WO2023276626A1 - Heat pump cycle apparatus - Google Patents

Abstract

This heat pump cycle apparatus comprises: a defrosting operation execution unit (S6, S7) for executing a defrosting operation, in which a heat-absorbing unit (35) is defrosted, when it is assessed by a frosting assessment unit (S1) that frosting has occurred on the heat-absorbing unit (35); and a defrosting operation prohibition unit (S4, S5) for prohibiting executing of the defrosting operation by the defrosting operation execution unit (S6, S7). During execution of the defrosting operation, the defrosting operation execution unit (S6, S7) defrosts the heat-absorbing unit (35) by using a heat medium heated by a heat-emitting unit (81) as a heat source. The defrosting operation prohibition unit (S4, S5) prohibits subsequent execution of the defrosting operation until a defrosting elapsed time (Tm2), which is the elapsed time from when the previous instance of the defrosting operation ended, is equal to or greater than a defrosting standby time (Tmi2).

Description

heat pump cycle device Cross-reference to related applications

This application is based on Japanese Patent Application No. 2021-108737 filed on June 30, 2021, and the contents thereof are incorporated herein.

The present disclosure relates to a heat pump cycle device that performs a defrosting operation when frost forms on the heat absorbing portion.

Conventionally, in Patent Document 1, it is applied to a vehicle air conditioner, and when frost forms on an outdoor heat exchanger forming a heat absorption part, a defrosting operation is performed to remove frost on the outdoor heat exchanger. A heat pump cycle device is disclosed.

More specifically, in the defrosting operation of the heat pump cycle device of Patent Document 1, the high-temperature and high-pressure refrigerant (so-called hot gas) discharged from the compressor flows into the outdoor heat exchanger, thereby reaching the outdoor heat exchanger. It melts and removes frost. Therefore, in the heat pump cycle device of Patent Document 1, the heat of the outside air cannot be absorbed by the refrigerant in the outdoor heat exchanger during the defrosting operation, and the vehicle interior cannot be heated. end up

Therefore, in the heat pump cycle device of Patent Document 1, even if frost forms on the outdoor heat exchanger, when a natural defrosting condition is established in which it is determined that the frost on the outdoor heat exchanger naturally melts, the defrosting is performed. Execution of frost operation is prohibited. As a result, the heat pump cycle device of Patent Literature 1 attempts to prevent the frequent execution of the defrosting operation and the inability to continue heating the vehicle interior.

JP 2019-43422 A

As described above, in the defrosting operation of the heat pump cycle device of Patent Document 1, hot gas is used as a heat source to remove frost. Therefore, in the heat pump cycle device of Patent Document 1, by operating the compressor, it is possible to relatively easily generate enough heat to melt and remove the frost.

However, in a heat pump cycle device that performs a defrosting operation using heat generated by a heat-generating part that is different from the compressor as a heat source, it is possible that sufficient heat cannot be secured to melt and remove the frost when performing the defrosting operation. There is also sex. Furthermore, if defrosting operation is performed in a state in which sufficient heat cannot be secured, defrosting will be insufficient. As a result, it may be determined that frost has formed on the heat absorbing portion again immediately after the defrosting operation ends, and the defrosting operation may be performed frequently.

In view of the above points, the present disclosure aims to provide a heat pump cycle device capable of suppressing execution of unnecessary defrosting operation.

In order to achieve the above object, a heat pump cycle device according to one aspect of the present disclosure includes a compressor, a heating unit, a pressure reducing unit, a heat absorbing unit, a frosting determination unit, a defrosting operation execution unit, and a defrosting and a driving prohibition unit.

The compressor compresses the refrigerant. The heating unit heats the fluid to be heated by dissipating heat from the refrigerant discharged from the compressor. The decompression unit decompresses the refrigerant flowing out from the heating unit. The heat absorption section causes the refrigerant decompressed by the decompression section to absorb heat of outside air. The frost formation determination unit determines that frost has formed on the heat absorption unit. The defrosting operation executing unit executes a defrosting operation for defrosting the heat absorbing unit when the frost formation determining unit determines that frost has formed on the heat absorbing unit. The defrosting operation prohibition unit prohibits the defrosting operation execution unit from performing the defrosting operation.

Furthermore, the heat absorption part has a heat medium circuit connected to a heat medium heat exchange part that exchanges heat between the refrigerant decompressed in the decompression part and the heat medium, and an outside air heat exchange part that exchanges heat between the heat medium and the outside air. have. A heat-generating portion that heats the heat medium is arranged in the heat medium circuit.

The defrosting operation execution unit defrosts the outside air heat exchange unit using the heat medium heated by the heat generating unit as a heat source when the defrosting operation is executed.

In addition, the defrosting operation prohibition unit prohibits the execution of the next defrosting operation until the defrosting elapsed time, which is the elapsed time from the end of the previous defrosting operation, is equal to or longer than a predetermined defrosting standby time. do.

According to this, the defrosting operation prohibiting unit prohibits execution of the next defrosting operation until the defrosting elapsed time is equal to or longer than the defrosting standby time.

Therefore, while the defrosting operation prohibition unit prohibits execution of the next defrosting operation, the heating unit can heat the heat medium. Further, the defrosting standby time can be set so that the amount of heat stored in the heat medium from the heat generating section is such that the frost on the outside air heat exchange section can be reliably melted and removed. .

Therefore, the defrosting operation executing section executes the defrosting operation, so that the frost on the outside air heat exchange section can be sufficiently removed. In other words, it is possible to prevent the defrosting from becoming insufficient and the frost formation determining unit determining that the heat absorbing unit is frosted again immediately after the defrosting operation ends.

As a result, frequent execution of the defrosting operation can be suppressed. That is, according to the heat pump cycle device of one aspect of the present disclosure, it is possible to provide a heat pump cycle device capable of suppressing execution of unnecessary defrosting operation.

The above and other objects, features and advantages of the present disclosure will become more apparent from the following detailed description with reference to the accompanying drawings.
1 is a schematic configuration diagram of a vehicle air conditioner to which a heat pump cycle device of one embodiment is applied; FIG. It is an explanatory view for explaining the operation mode of the five-way valve of one embodiment. It is an explanatory view for explaining another operation mode of the five-way valve of one embodiment. 1 is a schematic configuration diagram of an indoor air conditioning unit of one embodiment; FIG. It is a block diagram which shows the electric-control part of the heat pump cycle apparatus of one Embodiment. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a single cooling mode of a heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a single dehumidifying and heating mode of the heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a single heating mode of a heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a cooling mode of a heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a cooling, dehumidifying, and heating mode of the heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a cooling/heating mode of a heat pump cycle device of one embodiment; FIG. 1 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a single cooling mode of a heat pump cycle device of one embodiment; FIG. It is a flowchart which shows the control flow of the defrosting operation of the heat pump cycle apparatus of one Embodiment. FIG. 4 is a control characteristic diagram for determining a frost state by a frost formation determination unit of one embodiment; FIG. 2 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a defrosting operation of the heat pump cycle device of one embodiment; FIG. 10 is a schematic overall configuration diagram showing flows of a refrigerant and a heat medium in a defrosting operation of a heat pump cycle device of another embodiment;

An embodiment of a heat pump cycle device 1 according to the present disclosure will be described using FIGS. 1 to 15. FIG. The heat pump cycle device 1 of this embodiment is mounted on an electric vehicle, and is applied to a vehicle air conditioner with a vehicle-mounted device temperature adjustment function. An electric vehicle is a vehicle that obtains driving force for running from an electric motor.

In an electric vehicle, the heat pump cycle device 1 air-conditions the interior of the vehicle, which is the space to be air-conditioned, and adjusts the temperature of the in-vehicle equipment, which is the object of temperature adjustment. Vehicle-mounted devices that are temperature-adjusted objects of the heat pump cycle device 1 are the battery 80 and the high-voltage device 81 .

The battery 80 is a secondary battery that stores power to be supplied to a plurality of on-vehicle devices that operate on electricity. The battery 80 is an assembled battery formed by electrically connecting a plurality of stacked battery cells in series or in parallel. The battery cell of this embodiment is a lithium ion battery.

The battery 80 generates heat during operation (that is, during charging and discharging). The battery 80 has a characteristic that the output tends to decrease when the temperature becomes low, and the deterioration tends to progress when the temperature becomes high. Therefore, the temperature of the battery 80 must be maintained within an appropriate temperature range (15° C. or higher and 55° C. or lower in this embodiment).

The heavy electric system device 81 is an in-vehicle device that operates when power is supplied and generates heat during operation. The heavy electric system device 81 of this embodiment is specifically a sensor processing unit 82 , a power control unit 83 and a transaxle 84 .

The sensor processing unit 82 is a control device that aggregates environmental sensor interfaces and communication functions for automatic operation and energy-saving operation. The power control unit 83 is a power control unit that performs power transformation and power distribution. The transaxle 84 is a power transmission mechanism that integrates a transmission, a differential gear, and the like.

There is a possibility that the electrical circuit of the heavy electrical equipment 81 will deteriorate when it reaches a high temperature. Therefore, it is necessary to keep the temperature lower than the reference heat resistant temperature (130° C. in this embodiment) that can protect the respective electric circuits.

