporator. 6 and the first switching valve 791 are returned to the compressor 2 in order.

  On the other hand, in the second refrigerant circuit 62, the first switching valve 791 connects the refrigerant inlet 2a of the compressor 2 to the second bypass refrigerant passage 72, and the second switching valve 792 is the refrigerant outlet 2b of the compressor 2. Is established by connecting the first bypass refrigerant passage 77 to the first bypass refrigerant passage 77 and the on-off valve 793 opening the third bypass refrigerant passage 78. In the second refrigerant circuit 62, the refrigerant discharged from the compressor 2 includes the second switching valve 792, the on-off valve 793, the supercooling heat exchanger 4, the heating decompression device 66, the condenser 3, and the gas-liquid. It returns to the compressor 2 through the separator 68 and the 1st switching valve 791 in order. The operation of the heating decompression device 66 and the condenser 3 when the first refrigerant circuit 60 is established and when the second refrigerant circuit 62 is established is the same as that of the sixth embodiment.

  In the present embodiment, the same effects as those of the sixth embodiment described above can be obtained in the same manner as the sixth embodiment.

  In addition, although this embodiment is embodiment based on 6th Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3rd embodiment.

(Eighth embodiment)
Next, an eighth embodiment of the present invention will be described. In the present embodiment, differences from the above-described seventh embodiment will be mainly described.

  22 and 23 are diagrams showing a refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the present embodiment. In FIG. 22, the flow path of the refrigerant constituting the first refrigerant circuit 60 is represented by a solid line, and the flow path of the refrigerant removed from the first refrigerant circuit 60 is represented by a broken line. On the other hand, in FIG. 23, the flow path of the refrigerant constituting the second refrigerant circuit 62 is represented by a solid line, and the flow path of the refrigerant removed from the second refrigerant circuit 62 is represented by a broken line.

  As shown in FIGS. 22 and 23, the present embodiment is different from the seventh embodiment in the configuration of the refrigerant circuit and the cooling water circuit of the refrigeration cycle apparatus 1.

  The cooling water circuit 31 in the present embodiment is provided with a second heat exchanger 4a and a flow path switching valve 33a. The second heat exchanger 4a is provided outside the vehicle air conditioning unit, such as an engine room.

  The flow path switching valve 33a is controlled by the air conditioner ECU 50, and selectively switches the connection port 34a provided in the heater core 34 between the connection port 34b and the second heat exchanger 4a. In addition, the heater core 34 in this embodiment has four connection ports 34a to 34d, the cooling water flowing in from the connection port 34a flows out from the connection port 34c, and the cooling water flowing in from the connection port 34d is connected to the connection port. It flows out from 34b.

  When the passage switching valve 33a communicates with the two connection ports 34a and 34b provided in the heater core 34, the coolant flowing out from the connection port 34b of the heater core 34 passes through the passage switching valve 33a and the heater core 34. Into the connection port 34a. Further, the coolant flowing out from the connection port 34 c of the heater core 34 flows into the connection port 34 d of the heater core 34 via the supercooling heat exchanger 4 and the water pump 32.

  Further, when the connection port 34a provided in the heater core 34 and the second heat exchanger 4a communicate with each other by the flow path switching valve 33a, the coolant flowing out from the second heat exchanger 4a is transferred to the connection port 34a of the heater core 34. Flow into. Further, the coolant flowing out from the connection port 34 c of the heater core 34 flows into the connection port 34 d of the heater core 34 via the supercooling heat exchanger 4 and the water pump 32. Further, the coolant flowing out from the connection port 34b of the heater core 34 flows into the engine (not shown) and flows into the second heat exchanger 4a.

  In the present embodiment, the air conditioner ECU 50 controls the flow path switching valve 33a so as to communicate with the two connection ports 34a, 34b provided in the heater core 34 during the cooling operation, and the second heat during the heating operation. The flow path switching valve 33a is controlled so as to communicate between the exchanger 4a and the connection port 34a of the heater core 34.

  Further, the refrigeration cycle apparatus 1 of the present embodiment includes a decompression device 66a. The decompression device 66a decompresses and expands the refrigerant that has flowed out of the second heat exchanger 4a.

  The second refrigerant circuit 62 in the present embodiment is provided with an on-off valve 56a, a gas-liquid separator 68, and a switching valve 794. The on-off valve 56 a is provided in the second refrigerant passage 62 and opens and closes the second refrigerant passage 62. The gas-liquid separator 68 separates the refrigerant flowing out of the condenser 3 into a gas phase and a liquid phase, and flows the gas phase refrigerant to the refrigerant suction port 2 a of the compressor 2. The switching valve 794 is an electromagnetic three-way valve that is switched and controlled by the air conditioner ECU 50, and selectively connects the refrigerant inlet 21 a of the compressor 2 to the first refrigerant circuit 60 and the second refrigerant circuit 62.

  With such a configuration of the refrigeration cycle apparatus 1, the first refrigerant circuit 60 is established when the switching valve 794 communicates the refrigerant inlet 21 a of the compressor 2 with the refrigerant outlet 6 a of the evaporator 6. In the first refrigerant circuit 60, the refrigerant discharged from the compressor 2 is switched between the second heat exchanger 4a, the decompression device 66a, the condenser 3, the supercooling heat exchanger 4, the decompression device 5, and the evaporator 6. It returns to the compressor 2 through the valve 794 in order.

  On the other hand, the second refrigerant circuit 62 is established when the switching valve 794 communicates the refrigerant inlet 21a of the compressor 2 with the gas-liquid separator 68, and the second refrigerant circuit 62 is compressed by the switching valve 794. This is established by communicating the refrigerant inlet 21 a of the machine 2 with the gas-liquid separator 68. Then, in the second refrigerant circuit 62, the refrigerant discharged from the compressor 2 passes through the second heat exchanger 4a, the pressure reducing device 66a, the condenser 3, the on-off valve 56a, the gas-liquid separator 68, and the switching valve 794 in order. After that, it returns to the compressor 2.

  In the present embodiment, during the cooling operation, the flow path switching valve 33a is controlled to communicate between the two connection ports 34a and 34b provided in the heater core 34. Therefore, the temperature rise of the cooling water flowing through the supercooling heat exchanger 4 can be suppressed.

  Further, during the heating operation, the flow path switching valve 33a is controlled so that the second heat exchanger 4a communicates with the connection port 34a of the heater core 34. That is, the cooling water flowing into the heater core 34 is warmed not only by the heat of the engine but also by the second heat exchanger 4a. Therefore, it is possible to quickly increase the passenger compartment temperature.

  In the present embodiment, the same effects as those of the sixth embodiment described above can be obtained in the same manner as the sixth embodiment.

  In addition, although this embodiment is embodiment based on 6th Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3rd embodiment.

(Ninth embodiment)
Next, a ninth embodiment of the present invention will be described. In the present embodiment, differences from the above-described sixth embodiment will be mainly described.

  24 and 25 are diagrams showing the refrigerant circuit configuration of the refrigeration cycle apparatus 1 in the present embodiment. In FIG. 24, the flow path of the refrigerant constituting the first refrigerant circuit 60 is represented by a solid line, and the flow path of the refrigerant removed from the first refrigerant circuit 60 is represented by a broken line. On the other hand, in FIG. 25, the flow path of the refrigerant constituting the second refrigerant circuit 62 is represented by a solid line, and the flow path of the refrigerant removed from the second refrigerant circuit 62 is represented by a broken line.

  As shown in FIGS. 24 and 25, in this embodiment, the refrigerant circuit configuration of the refrigeration cycle apparatus 1 is different from that in the sixth embodiment. Specifically, the first branch point 9a and the third branch point 9c provided in the refrigerant pipe 9 of the refrigeration cycle apparatus 1 are arranged in the same manner as in the sixth embodiment, but the second branch point 9b is the sixth branch point 9b. Unlike the embodiment, it is disposed between the condenser 3 and the subcooling heat exchanger 4.