The heat pump cycle device 1 includes a heat pump cycle 10, a high temperature side heat medium circuit 20, and a low temperature side heat medium circuit 30, as shown in the overall configuration diagram of FIG. Furthermore, the heat pump cycle device 1 includes an indoor air conditioning unit 40 shown in FIG. 4 and a control device 50 shown in FIG.

The heat pump cycle device 1 can execute normal operation for air-conditioning the vehicle interior and adjusting the temperature of on-vehicle equipment. During normal operation, the circuit configurations of the heat pump cycle 10, the high temperature side heat medium circuit 20, and the low temperature side heat medium circuit 30 can be switched to switch between various operation modes. Furthermore, when frost forms on the heat absorbing portion, which will be described later, during normal operation, it is possible to perform a defrosting operation to remove frost from the heat absorbing portion.

First, the heat pump cycle 10 will be explained. The heat pump cycle 10 supplies the air blown into the vehicle interior, the high temperature side heat medium circulating through the high temperature side heat medium circuit 20, and the low temperature side heat medium circuit 30 to air-condition the vehicle interior and adjust the temperature of the onboard equipment. It is a vapor compression refrigeration cycle device that adjusts the temperature of the circulating low-temperature heat medium.

The heat pump cycle 10 employs an HFO-based refrigerant (specifically, R1234yf) as the refrigerant. The heat pump cycle 10 constitutes a subcritical refrigeration cycle in which the pressure of the high-pressure refrigerant discharged from the compressor 11 does not exceed the critical pressure of the refrigerant. Refrigerant oil for lubricating the compressor 11 is mixed in the refrigerant. Refrigerating machine oil is PAG oil having compatibility with the liquid phase refrigerant. Some of the refrigerating machine oil circulates through the cycle together with the refrigerant.

In the heat pump cycle 10, the compressor 11 sucks, compresses, and discharges the refrigerant. The compressor 11 is arranged in the drive unit room on the front side of the passenger compartment. The driving device room forms a space in which at least part of a device (for example, a motor generator) used to generate driving force for running the vehicle is arranged.

The compressor 11 is an electric compressor in which an electric motor drives a fixed displacement type compression mechanism with a fixed displacement. The compressor 11 has its rotation speed (that is, refrigerant discharge capacity) controlled by a control signal output from a control device 50, which will be described later.

The inlet side of the refrigerant passage of the water-refrigerant heat exchanger 12 is connected to the discharge port of the compressor 11 . The water-refrigerant heat exchanger 12 has a refrigerant passage through which the high pressure refrigerant discharged from the compressor 11 flows, and a heat medium passage through which the high temperature side heat medium circulating in the high temperature side heat medium circuit 20 flows. The water-refrigerant heat exchanger 12 is a heat exchange unit that heats the high temperature side heat medium by exchanging heat between the high pressure refrigerant flowing through the refrigerant passage and the high temperature side heat medium flowing through the heat medium passage.

The inlet side of the receiver 13 is connected to the outlet of the refrigerant passage of the water-refrigerant heat exchanger 12 . The receiver 13 is a high-pressure-side gas-liquid separator that separates the gas-liquid of the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 and stores surplus liquid-phase refrigerant in the cycle. The refrigerant outlet of the receiver 13 is connected to the inlet side of the first refrigerant joint portion 14a.

The first refrigerant joint portion 14a is a three-way joint having three inlets and outlets communicating with each other. As the first refrigerant joint portion 14a, a joint member formed by joining a plurality of pipes or a joint member formed by providing a plurality of refrigerant passages in a metal block or a resin block can be adopted.

Furthermore, the heat pump cycle 10 has a second refrigerant joint portion 14b. The basic configuration of the second refrigerant joint portion 14b is the same as that of the first refrigerant joint portion 14a.

When one of the three inflow ports is used as the inflow port and the remaining two are used as the outflow ports, these joints serve as branching portions that branch the flow of the refrigerant. Further, when two of the three inflow ports are used as the inflow port and the remaining one is used as the outflow port, it becomes a confluence portion that merges the flows of the refrigerant.

The inlet side of the cooling expansion valve 15a is connected to one outlet of the first refrigerant joint portion 14a. The inlet side of the cooling expansion valve 15b is connected to the other outflow port of the first refrigerant joint portion 14a.

The cooling expansion valve 15a reduces the pressure of the high-pressure refrigerant that has flowed out of the refrigerant passage of the water-refrigerant heat exchanger 12 and adjusts the flow rate (mass flow rate) of the refrigerant that flows out downstream during a single cooling mode or the like, which will be described later. .

The cooling expansion valve 15a is an electric variable valve having a valve body portion that changes the opening degree of the throttle passage (that is, the valve opening degree) and an electric actuator (specifically, a stepping motor) that displaces the valve body portion. A diaphragm mechanism. The operation of the cooling expansion valve 15 a is controlled by a control signal (specifically, a control pulse) output from the control device 50 .

The cooling expansion valve 15b reduces the pressure of the high-pressure refrigerant flowing out of the refrigerant passage of the water-refrigerant heat exchanger 12 and adjusts the flow rate (mass flow rate) of the refrigerant flowing out to the downstream side during a single cooling mode or the like, which will be described later. This is the decompression section. The basic configuration of the cooling expansion valve 15b is similar to that of the cooling expansion valve 15a.

The cooling expansion valve 15a and the cooling expansion valve 15b have a fully closing function of closing the refrigerant passage by fully closing the throttle passage with the valve body. The cooling expansion valve 15a and the cooling expansion valve 15b can switch the refrigerant circuit of the heat pump cycle 10 by the fully closed function. Therefore, the cooling expansion valve 15a and the cooling expansion valve 15b also function as a refrigerant circuit switching unit.

The refrigerant inlet side of the indoor evaporator 16 is connected to the outlet of the cooling expansion valve 15a. The indoor evaporator 16 is arranged in an air conditioning case 41 of an indoor air conditioning unit 40, which will be described later. The indoor evaporator 16 is a heat exchange unit that exchanges heat between the low-pressure refrigerant decompressed by the cooling expansion valve 15a and the air blown into the vehicle interior. The indoor evaporator 16 cools the blown air by evaporating the low-pressure refrigerant and exerting an endothermic effect.

The refrigerant outlet of the indoor evaporator 16 is connected to the inlet side of the evaporation pressure regulating valve 17 . The evaporation pressure regulating valve 17 maintains the refrigerant evaporation temperature in the indoor evaporator 16 at a frost suppression temperature (in this embodiment, 1° C.) or higher at which frost formation of the indoor evaporator 16 can be suppressed. The evaporating pressure regulating valve 17 is composed of a mechanical mechanism that increases the valve opening as the refrigerant pressure on the refrigerant outlet side of the indoor evaporator 16 increases.

The outlet of the evaporating pressure regulating valve 17 is connected to one inlet side of the second refrigerant joint 14b.

The inlet side of the refrigerant passage of the chiller 18 is connected to the outlet of the cooling expansion valve 15b. The chiller 18 has a refrigerant passage through which the low-pressure refrigerant flowing out from the cooling expansion valve 15b flows, and a heat medium passage through which the low temperature side heat medium circulating in the low temperature side heat medium circuit 30 flows. The chiller 18 is a heat medium heat exchange unit that exchanges heat between the low-pressure refrigerant flowing through the refrigerant passage and the low-temperature side heat medium flowing through the heat medium passage. The chiller 18 cools the low-temperature side heat medium by evaporating the low-pressure refrigerant and exerting an endothermic action.

The outlet of the refrigerant passage of the chiller 18 is connected to the other inlet side of the second refrigerant joint 14b. The suction port side of the compressor 11 is connected to the outflow port of the second refrigerant joint portion 14b.

Next, the high temperature side heat medium circuit 20 will be described. The high temperature side heat medium circuit 20 is a circuit that circulates the high temperature side heat medium. The high temperature side heat medium circuit 20 employs an ethylene glycol aqueous solution as the high temperature side heat medium.

The high temperature side heat medium circuit 20 includes a high temperature side pump 21, a high temperature side flow control valve 22, a heater core 23, a high temperature side radiator 25, and the like. Furthermore, the heat medium passage of the water-refrigerant heat exchanger 12 is connected to the high temperature side heat medium circuit 20 .

The high temperature side pump 21 is an electric water pump that draws in the high temperature side heat medium that has flowed out from the heat medium passage of the water-refrigerant heat exchanger 12 and pumps it to the inlet side of the high temperature side flow control valve 22 . The high temperature side pump 21 has its rotation speed (that is, pumping capability) controlled by a control voltage output from the control device 50 .

The high-temperature side flow control valve 22 is an electric three-way flow control valve that has one inlet and two outlets and can continuously adjust the passage area ratio of the two outlets. The operation of the high temperature side flow control valve 22 is controlled by a control signal output from the control device 50 .

The heating medium inlet side of the heater core 23 is connected to one outflow port of the high temperature side flow control valve 22 . Also, the heat medium inlet side of the high temperature side radiator 25 is connected to the other outflow port of the high temperature side flow control valve 22 .

Therefore, the high temperature side flow control valve 22 adjusts the flow rate of the high temperature side heat medium that flows into the heater core 23 and the flow rate of the high temperature side heat medium that flows into the high temperature side radiator 25 among the high temperature side heat medium pressure-fed from the high temperature side pump 21 . can be continuously adjusted.

Furthermore, the high-temperature side flow control valve 22 adjusts the flow ratio so that the entire flow rate of the high-temperature side heat medium pressure-fed from the high-temperature side pump 21 flows out to either the heater core 23 side or the high-temperature side radiator 25 side. can be made Therefore, the high temperature side flow control valve 22 also functions as a high temperature side heat medium circuit switching section for switching the circuit configuration of the high temperature side heat medium circuit 20 .

The heater core 23 is a heat exchange section that heats the air blown into the passenger compartment by exchanging heat between the high temperature side heat medium flowing out of the high temperature side flow control valve 22 and the air blown into the vehicle compartment. The heater core 23 is arranged inside the air conditioning case 41 of the indoor air conditioning unit 40 . Therefore, the blown air becomes the fluid to be heated by the heat pump cycle device 1 .

The heat medium outlet of the heater core 23 is connected to one inlet side of the first heat medium joint 24a. The first heat medium joint portion 24a is a three-way joint having the same configuration as the first refrigerant joint portion 14a and the like.

A high-voltage heater 26 is arranged in the heat medium flow path connecting the high temperature side flow control valve 22 , one outlet, and the heat medium inlet of the heater core 23 . The high voltage heater 26 is an electric heater that heats the high temperature side heat medium. The high voltage heater 26 is a PTC heater having a positive temperature coefficient thermistor. The amount of heat generated by the high voltage heater 26 is controlled by a control voltage output from the control device 50 .

Here, the amount of energy consumed when using the high-voltage heater 26 to raise the temperature of the heat medium flowing into the heater core 23 by a predetermined amount is greater than when using the heat pump cycle 10 to raise the temperature. Therefore, when heating the vehicle interior, operating the heat pump cycle 10 can reduce the amount of power stored in the battery 80 rather than energizing the high voltage heater 26 .

The high temperature side radiator 25 is a heat exchange section that exchanges heat between the high temperature side heat medium flowing out of the high temperature side flow control valve 22 and the outside air. The high temperature side radiator 25 is arranged on the front side in the drive unit room together with the low temperature side radiator 35 which will be described later. Therefore, when the vehicle is running, the high-temperature side radiator 25 can be exposed to running wind that has flowed into the drive unit compartment through the grill.

The heat medium outlet of the high temperature side radiator 25 is connected to the other inlet side of the first heat medium joint 24a. The inlet side of the heat medium passage of the water-refrigerant heat exchanger 12 is connected to the outflow port of the first heat medium joint portion 24 a via the high temperature side reserve tank 27 .

The high temperature side reserve tank 27 is a reservoir that stores the high temperature side heat medium. In the high temperature side heat medium circuit 20, by storing the surplus high temperature side heat medium in the high temperature side reserve tank 27, it is possible to suppress the decrease in the liquid amount of the high temperature side heat medium circulating in the high temperature side heat medium circuit 20. can. Furthermore, the high temperature side reserve tank 27 has a heat medium supply port for replenishing the high temperature side heat medium when the high temperature side heat medium is insufficient.

Therefore, in the high-temperature-side heat medium circuit 20, the water-refrigerant heat exchanger 12 heat-exchanges the high-temperature-side heat medium and the high-pressure refrigerant to heat the high-temperature-side heat medium. Furthermore, the heater core 23 heat-exchanges the high-temperature-side heat medium and the blast air to heat the blast air. That is, the water-refrigerant heat exchanger 12 and the heater core 23 of the high-temperature side heat medium circuit 20 form a heating portion that heats the blast air, which is the fluid to be heated, using the refrigerant discharged from the compressor 11 as a heat source.

Next, the low temperature side heat medium circuit 30 will be described. The low temperature side heat medium circuit 30 is a heat medium circuit that circulates a low temperature side heat medium that is a heat medium. In the low temperature side heat medium circuit 30, the same kind of fluid as the high temperature side heat medium is used as the low temperature side heat medium.

A first low temperature side pump 31a, a second low temperature side pump 31b, a five-way valve 32, a low temperature side radiator 35, a bypass passage 38, and the like are connected to the low temperature side heat medium circuit 30. Furthermore, the heat medium passage of the chiller 18 , the cooling water passage 80 a of the battery 80 , and the cooling water passage of the high-voltage equipment 81 are connected to the low temperature side heat medium circuit 30 .

A cooling water passage 80a of the battery 80 is formed within a dedicated case that accommodates a plurality of battery cells. A cooling water passage 80a of the battery 80 is a heat exchange portion that exchanges heat between the plurality of battery cells forming the battery 80 and the low temperature side heat medium.

The cooling water passage 80a of the battery 80 can cool the battery 80 by exchanging heat between the low temperature side heat medium cooled by the chiller 18 and the battery 80. Also, the battery 80 can be heated by exchanging heat between the battery 80 and the low-temperature heat medium heated by the battery heater 36, which will be described later.

The cooling water passages of the high-voltage equipment 81 specifically include a cooling water passage 82a of the sensor processing unit 82, a cooling water passage 83a of the power control unit 83, and a cooling water passage 84a of the transaxle 84. Each of the cooling water passages 82a-84a is connected in series with the flow of the low temperature side heat medium. Each of the cooling water passages 82a to 84a is a heat exchange portion that exchanges heat between the low-temperature side heat medium and the high-voltage equipment 81. As shown in FIG.

In the cooling water passage of the high current system equipment 81, the high current system equipment 81 can be cooled by heat exchange between the low temperature side heat medium cooled by the low temperature side radiator 35 and the high current system equipment 81. In other words, in the cooling water passage of the high-voltage equipment 81, the low-temperature side heat medium can be heat-exchanged with the high-voltage equipment 81 to heat the low-temperature side heat medium. Therefore, the high-power system device 81 serves as a heat generating portion that heats the low-temperature side heat medium.

The first low temperature side pump 31a is an electric water pump that draws in the low temperature side heat medium that has flowed out from the second heat medium joint 34b and pumps it to the inlet side of the heat medium passage of the chiller 18. The basic configuration of the first low temperature side pump 31a and the second low temperature side pump 31b is the same as that of the high temperature side pump 21 . The basic configurations of the second heat medium joint portion 34b, the third heat medium joint portion 34c, and the fourth heat medium joint portion 34d, which will be described later, are the same as those of the first heat medium joint portion 24a.

A chiller-side inflow port 32a side of a five-way valve 32 is connected to the outlet of the heat medium passage of the chiller 18. The five-way valve 32 is a low temperature side heat medium circuit switching unit that switches the circuit configuration of the low temperature side heat medium circuit 30 .

The five-way valve 32 has five inlets and outlets. Specifically, the five-way valve 32 has a chiller-side inlet 32a and a high-power equipment-side inlet 32b as inlets for inflowing the low-temperature heat medium. The five-way valve 32 has a battery side outflow port 32c, a radiator side outflow port 32d, and a bypass passage side outflow port 32e as outflow ports for outflowing the low temperature side heat medium that has flowed into the interior. A detailed configuration of the five-way valve 32 will be described later.

The inlet side of the cooling water passage 80a of the battery 80 is connected to the battery side outlet 32c of the five-way valve 32. A battery heater 36 is arranged in a heat medium flow path that connects the battery side outlet 32 c of the five-way valve 32 and the inlet of the cooling water passage 80 a of the battery 80 .

The battery heater 36 is an electric heater that heats the low temperature side heat medium flowing into the cooling water passage 80 a of the battery 80 in order to warm up the battery 80 . A basic configuration of the battery heater 36 is similar to that of the high voltage heater 26 . As the battery heater 36, an electric heater having a smaller output than the high voltage heater 26 can be used.

The outlet of the cooling water passage 80a of the battery 80 is connected to one inlet side of the second heat medium joint portion 34b. The suction port side of the first low temperature side pump 31a is connected to the outflow port of the second heat medium joint portion 34b.

The second low-temperature side pump 31b is an electric water pump that draws in the low-temperature side heat medium that has flowed out from the third heat medium joint portion 34c and pumps it to the inlet side of the cooling water passage of the high-voltage equipment 81. More specifically, the low temperature side heat medium pressure-fed from the second low temperature side pump 31b passes through the cooling water passage 82a of the sensor processing unit 82, the cooling water passage 83a of the power control unit 83, and the cooling water passage 84a of the transaxle 84. flow in the order of

A low temperature side reserve tank 37 is arranged in the heat medium flow path connecting the outlet of the third heat medium joint 34c and the suction port of the second low temperature side pump 31b. The low temperature side reserve tank 37 is a reservoir that stores the low temperature side heat medium. The basic configuration of the low temperature side reserve tank 37 is similar to that of the high temperature side reserve tank 27 .

The high-current equipment side inflow port 32b side of the five-way valve 32 is connected to the outlet of the cooling water passage of the high-current equipment 81, that is, the outlet of the cooling water passage 84a of the transaxle 84.

The heat medium inlet side of the low temperature side radiator 35 is connected to the radiator side outlet 32 d of the five-way valve 32 . The low-temperature side radiator 35 is an outside air heat exchange section that exchanges heat between the low-temperature side heat medium flowing out from the radiator-side outlet 32d of the five-way valve 32 and the outside air. The basic configuration of the low temperature side radiator 35 is similar to that of the high temperature side radiator 25 .