  Further, the second refrigerant circuit 62 connects the first bypass refrigerant passage 74 that connects the first branch point 9a and the second branch point 9b to each other, the third branch point 9c, and the refrigerant inlet 2a of the compressor 2 to each other. And a second bypass refrigerant passage 72 to be connected. The first bypass refrigerant passage 74 of the present embodiment replaces the first bypass refrigerant passage 71 of the sixth embodiment.

  Moreover, the refrigerating cycle apparatus 1 of this embodiment has the heating pressure-reduction apparatus 66 and the gas-liquid separator 68 similarly to 6th Embodiment. However, the heating decompression device 66 is provided in the first bypass refrigerant passage 74. The arrangement of the gas-liquid separator 68 is the same as in the sixth embodiment.

  Furthermore, the refrigeration cycle apparatus 1 has a heat exchanger 75 for heating. The heating heat exchanger 75 is disposed between the first branch point 9 a and the heating decompression device 66 in the first bypass refrigerant passage 74. That is, the first bypass refrigerant passage 74 is disposed upstream of the refrigerant flow with respect to the heating decompression device 66. Accordingly, the heating decompression device 66 decompresses the refrigerant flowing out of the heating heat exchanger 75 under the control of the air conditioner ECU 50.

  The heating heat exchanger 75 is a water-refrigerant heat exchanger, and exchanges heat between the cooling water as the heat medium flowing into the heater core 34 and the refrigerant flowing through the first bypass refrigerant passage 74, thereby the heater core. The cooling water flowing into 34 is heated.

  The circuit switching device 54 has a switching valve 73 (hereinafter referred to as the first switching valve 73 in the present embodiment) similar to that of the sixth embodiment, and is replaced with the on-off valve 56 of the sixth embodiment. A second switching valve 76 is provided. The second switching valve 76 is an electromagnetic three-way valve that is switch-controlled by the air conditioner ECU 50, and is provided in the refrigerant suction port 2 a of the compressor 2. The second switching valve 76 selectively communicates the refrigerant suction port 2 a of the compressor 2 with the second bypass refrigerant passage 72 and the evaporator 6.

  With such a configuration of the refrigeration cycle apparatus 1, the first refrigerant circuit 60 is configured such that the first switching valve 73 communicates the condenser 3 with the first branch point 9 a and the second switching valve 76 is the refrigerant inlet of the compressor 2. It is established by connecting 2a to the evaporator 6. In the first refrigerant circuit 60, the refrigerant discharged from the compressor 2 is the first switching valve 73, the condenser 3, the supercooling heat exchanger 4, the decompression device 5, the evaporator 6, and the second switching valve. The sequence returns to the compressor 2 through 76. When the first refrigerant circuit 60 is established, the condenser 3 condenses the refrigerant.

  On the other hand, in the second refrigerant circuit 62, the first switching valve 73 communicates the condenser 3 with the second bypass refrigerant passage 72, and the second switching valve 76 connects the refrigerant inlet 2a of the compressor 2 to the second bypass refrigerant. This is established by communicating with the passage 72. In the second refrigerant circuit 62, the refrigerant discharged from the compressor 2 is supplied to the heating heat exchanger 75, the heating decompressor 66, the condenser 3, the first switching valve 73, the gas-liquid separator 68, and the second refrigerant circuit 62. It returns to the compressor 2 through the 2 switching valve 76 in order. At this time, the throttle opening degree of the heating decompression device 66 is controlled by the air conditioner ECU 50, and the heating decompression device 66 decompresses the refrigerant flowing from the heating heat exchanger 75 to the condenser 3. The condenser 3 functions as an evaporator when the second refrigerant circuit 62 is established, and evaporates the refrigerant.

  In addition, the air conditioner ECU 50 of the present embodiment may establish the second refrigerant circuit 62 when performing the heating operation, and when the second refrigerant circuit 62 is established, as shown in FIG. Although the refrigerant does not circulate to the container 4, the air conditioner ECU 50 executes the control processing shown in the flowcharts of FIGS. 13 and 14 in the same manner as in the sixth embodiment. Accordingly, the air conditioner ECU 50 heats the vehicle interior by operating the air mix door device 17 so that air flows to the heater core 34 in the air conditioning duct 10 and establishing the second refrigerant circuit 62 by the circuit switching device 54. .