The low temperature side radiator 35 is arranged on the front side in the driving device room together with the high temperature side radiator 25 described above. More specifically, the low temperature side radiator 35 is arranged downstream of the high temperature side radiator 25 in the flow of outside air. Therefore, in the low-temperature side radiator 35 , heat is exchanged between the low-temperature side heat medium and the outside air after passing through the high-temperature side radiator 25 .

Also, the high temperature side radiator 25 and the low temperature side radiator 35 of the present embodiment are integrated so that the heat of the high temperature side heat medium and the heat of the low temperature side heat medium can be transferred to each other. Therefore, the high temperature side radiator 25 and the low temperature side radiator 35 can transfer the heat of the high temperature side heat medium to the low temperature side radiator 35 . Furthermore, the heat of the low temperature side heat medium can be transferred to the high temperature side radiator 25 .

More specifically, in the high temperature side radiator 25 and the low temperature side radiator 35 of this embodiment, the metal heat exchange fins 25a for promoting heat exchange are formed of a common member. The heat of the high-temperature side heat medium and the heat of the low-temperature side heat medium can be mutually transferred via the heat exchange fins 25a, which are common members.

The heat medium outlet of the low temperature side radiator 35 is connected to the inlet side of the fourth heat medium joint 34d. One inflow port side of the third heat medium joint portion 34c is connected to one outflow port of the fourth heat medium joint portion 34d. The other inflow port side of the second heat medium joint portion 34b is connected to the other outflow port of the fourth heat medium joint portion 34d.

The inlet side of the bypass passage 38 is connected to the bypass passage side outlet 32 e of the five-way valve 32 . The bypass passage 38 is a heat medium flow path that guides the low temperature side heat medium that has flowed into the five-way valve 32 to the side of the third heat medium joint portion 34c, bypassing the low temperature side radiator 35 . Therefore, the outlet of the bypass passage 38 is connected to the other inlet side of the third heat medium joint portion 34c.

Next, the detailed configuration of the five-way valve 32 will be described with reference to FIGS. 2 and 3. FIG. As shown in FIGS. 2 and 3, the five-way valve 32 allows the low-temperature side heat medium to flow into the interior from a chiller-side inlet 32a and a high-current equipment-side inlet 32b. Further, the low temperature side heat medium that has flowed inside is caused to flow out from at least one of the battery side outlet 32c, the radiator side outlet 32d, and the bypass passage side outlet 32e.

2 and 3, the five-way valve 32 includes, for example, a plurality of three-way flow control valves having the same configuration as the high temperature side flow control valve 22, the first heat medium joint portion 24a, and the like. can be formed by combining three-way joints having the configuration of

The five-way valve 32 allows the low-temperature side heat medium that has flowed out of the heat medium passage of the chiller 18 to flow inside from the chiller side inlet 32a, as indicated by the thick solid line arrows in the explanatory view of FIG. Then, the low-temperature heat medium that has flowed into the interior from the chiller-side inlet 32a can flow out from at least one of the battery-side outlet 32c and the radiator-side outlet 32d.

In other words, the five-way valve 32 controls the flow rate of the low-temperature side heat medium flowing out from the battery side outlet 32c to the inlet side of the cooling water passage 80a of the battery 80 and the flow rate of the low temperature side heat medium from the radiator side outlet 32d to the heat medium inlet side of the low temperature side radiator 35. It is possible to continuously adjust the flow rate ratio with the flow rate of the low temperature side heat medium flowing out to.

Furthermore, the five-way valve 32 adjusts the flow ratio so that the total flow of the low-temperature side heat medium flowing into the interior from the chiller-side inlet 32a is diverted to the inlet side of the cooling water passage 80a of the battery 80 and the low-temperature side radiator. It is also possible to flow out to either one of the heat medium inlet sides of 35 . Thereby, the five-way valve 32 can switch a part of the circuit configuration of the low temperature side heat medium circuit 30 to the battery cooling circuit and the heat absorption circuit.

In the battery cooling circuit, the low temperature side heat medium pressure-fed from the first low temperature side pump 31a is sucked into the heat medium passage of the chiller 18, the battery heater 36, the cooling water passage 80a of the battery 80, and the first low temperature side pump 31a. Circulate in mouth order. In the heat absorption circuit, the low temperature side heat medium pressure-fed from the first low temperature side pump 31a circulates through the heat medium passage of the chiller 18, the low temperature side radiator 35, and the suction port of the first low temperature side pump 31a in this order.

Furthermore, the five-way valve 32 switches the circuit configuration of a part of the low temperature side heat medium circuit 30 to the battery cooling circuit or the battery cooling circuit, and at the same time, as indicated by the thin solid line arrow in FIG. Another part of the circuit configuration of the medium circuit 30 can be switched to a heat storage circuit, which will be described later.

3, the five-way valve 32 allows the low-temperature-side heat medium that has flowed out of the cooling water passage 84a of the transaxle 84 to enter through the high-current equipment-side inlet 32b. Let Then, the low-temperature side heat medium that has flowed into the interior from the high-voltage equipment side inlet 32b can be flowed out from at least one of the radiator side outlet 32d and the bypass passage side outlet 32e.

In other words, the five-way valve 32 regulates the flow rate of the low temperature side heat medium flowing out from the radiator side outlet 32d to the heat medium inlet side of the low temperature side radiator 35 and the low temperature side heat flowing out from the bypass passage side outlet 32e to the bypass passage 38. The flow ratio to the medium flow can be adjusted continuously.

Furthermore, the five-way valve 32 adjusts the flow ratio so that the entire flow of the low-temperature side heat medium flowing into the inside from the high-voltage equipment side inlet 32b is diverted to the heat medium inlet side of the low-temperature side radiator 35 and the bypass passage. It is also possible to flow out to either one of the 38 sides. Thereby, the five-way valve 32 can switch a part of the circuit configuration of the low temperature side heat medium circuit 30 to the equipment cooling circuit and the heat storage circuit.

In the device cooling circuit, the low-temperature side heat medium pumped from the second low-temperature side pump 31b circulates through the cooling water passage of the high-voltage device 81, the low-temperature side radiator 35, and the suction port of the second low-temperature side pump 31b in this order. In the heat storage circuit, the low-temperature side heat medium pressure-fed from the second low-temperature side pump 31b circulates through the cooling water passage of the high-voltage equipment 81, the bypass passage 38, and the suction port of the second low-temperature side pump 31b in this order.

Furthermore, the five-way valve 32 switches the circuit configuration of a part of the low temperature side heat medium circuit 30 to the equipment cooling circuit or the heat storage circuit, and at the same time, as indicated by the thin solid line arrow in FIG. Another portion of the circuit configuration of circuit 30 may be switched to form the battery cooling circuit described above.

Next, the indoor air conditioning unit 40 will be explained. The indoor air-conditioning unit 40 is a unit that integrates a plurality of components for blowing air adjusted to an appropriate temperature for air-conditioning the vehicle interior to appropriate locations within the vehicle interior. The indoor air conditioning unit 40 is arranged inside the dashboard (instrument panel) at the forefront of the vehicle interior.

As shown in FIG. 4, the indoor air conditioning unit 40 houses an indoor blower 42, an indoor evaporator 16, a heater core 23, etc. in an air conditioning case 41 that forms an air passage for blown air. The air-conditioning case 41 is molded from a resin (for example, polypropylene) having a certain degree of elasticity and excellent strength.

An inside/outside air switching device 43 is arranged on the most upstream side of the air-conditioning case 41 in the blown air flow. The inside/outside air switching device 43 switches and introduces inside air (that is, vehicle interior air) and outside air (that is, vehicle exterior air) into the air conditioning case 41 . The operation of the inside/outside air switching device 43 is controlled by a control signal output from the control device 50 .

An indoor fan 42 is arranged on the downstream side of the inside/outside air switching device 43 in the blown air flow. The indoor air blower 42 blows the air sucked through the inside/outside air switching device 43 into the vehicle interior. The indoor blower 42 is an electric blower that drives a centrifugal multi-blade fan with an electric motor. The indoor fan 42 has its rotation speed (that is, air blowing capacity) controlled by a control voltage output from the control device 50 .

The indoor evaporator 16 and the heater core 23 are arranged on the downstream side of the indoor blower 42 in the blown air flow. The indoor evaporator 16 is arranged upstream of the heater core 23 in the air flow. In addition, a cold air bypass passage 45 is formed in the air conditioning case 41 so that the air that has passed through the indoor evaporator 16 flows around the heater core 23 .

An air mix door 44 is arranged downstream of the indoor evaporator 16 in the air conditioning case 41 and upstream of the heater core 23 and the cold air bypass passage 45 .

The air mix door 44 adjusts the air volume ratio between the air volume of the air that passes through the heater core 23 side and the air volume of the air that passes through the cold air bypass passage 45 among the air that has passed through the indoor evaporator 16. Department. The air mix door 44 is driven by an air mix door electric actuator. The operation of the electric actuator for the air mix door is controlled by a control signal output from the control device 50 .

A mixing space 46 is arranged on the downstream side of the heater core 23 and the cold air bypass passage 45 in the blown air flow. The mixing space 46 is a space for mixing the blast air heated by the heater core 23 and the unheated blast air that has passed through the cold air bypass passage 45 . Therefore, in the indoor air conditioning unit 40 , the temperature of the air mixed in the mixing space 46 (that is, the conditioned air) can be adjusted by adjusting the opening degree of the air mix door 44 .

A plurality of opening holes (not shown) for blowing out the blast air mixed in the mixing space 46 into the vehicle interior are formed at the most downstream portion of the blast air flow of the air conditioning case 41 . A plurality of opening holes communicate with a plurality of outlets formed in the passenger compartment. A face outlet, a foot outlet, and a defroster outlet are provided as the plurality of outlets.

The face air outlet is an air outlet that blows air toward the upper body of the passenger (that is, the user). The foot air outlet is an air outlet that blows air toward the feet of the occupant. The defroster outlet is an outlet that blows air toward the windshield in front of the vehicle.

A blowout mode door (not shown) is arranged in each of the plurality of opening holes. Blow-mode doors open and close respective apertures. The blow mode door is driven by a blow mode door electric actuator. The operation of the electric actuator for the blowout mode door is controlled by a control signal output from the control device 50 .

Therefore, in the indoor air conditioning unit 40, by switching the opening hole opened by the blow-out mode door, it is possible to change the location from which the conditioned air is blown out in the vehicle compartment.

Next, an outline of the electric control unit of the heat pump cycle device 1 will be described. The control device 50 is composed of a well-known microcomputer including CPU, ROM, RAM, etc. and its peripheral circuits. The control device 50 performs various calculations and processes based on the control program stored in the ROM, and controls various controlled devices 11, 15a, 15b, 21, 22, 26, 31a, 31b, Controls the operation of 32, 36, etc.

As shown in the block diagram of FIG. 5, the input side of the control device 50 includes an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, a chiller temperature sensor 64c, an evaporator temperature sensor 64e, and a high pressure sensor 65a. , chiller pressure sensor 65c, evaporator pressure sensor 65e, high temperature side heat medium temperature sensor 66a, first low temperature side heat medium temperature sensor 67a, second low temperature side heat medium temperature sensor 67b, third low temperature side heat medium temperature sensor 67c, A control sensor group such as a battery temperature sensor 68 and an air conditioning air temperature sensor 69 is connected. Detection signals from a group of sensors for control are input to the control device 50 .

The inside air temperature sensor 61 is an inside air temperature detection unit that detects the vehicle interior temperature (inside air temperature) Tr. The outside air temperature sensor 62 is an outside air temperature detection unit that detects the vehicle outside temperature (outside air temperature) Tam. The solar radiation sensor 63 is a solar radiation amount detection unit that detects the solar radiation amount As irradiated into the vehicle interior.

The chiller temperature sensor 64c is a chiller outlet side refrigerant temperature detection section that detects the chiller side refrigerant temperature Tc, which is the temperature of the refrigerant flowing out of the refrigerant passage of the chiller 18 . The evaporator temperature sensor 64 e is an evaporator temperature detection unit that detects the refrigerant evaporation temperature (evaporator temperature) Tefin in the indoor evaporator 16 . Specifically, the evaporator temperature sensor 64e of the present embodiment detects the heat exchange fin temperature of the indoor evaporator 16 .

The high-pressure sensor 65a is a high-pressure refrigerant pressure detection unit that detects the high-pressure refrigerant pressure Pd, which is the pressure of the high-pressure refrigerant discharged from the compressor 11. The chiller pressure sensor 65c is a chiller-side refrigerant pressure detection unit that detects the chiller-side refrigerant pressure Pc, which is the pressure of the refrigerant in the refrigerant passage of the chiller 18 . The evaporator pressure sensor 65 e is an evaporator-side refrigerant pressure detection unit that detects the evaporator-side refrigerant pressure Pe, which is the pressure of the refrigerant in the indoor evaporator 16 .

A high temperature side heat medium temperature sensor 66 a is a high temperature side heat medium temperature detection unit that detects a high temperature side heat medium temperature TWH that is the temperature of the high temperature side heat medium flowing into the heater core 23 .

The first low temperature side heat medium temperature sensor 67a is a first low temperature side heat medium temperature detection unit that detects a first low temperature side heat medium temperature TWL1, which is the temperature of the low temperature side heat medium flowing into the cooling water passage 80a of the battery 80. be.

The second low-temperature side heat medium temperature sensor 67b detects a second low-temperature side heat medium temperature TWL2, which is the temperature of the low-temperature side heat medium flowing out of the cooling water passage of the high-voltage device 81. is. Specifically, the second low-temperature-side heat medium temperature sensor 67b of the present embodiment detects the temperature of the low-temperature-side heat medium immediately after it flows out from the cooling water passage 84a of the transaxle 84 .

The third low temperature side heat medium temperature sensor 67c is a third low temperature side heat medium temperature detection unit that detects a third low temperature side heat medium temperature TWL3, which is the temperature of the low temperature side heat medium immediately after flowing out from the low temperature side radiator 35. .

The battery temperature sensor 68 is a battery temperature detection unit that detects the battery temperature TB, which is the temperature of the battery 80 . The battery temperature sensor 68 of this embodiment has a plurality of temperature sensors and detects temperatures at a plurality of locations of the battery 80 . Therefore, the control device 50 can detect the temperature difference between the battery cells forming the battery 80 . Furthermore, as the battery temperature TB, an average value of detection values of a plurality of temperature sensors is used.

The air-conditioning air temperature sensor 69 is an air-conditioning air temperature detection unit that detects the air temperature TAV, which is the temperature of the air blown from the mixing space 46 into the vehicle interior.

Furthermore, an air conditioning operation panel 70 is connected to the input side of the control device 50, as shown in FIG. An air-conditioning operation panel 70 is arranged near the instrument panel in the front part of the passenger compartment. Operation signals from various operation switches provided on an operation panel 70 for air conditioning are input to the control device 50 .

Specific examples of the various operation switches provided on the operation panel 70 for air conditioning include an auto switch, an air conditioner switch, an air volume setting switch, a temperature setting switch, a defrosting permission switch 70a, and the like.

The auto switch is an operation unit that allows the user to set or cancel the automatic control operation of the cabin air conditioning. The air conditioner switch is an operation unit for requesting that the indoor evaporator 16 cool the blown air. The air volume setting switch is an operation unit for manually setting the air volume of the indoor fan 42 by the user. The temperature setting switch is an operation unit for the user to set the set temperature Tset inside the vehicle compartment. The defrosting permission switch 70a is an operation unit for allowing the user to perform the defrosting operation.

In addition, the control device 50 can store whether or not the defrosting operation has been performed since the user started the vehicle system.

In addition, the controller 50 can measure and store the startup elapsed time Tm1, the defrosting elapsed time Tm2, and the defrosting time Tmd. The activation elapsed time Tm1 is the elapsed time after the vehicle system is activated. The defrosting elapsed time Tm2 is the elapsed time since the previous defrosting operation ended. The defrosting time Tmd is the elapsed time after starting the defrosting operation.

The control device 50 is integrally configured with a control unit that controls various controlled devices connected to the output side. In the control device 50, the configuration (hardware and software) that controls the operation of each controlled device constitutes a control unit that controls the operation of each controlled device. For example, in the control device 50, the configuration for controlling the refrigerant discharge capacity of the compressor 11 constitutes a discharge capacity control section 50a.

Next, the operation of the heat pump cycle device 1 applied to the vehicle air conditioner of this embodiment having the above configuration will be described. The heat pump cycle device 1 switches the circuit configurations of the heat pump cycle 10, the high temperature side heat medium circuit 20, and the low temperature side heat medium circuit 30 during normal operation for air conditioning the vehicle interior and adjusting the temperature of the onboard equipment, and operates in various operation modes. can be switched.

The switching of the operation mode during normal operation is performed by executing a control program stored in the control device 50 in advance. The control program is executed not only when the vehicle system is activated, but also when the battery 80 is being charged from the external power supply.

In the main routine of the control program, the detection signals of the above-described sensor group and the operation signals of the operation switches of the operation panel 70 are read at predetermined intervals. Further, when the auto switch of the operation panel 70 is turned on (ON) and automatic control operation of the vehicle interior air conditioning is set, the amount of blown air blown into the vehicle interior is controlled based on the read detection signal and operation signal. A target outlet temperature TAO, which is a target temperature, is calculated.

The target blowing temperature TAO is calculated using the following formula F1.
TAO=Kset×Tset−Kr×Tr−Kam×Tam−Ks×As+C (F1)
Note that Tset is the set temperature in the passenger compartment set by the temperature setting switch on the operation panel 70 . Tr is the internal temperature detected by the internal temperature sensor 61 . Tam is the outside temperature detected by the outside temperature sensor 62 . As is the amount of solar radiation detected by the solar radiation sensor 63 . Kset, Kr, Kam, and Ks are control gains, and C is a correction constant. Detailed operation of each operation mode will be described below.

(a) Single Cooling Mode The single cooling mode is an operation mode in which the vehicle interior is cooled by blowing cooled air into the vehicle interior without cooling the battery 80 . In the control program of the present embodiment, an operation mode for cooling the passenger compartment is executed when the target air temperature TAO is in the low temperature range or when the outside air temperature Tam is relatively high. do.