  Specifically, the refrigeration cycle apparatus 1 indirectly heats the air flowing in the air conditioning duct 10 through the cooling water of the heater core 34 by heating the cooling water flowing into the heater core 34 with the engine 30.

  In the present embodiment, the same effects as those of the sixth embodiment described above can be obtained in the same manner as the sixth embodiment.

  In addition, although this embodiment is embodiment based on 6th Embodiment, it is also possible to combine this embodiment with either of the above-mentioned 2nd-3rd embodiment.

(Other embodiments)
(1) In the above-described embodiment, the engine 30 mounted on the vehicle is a heat generating device. However, a traveling electric motor mounted on a hybrid vehicle or an electric vehicle may be a heat generating device. In addition, a power storage device that supplies power to the electric motor, a drive circuit unit that controls driving of the electric motor, and the like can be used as heat generating devices.

  (2) In the first to third embodiments, in S106, it is determined that the cooling water needs to be heated when the target blowing temperature TAO is equal to or higher than the outside air temperature TAM. When the temperature TAO is equal to or higher than the temperature of the refrigerant output from the condenser 3, it can be determined that the cooling water needs to be heated. Moreover, when the target blowing temperature TAO is equal to or higher than the air temperature TSC heated by the supercooling heat exchanger 4, it can be determined that the cooling water needs to be heated.

  (3) In each of the above-described embodiments, the processing of each step shown in the flowcharts of FIGS. 3, 4, 9, and 11 is realized by a computer program, but is configured by hard logic. There is no problem.

  In addition, this invention is not limited to above-described embodiment, In the range described in the claim, it can change suitably. Further, the above embodiments are not irrelevant to each other, and can be combined as appropriate unless the combination is clearly impossible. In each of the above-described embodiments, it is needless to say that elements constituting the embodiment are not necessarily indispensable except for the case where it is clearly indicated that the element is essential and the case where the element is clearly considered essential in principle. Yes. Further, in each of the above embodiments, when numerical values such as the number, numerical value, quantity, range, etc. of the constituent elements of the embodiment are mentioned, it is clearly limited to a specific number when clearly indicated as essential and in principle. The number is not limited to the specific number except for the case. In each of the above embodiments, when referring to the material, shape, positional relationship, etc. of the constituent elements, etc., unless otherwise specified, or in principle limited to a specific material, shape, positional relationship, etc. The material, shape, positional relationship, etc. are not limited.

DESCRIPTION OF SYMBOLS 1 Refrigeration cycle apparatus 2 Compressor 3 Condenser 4 Supercooling heat exchanger 5 Depressurization apparatus 6 Evaporator 10 Air conditioning duct 31 Cooling water circuit 60 1st refrigerant circuit 62 2nd refrigerant circuit

Claims (5)