In the heat pump cycle 10 in the single cooling mode, the control device 50 puts the cooling expansion valve 15a in a throttled state that exerts a refrigerant decompression action, and puts the cooling expansion valve 15b in a fully closed state.

Therefore, in the single cooling mode heat pump cycle 10, as shown in FIG. 16, the evaporating pressure regulating valve 17, and the suction side of the compressor 11, in that order.

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11 so that the evaporator temperature Tefin detected by the evaporator temperature sensor 64e approaches the target evaporator temperature TEO. The target evaporator temperature TEO is determined by referring to a control map stored in advance in the controller 50 based on the target outlet temperature TAO.

In addition, the control device 50 controls the degree of throttle opening of the cooling expansion valve 15a so that the degree of superheat SH1 of the refrigerant on the outlet side of the indoor evaporator 16 reaches a predetermined reference degree of superheat KSH (5° C. in this embodiment). Control to get closer. The degree of superheat SH1 can be determined based on the evaporator temperature Tefin and the evaporator-side refrigerant pressure Pe detected by the evaporator pressure sensor 65e.

In addition, in the high temperature side heat medium circuit 20 in the single cooling mode, the control device 50 operates the high temperature side pump 21 so as to exhibit a predetermined reference pumping capability.

Further, the control device 50 operates the high-temperature side flow control valve 22 so that the high-temperature side heat medium temperature TWH detected by the high-temperature side heat medium temperature sensor 66a approaches a predetermined reference high-temperature side heat medium temperature KTWH. to control.

Therefore, the high temperature side flow control valve 22 causes the high temperature side heat medium to flow out to the heater core 23 side and the high temperature side radiator 25 side so that the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH. Adjust the flow rate ratio with the flow rate of the high temperature side heat medium. The reference high temperature side heat medium temperature KTWH is set to a value that can appropriately heat the blown air when the high temperature side heat medium is caused to flow into the heater core 23 .

Furthermore, even if the entire flow rate of the high temperature side heat medium that has flowed into the high temperature side flow control valve 22 is allowed to flow out to the heater core 23 side, the control device 50 keeps the high temperature side heat medium temperature TWH at the reference high temperature side heat medium temperature KTWH. When it does not reach, the high voltage heater 26 is caused to generate heat. Then, the control device 50 controls the amount of heat generated by the high voltage heater 26 so that the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH.

Here, the operation mode for cooling the interior of the vehicle is executed when the target blowout temperature TAO is in the low temperature range. Therefore, in the single cooling mode, the amount of heat radiated from the high-temperature side heat medium to the blast air by the heater core 23 tends to decrease. Therefore, in the single cooling mode, the flow rate of the high temperature side heat medium flowing out to the high temperature side radiator 25 side tends to be larger than the flow rate of the high temperature side heat medium flowing out from the high temperature side flow control valve 22 to the heater core 23 side.

Therefore, in FIG. 6, the flow of the high temperature side heat medium flowing out from the high temperature side flow control valve 22 to the heater core 23 side is indicated by a thick dashed line. flow is indicated by a thick solid line.

In addition, in the low temperature side heat medium circuit 30 in the independent cooling mode, the control device 50 stops the first low temperature side pump 31a and operates the second low temperature side pump 31b so as to exhibit a predetermined reference pumping capability.
For the five-way valve 32, the control device 50 controls the second low temperature side heat medium temperature TWL2 detected by the second low temperature side heat medium temperature sensor 67b to reach the predetermined second reference low temperature side heat medium temperature KTWL2. Control the movement to get closer.

Therefore, the five-way valve 32 adjusts the flow rate of the low temperature side heat medium flowing out to the low temperature side radiator 35 side and the bypass passage 38 side so that the second low temperature side heat medium temperature TWL2 approaches the second reference low temperature side heat medium temperature KTWL2. Adjust the flow ratio with the flow rate of the low temperature side heat medium flowing out to.

The second reference low-temperature side heat medium temperature KTWL2 is obtained by causing the low-temperature side heat medium pressure-fed from the second low-temperature side pump 31b to flow into the cooling water passage of the high-power system device 81, thereby setting the temperature of the high-power device 81 to the reference heat resistance temperature. It is set to a value that can be maintained below the temperature.

Here, the operation mode for cooling the vehicle interior is executed when the outside air temperature Tam is relatively high. Therefore, in the independent cooling mode, the high-voltage equipment 81 heats the low-temperature side heat medium, and the temperature of the low-temperature side heat medium circulating in the heat storage circuit tends to rise. Therefore, as shown in FIG. 6, the five-way valve 32 in the single cooling mode often switches the circuit configuration of the low temperature side heat medium circuit 30 to the device cooling circuit.

Also, in the indoor air conditioning unit 40 in the single cooling mode, the control device 50 operates the indoor fan 42 so as to exhibit the target air blowing capacity. The target blowing capacity is determined by referring to a control map stored in advance in the control device 50 based on the target blowing temperature TAO.

In the control map for the indoor fan 42, the blowing capacity is maximized when the target outlet temperature TAO is in the extremely low temperature range (that is, maximum cooling) or the extremely high temperature range (that is, maximum heating). decide. Further, the blowing capacity is determined to decrease as the target blowing temperature TAO moves from the extremely low temperature range or the extremely high temperature range to the intermediate temperature range. Then, when the target blowout temperature TAO is in the intermediate temperature range, the blowing capacity is determined to be the minimum.

As for the electric actuator for the air mix door, the controller 50 changes the opening degree of the air mix door 44 so that the air temperature TAV detected by the conditioned air temperature sensor 69 approaches the target outlet temperature TAO.

In addition, based on the target blowout temperature TAO, the control device 50 refers to a control map stored in advance in the control device 50 to control the operation of the inside/outside air switching device 43 and the electric actuator for the blowout mode door.

Therefore, in the heat pump cycle 10 in the single cooling mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 16 functions as an evaporator. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the indoor evaporator 16, heat is exchanged between the low-pressure refrigerant and the blown air to cool the blown air.

In addition, in the high temperature side heat medium circuit 20 in the independent cooling mode, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows through the heater core 23 and the high temperature side radiator 25 depending on the operating state of the high temperature side flow control valve 22. flow into As a result, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH.

In the heater core 23, heat is exchanged between the high-temperature heat medium and the blast air according to the degree of opening of the air mix door 44, and the blast air is heated. In the high temperature side radiator 25, heat is exchanged between the high temperature side heat medium and the outside air, and the heat of the high temperature side heat medium is radiated to the outside air.

In addition, in the low-temperature side heat medium circuit 30 in the independent cooling mode, the low-temperature side heat medium pumped from the second low-temperature side pump 31 b flows through the cooling water passages of the high-voltage equipment 81 . As a result, the heavy electrical equipment 81 is cooled. In other words, the low-temperature heat medium is heated in the cooling water passage of the high-voltage equipment 81 .

The low-temperature side heat medium flowing out of the cooling water passage of the high-voltage equipment 81 flows into the low-temperature side radiator 35 and the bypass passage 38 according to the operating state of the five-way valve 32 . As a result, the second low temperature side heat medium temperature TWL2 approaches the second reference low temperature side heat medium temperature KTWL2. In the low temperature side radiator 35, heat is exchanged between the low temperature side heat medium and the outside air that has passed through the high temperature side radiator 25, and the heat of the low temperature side heat medium is radiated to the outside air.

Also, in the indoor air conditioning unit 40 in the single cooling mode, the air blown from the indoor blower 42 is cooled by the indoor evaporator 16 . The blown air cooled by the indoor evaporator 16 is adjusted in temperature by adjusting the opening of the air mix door 44 so as to approach the target blowout temperature TAO. Then, the temperature-controlled blowing air is blown into the vehicle interior, thereby cooling the vehicle interior.

(b) Single Dehumidification and Heating Mode The single dehumidification and heating mode is an operation mode in which the dehumidification and heating of the vehicle interior is performed by reheating the cooled and dehumidified blast air and blowing it into the vehicle interior without cooling the battery 80. is.

In the heat pump cycle 10 in the single dehumidifying and heating mode, the controller 50 throttles the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the single dehumidifying and heating mode, as shown in FIG. The refrigerant circuit is switched to circulate in the order of the evaporator 16, the evaporating pressure regulating valve 17, and the suction side of the compressor 11. FIG. At the same time, the refrigerant discharged from the compressor 11 is switched to a refrigerant circuit that circulates through the refrigerant passage of the water-refrigerant heat exchanger 12, the receiver 13, the cooling expansion valve 15b, the chiller 18, and the suction side of the compressor 11 in that order. That is, the indoor evaporator 16 and the chiller 18 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening of the cooling expansion valve 15a in the same manner as in the single cooling mode. Further, the control device 50 controls the throttle opening degree of the cooling expansion valve 15b so that the chiller-side refrigerant temperature Tc detected by the chiller temperature sensor 64c is lower than the outside air temperature Tam.

In addition, in the high temperature side heat medium circuit 20 in the independent dehumidifying and heating mode, the control device 50 operates the high temperature side pump 21 and controls the operation of the high temperature side flow control valve 22 in the same manner as in the independent cooling mode.

Here, in the single dehumidification heating mode, the heater core 23 reheats the blown air cooled by the indoor evaporator 16 . Therefore, in the high temperature side flow control valve 22 in the single dehumidification and heating mode, as shown in FIG.

In addition, in the low-temperature side heat medium circuit 30 in the single dehumidifying and heating mode, the control device 50 operates the first low-temperature side pump 31a and the second low-temperature side pump 31b so as to exhibit a predetermined reference pumping capability. Further, the control device 50 controls the operation of the five-way valve 32 so that the heat absorbing circuit and the heat storing circuit are simultaneously formed as shown in FIG.

Further, in the indoor air conditioning unit 40 in the single dehumidifying and heating mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the single cooling mode. controls the operation of

Therefore, in the heat pump cycle 10 in the single dehumidifying and heating mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 16 and chiller 18 function as evaporators. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the indoor evaporator 16, heat is exchanged between the low-pressure refrigerant and the blown air to cool the blown air. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

In addition, in the high temperature side heat medium circuit 20 in the single dehumidifying and heating mode, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH, as in the single cooling mode. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated.

In addition, in the low temperature side heat medium circuit 30 in the single dehumidification heating mode, the low temperature side heat medium pumped from the first low temperature side pump 31a circulates in the heat absorption circuit. In the low temperature side radiator 35, heat is exchanged between the low temperature side heat medium and the outside air that has passed through the high temperature side radiator 25, and the low temperature side heat medium absorbs heat from the outside air. In the chiller 18, the low-pressure refrigerant and the low-temperature side heat medium exchange heat, and the low-pressure refrigerant absorbs heat from the low-temperature side heat medium.

The low temperature side heat medium pumped from the second low temperature side pump 31b circulates in the heat storage circuit. As a result, the low-temperature side heat medium circulating in the heat storage circuit is heated by the high-voltage equipment 81 . That is, the heat generated by the high-voltage equipment 81 is stored in the low temperature side heat medium circulating in the heat storage circuit.

In addition, in the indoor air conditioning unit 40 in the single dehumidifying and heating mode, the air blown from the indoor blower 42 is cooled by the indoor evaporator 16 and dehumidified. The temperature of the air cooled and dehumidified by the indoor evaporator 16 is adjusted by adjusting the opening of the air mix door 44 so as to approach the target blowout temperature TAO. Dehumidification and heating of the interior of the vehicle are achieved by blowing out the temperature-adjusted blown air into the interior of the vehicle.

As is clear from the above description, in the single dehumidifying and heating mode, the low-pressure refrigerant absorbs the heat of the outside air via the low-temperature side heat medium circulating in the heat absorption circuit of the low-temperature side heat medium circuit 30, and the blown air is used as a heat source to heat the Therefore, the chiller 18 and the low-temperature side radiator 35 of the low-temperature side heat medium circuit 30 form a heat absorbing portion that causes the low-pressure refrigerant decompressed by the cooling expansion valve 15b to absorb the heat of the outside air.

(c) Single Heating Mode The single heating mode is an operation mode in which the vehicle interior is heated by blowing heated air into the vehicle interior without cooling the battery 80 . In the control program of the present embodiment, an operation mode for heating the passenger compartment is executed when the target air temperature TAO is in the high temperature range or when the outside air temperature Tam is relatively low. do.

In the heat pump cycle 10 in the single heating mode, the controller 50 fully closes the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

For this reason, in the heat pump cycle 10 in the single heating mode, as shown in FIG. , to the refrigerant circuit that circulates in the order of the suction side of the compressor 11 .

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11 so that the high-pressure refrigerant pressure Pd detected by the high-pressure sensor 65a approaches the target high-pressure PDO. The target high pressure PDO is determined by referring to a control map stored in advance in the controller 50 based on the target outlet temperature TAO.

In addition, the controller 50 controls the throttle opening of the cooling expansion valve 15b so that the degree of superheat SH2 of the refrigerant flowing out of the refrigerant passage of the chiller 18 approaches a predetermined reference degree of superheat KSH. The degree of superheat SH2 can be determined based on the chiller-side refrigerant temperature Tc detected by the chiller temperature sensor 64c and the chiller-side refrigerant pressure Pc detected by the chiller pressure sensor 65c.

In addition, in the high temperature side heat medium circuit 20 in the single heating mode, the control device 50 operates the high temperature side pump 21 and controls the operation of the high temperature side flow control valve 22 as in the single cooling mode. In the high temperature side flow control valve 22 in the individual heating mode, as shown in FIG. 8, the entire flow rate of the high temperature side heat medium pressure-fed from the high temperature side pump 21 flows out to the heater core 23 side, as in the individual dehumidifying heating mode. There are many things.

In addition, in the low temperature side heat medium circuit 30 in the single heating mode, the control device 50 operates the first low temperature side pump 31a and the second low temperature side pump 31b in the same manner as in the single dehumidifying and heating mode. Further, the control device 50 controls the operation of the five-way valve 32 so that the heat absorption circuit and the heat storage circuit are simultaneously formed, as in the single dehumidifying and heating mode, as shown in FIG.

Further, in the indoor air conditioning unit 40 in the single heating mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the single cooling mode. control the actuation.

Here, the operation mode for heating the interior of the vehicle is executed when the outside air temperature Tam is relatively low. Therefore, in the single heating mode, the control device 50 often adjusts the opening degree of the air mix door 44 so that the entire amount of air blown from the indoor fan 42 flows into the heater core 23 side.

Therefore, in the heat pump cycle 10 in the single heating mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the chiller 18 functions as an evaporator. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

Also, in the high temperature side heat medium circuit 20 in the single heating mode, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH, as in the single cooling mode. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated.

In addition, in the low temperature side heat medium circuit 30 in the single heating mode, the low temperature side heat medium pumped from the first low temperature side pump 31a circulates in the heat absorption circuit in the same manner as in the single dehumidifying and heating mode. In the low temperature side radiator 35, heat is exchanged between the low temperature side heat medium and the outside air that has passed through the high temperature side radiator 25, and the low temperature side heat medium absorbs heat from the outside air. In the chiller 18, the low-pressure refrigerant and the low-temperature side heat medium exchange heat, and the low-pressure refrigerant absorbs heat from the low-temperature side heat medium.

The low temperature side heat medium pumped from the second low temperature side pump 31b circulates in the heat storage circuit. As a result, the heat generated by the high-voltage equipment 81 is stored in the low-temperature side heat medium circulating in the heat storage circuit.

Also, in the indoor air conditioning unit 40 in the single heating mode, the air blown from the indoor blower 42 passes through the indoor evaporator 16 . The temperature of the blown air that has passed through the indoor evaporator 16 is adjusted so as to approach the target blowout temperature TAO by adjusting the opening of the air mix door 44 . Then, the temperature-controlled blowing air is blown into the vehicle interior, thereby heating the vehicle interior.

Furthermore, in the individual heating mode, the chiller 18 and the low-temperature side radiator 35 of the low-temperature side heat medium circuit 30 form a heat absorption portion, as in the individual dehumidifying and heating mode.

(d) Cooling/cooling mode The cooling/cooling mode is an operation mode in which the battery 80 is cooled and the vehicle interior is cooled. The control program of the present embodiment executes an operation mode for cooling the battery 80 when the battery temperature TB detected by the battery temperature sensor 68 is equal to or higher than a predetermined reference upper limit temperature KTBH.

In the heat pump cycle 10 in the cooling mode, the controller 50 throttles the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the cooling cooling mode, as shown in FIG. 9, the refrigerant circuit is switched to the same refrigerant circuit as in the single dehumidifying heating mode. That is, the indoor evaporator 16 and the chiller 18 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening of the cooling expansion valve 15a in the same manner as in the single cooling mode.

Further, the control device 50 controls the throttle opening degree of the cooling expansion valve 15b so that the first low-temperature-side heat-medium temperature TWL1 detected by the first low-temperature-side heat-medium temperature sensor 67a reaches a predetermined first reference low-temperature-side temperature. The temperature is controlled so as to approach the heat medium temperature KTWL1. The first reference low-temperature-side heat medium temperature KTWL1 is set to a value that allows the battery 80 to be appropriately cooled when the low-temperature-side heat medium is caused to flow into the cooling water passage 80a of the battery 80 .

In addition, in the high temperature side heat medium circuit 20 in the cooling cooling mode, the control device 50 operates the high temperature side pump 21 and controls the operation of the high temperature side flow control valve 22 as in the single cooling mode.

Here, in the cooling cooling mode, as in the single cooling mode, the amount of heat released by the high-temperature-side heat medium in the heater core 23 to the blown air is reduced. Furthermore, in the cooling mode, the heat absorbed by the low-pressure refrigerant from the low-temperature heat medium in the chiller 18 (that is, the waste heat of the battery 80) must also be released to the outside air via the high-temperature heat medium.

Therefore, in the high-temperature side flow control valve 22 in the cooling mode, as shown in FIG. 9, the high-temperature side heat transfer medium pressure-fed from the high-temperature side pump 21 often flows out to the high-temperature side radiator 25 side. .

In addition, in the low temperature side heat medium circuit 30 in the cooling cooling mode, the control device 50 operates the first low temperature side pump 31a and the second low temperature side pump 31b so as to exhibit a predetermined reference pumping capability.