An air conditioning duct (10) for circulating air blown into the passenger compartment;
A compressor (2) that compresses and discharges the sucked refrigerant, a condenser (3) that condenses the refrigerant discharged from the compressor by heat exchange with outside air, and a decompression device that depressurizes the refrigerant condensed in the condenser (5) and a refrigeration cycle apparatus (1) having an evaporator (6) for cooling air flowing in the air conditioning duct;
A heater core that is arranged on the downstream side of the air flow from the evaporator in the air conditioning duct and heats the air cooled by the evaporator by heat exchange with a coolant that cools the heat generating device (30) mounted on the vehicle. (34)
Auxiliary heat exchange for cooling the refrigerant flowing out of the condenser by heat exchange between the refrigerant flowing out of the condenser and flowing into the decompression device and the cooling liquid cooled by the heater core outside the air conditioning duct. Vessel (4),
The coolant that has flowed out of the auxiliary heat exchanger flows into the auxiliary heat exchanger through the heater core without passing through the heat generating device, and the heat generating device and the heater core through the heater core. A first flow path switching device (33) for switching between the flow path flowing into the auxiliary heat exchanger;
Heating determination means (S106) for determining whether or not heating of the coolant is necessary based on the target blowing temperature;
When it is determined by the heating determination means that heating of the cooling liquid is not necessary, the cooling liquid that has flowed out of the auxiliary heat exchanger passes through the heater core without passing through the heating device, and the auxiliary heat exchange. First flow path control means (S107) for controlling the first flow path switching device so as to be a flow path flowing into the vessel;
When it is determined by the heating determination means that the cooling liquid needs to be heated, the cooling liquid flowing out from the auxiliary heat exchanger flows into the auxiliary heat exchanger via the heat generating device and the heater core. A vehicle air conditioner comprising: second flow path control means (S108) for controlling the first flow path switching device so as to be a flow path . An air conditioning duct (10) for circulating air blown into the passenger compartment;
A compressor (2) that compresses and discharges the sucked refrigerant, a condenser (3) that condenses the refrigerant discharged from the compressor by heat exchange with outside air, and a decompression device that depressurizes the refrigerant condensed in the condenser (5) and a refrigeration cycle apparatus (1) having an evaporator (6) for cooling air flowing in the air conditioning duct;
A heater core that is arranged on the downstream side of the air flow from the evaporator in the air conditioning duct and heats the air cooled by the evaporator by heat exchange with a coolant that cools the heat generating device (30) mounted on the vehicle. (34)
Auxiliary heat exchange for cooling the refrigerant flowing out of the condenser by heat exchange between the refrigerant flowing out of the condenser and flowing into the decompression device and the cooling liquid cooled by the heater core outside the air conditioning duct. Vessel (4),
The coolant flowing out of the heater core flows into the heater core via the auxiliary heat exchanger and the heat generating device, and to the heater core via the heat generating device without passing through the auxiliary heat exchanger. A second flow path switching device (33a, 33b) for switching between the flow paths flowing in;
Heating determination means (S106) for determining whether or not heating of the coolant is necessary based on the target blowing temperature;
When the heating determination means determines that heating of the cooling liquid is not necessary, the cooling liquid flowing out from the heater core becomes a flow path for flowing into the heater core via the auxiliary heat exchanger and the heat generating device. Third flow path control means (S207) for controlling the second flow path switching device,
When it is determined by the heating determination means that the cooling liquid needs to be heated, the cooling liquid flowing out from the heater core flows into the heater core via the heat generating device without passing through the auxiliary heat exchanger. A vehicle air conditioner comprising: fourth flow path control means (S208) for controlling the second flow path switching device so as to be a flow path . The vehicle air conditioner according to claim 1 or 2 , further comprising a flow rate adjusting means (35) for adjusting a flow rate of the coolant flowing out of the heater core. Temperature determining means (S306) for determining whether the temperature of the coolant flowing out of the heater core and flowing into the auxiliary heat exchanger is higher than the temperature of the refrigerant flowing into the auxiliary heat exchanger;
When the temperature determining means determines that the temperature of the coolant flowing out from the heater core and flowing into the auxiliary heat exchanger is higher than the temperature of the refrigerant flowing into the auxiliary heat exchanger, the cooling flowing out from the heater core The vehicle air conditioner according to claim 3 , further comprising a flow rate control unit (S307) for controlling the flow rate adjusting unit so as to reduce a flow rate of the liquid. The refrigeration cycle apparatus includes a first refrigerant circuit (60) in which refrigerant discharged from the compressor returns to the compressor through the condenser, the auxiliary heat exchanger, the decompression device, and the evaporator in order. The second refrigerant circuit (62) in which the refrigerant discharged from the compressor is introduced into the auxiliary heat exchanger without passing through the condenser, and the first refrigerant circuit and the second refrigerant circuit are alternatively selected. A circuit switching device (54) to be established
Switching control means (S02, S13, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14, S14) controls the circuit switching device. The vehicle air conditioner according to any one of claims 1 to 4 , further comprising S204).

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