For the five-way valve 32, the control device 50 controls the second low temperature side heat medium temperature TWL2 detected by the second low temperature side heat medium temperature sensor 67b to reach the predetermined second reference low temperature side heat medium temperature KTWL2. At the same time as controlling the operation to approach, as shown in FIG. 9, the operation is controlled so that a circuit for cooling the battery is formed.

Here, in the cooling cooling mode, the temperature of the low temperature side heat medium circulating in the heat storage circuit tends to rise, as in the independent cooling mode. Therefore, in the five-way valve 32 in the cooling cooling mode, as shown in FIG. 9, the low-temperature side heat medium circuit 30 is often switched to a circuit configuration in which the device cooling circuit and the battery cooling circuit are formed at the same time.

In addition, in the indoor air conditioning unit 40 in the cooling cooling mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the independent cooling mode. control the actuation.

Therefore, in the heat pump cycle 10 in the cooling cooling mode, a vapor compression refrigeration cycle similar to that in the single dehumidifying heating mode is formed. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the indoor evaporator 16, heat is exchanged between the low-pressure refrigerant and the blown air to cool the blown air. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

Also, in the high temperature side heat medium circuit 20 in the cooling cooling mode, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH, as in the single cooling mode. In the high temperature side radiator 25, heat is exchanged between the high temperature side heat medium and the outside air, and the heat of the high temperature side heat medium is radiated to the outside air.

In addition, in the low-temperature side heat medium circuit 30 in the cooling cooling mode, the low-temperature side heat medium pumped from the first low-temperature side pump 31a is cooled by the chiller 18 by exchanging heat with the low-pressure refrigerant. As a result, the first low temperature side heat medium temperature TWL1 approaches the first reference low temperature side heat medium temperature KTWL1. Then, when the low temperature side heat medium cooled by the chiller 18 flows through the cooling water passage 80a of the battery 80, the battery 80 is cooled.

The low temperature side heat medium pressure-fed from the second low temperature side pump 31b flows into the low temperature side radiator 35 and the bypass passage 38 according to the operating state of the five-way valve 32, as in the single cooling mode. As a result, the second low temperature side heat medium temperature TWL2 approaches the second reference low temperature side heat medium temperature KTWL2. In the low temperature side radiator 35, heat is exchanged between the low temperature side heat medium and the outside air that has passed through the high temperature side radiator 25, and the heat of the low temperature side heat medium is radiated to the outside air.

In addition, in the indoor air conditioning unit 40 in the cooling cooling mode, the air blown from the indoor blower 42 is cooled by the indoor evaporator 16 in the same manner as in the independent cooling mode. The blown air cooled by the indoor evaporator 16 is adjusted in temperature by adjusting the opening of the air mix door 44 so as to approach the target blowout temperature TAO. Then, the temperature-controlled blowing air is blown into the vehicle interior, thereby cooling the vehicle interior.

(e) Cooling, Dehumidifying, and Heating Mode The cooling, dehumidifying, and heating mode is an operation mode that cools the battery 80 and performs dehumidifying and heating in the passenger compartment.

In the heat pump cycle 10 in the cooling/dehumidifying/heating mode, the controller 50 throttles the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the cooling dehumidification heating mode, as shown in FIG. 10, the refrigerant circuit is switched to the same refrigerant circuit as in the single dehumidification heating mode. That is, the indoor evaporator 16 and the chiller 18 are switched to a refrigerant circuit that is connected in parallel with respect to the refrigerant flow.

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11, the throttle opening degree of the cooling expansion valve 15a, and the throttle opening degree of the cooling expansion valve 15b in the same manner as in the cooling mode.

In addition, in the high temperature side heat medium circuit 20 in the cooling dehumidification heating mode, the control device 50 operates the high temperature side pump 21 and controls the operation of the high temperature side flow control valve 22 in the same manner as in the single dehumidification heating mode.

Here, in the cooling dehumidification heating mode, it is necessary to reheat the blown air cooled by the indoor evaporator 16 by the heater core 23, as in the single dehumidification heating mode. At this time, in the cooling/dehumidifying/heating mode, the heat absorbed by the low-pressure refrigerant from the low-temperature side heat medium in the chiller 18 (that is, the waste heat of the battery 80) can be used as a heat source for heating the high-temperature side heat medium. can. On the other hand, as in the cooling mode, when the low-pressure refrigerant absorbs heat from the low-temperature side heat medium in the chiller 18 and the excess heat becomes excessive, it is necessary to dissipate the heat to the outside air via the high-temperature side heat medium.

Therefore, in the cooling dehumidifying heating mode, the flow rate of the high temperature side heat medium flowing out from the high temperature side flow control valve 22 to the high temperature side radiator 25 side increases more than in the single dehumidifying heating mode. Therefore, in FIG. 10, the flow of the high temperature side heat medium flowing out from the high temperature side flow control valve 22 to the heater core 23 side is indicated by a thick solid line. flow is indicated by a thick dashed line.

In addition, in the low temperature side heat medium circuit 30 in the cooling dehumidification heating mode, the control device 50 operates the first low temperature side pump 31a and the second low temperature side pump 31b in the same manner as in the cooling cooling mode. The controller 50 also controls the operation of the five-way valve 32 in the same manner as in the cooling mode. FIG. 10 shows the flow of the low temperature side heat medium when the five-way valve 32 switches the low temperature side heat medium circuit 30 to a circuit configuration in which the battery cooling circuit and the device cooling circuit are simultaneously formed.

In addition, in the indoor air conditioning unit 40 in the cooling dehumidifying heating mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the single cooling mode. controls the operation of

Therefore, in the heat pump cycle 10 in the cooling dehumidification heating mode, a vapor compression refrigeration cycle similar to that in the single dehumidification heating mode is formed. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the indoor evaporator 16, heat is exchanged between the low-pressure refrigerant and the blown air to cool the blown air. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

Also, in the high temperature side heat medium circuit 20 in the cooling dehumidification heating mode, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH, as in the single cooling mode. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated. In the high temperature side radiator 25, heat is exchanged between the high temperature side heat medium and the outside air, and the heat of the high temperature side heat medium is radiated to the outside air.

Also, in the low temperature side heat medium circuit 30 in the cooling dehumidifying heating mode, the first low temperature side heat medium temperature TWL1 approaches the first reference low temperature side heat medium temperature KTWL1, as in the cooling cooling mode. Then, when the low temperature side heat medium cooled by the chiller 18 flows through the cooling water passage 80a of the battery 80, the battery 80 is cooled.

The low temperature side heat medium pressure-fed from the second low temperature side pump 31b flows into the low temperature side radiator 35 and the bypass passage 38 according to the operating state of the five-way valve 32, as in the cooling cooling mode. As a result, the second low temperature side heat medium temperature TWL2 approaches the second reference low temperature side heat medium temperature KTWL2. In the low temperature side radiator 35, heat is exchanged between the low temperature side heat medium and the outside air that has passed through the high temperature side radiator 25, and the heat of the low temperature side heat medium is radiated to the outside air.

In addition, in the indoor air conditioning unit 40 in the cooling dehumidifying heating mode, the air blown from the indoor blower 42 is cooled and dehumidified by the indoor evaporator 16 as in the single dehumidifying heating mode. The temperature of the air cooled and dehumidified by the indoor evaporator 16 is adjusted by adjusting the opening of the air mix door 44 so as to approach the target blowout temperature TAO. Dehumidification and heating of the interior of the vehicle are achieved by blowing out the temperature-adjusted blown air into the interior of the vehicle.

(f) Cooling/heating mode The cooling/heating mode is an operation mode in which the battery 80 is cooled and the vehicle interior is heated.

In the heat pump cycle 10 in the cooling/heating mode, the controller 50 fully closes the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the cooling/heating mode, as shown in FIG. 11, the refrigerant circuit is switched to the same refrigerant circuit as in the single heating mode.

Also, the control device 50 controls the refrigerant discharge capacity of the compressor 11 in the same manner as in the single heating mode. Further, the controller 50 controls the throttle opening of the cooling expansion valve 15b in the same manner as in the cooling mode.

In addition, in the high temperature side heat medium circuit 20 in the cooling/heating mode, the control device 50 operates the high temperature side pump 21 and controls the operation of the high temperature side flow control valve 22 in the same manner as in the single heating mode. In the cooling/heating mode, as in the cooling/dehumidifying/heating mode, as shown in FIG. Drain the medium.

In addition, in the low temperature side heat medium circuit 30 in the cooling/heating mode, the control device 50 operates the first low temperature side pump 31a and the second low temperature side pump 31b as in the cooling/cooling mode. The controller 50 also controls the operation of the five-way valve 32 in the same manner as in the cooling mode. FIG. 11 shows the flow of the low temperature side heat medium when the five-way valve 32 switches the low temperature side heat medium circuit 30 to a circuit configuration in which a battery cooling circuit and a heat storage circuit are simultaneously formed.

In addition, in the indoor air conditioning unit 40 in the cooling/heating mode, the controller 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the single cooling mode. control the actuation.

Therefore, in the heat pump cycle 10 in the cooling/heating mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the chiller 18 functions as an evaporator. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

Also, in the high temperature side heat medium circuit 20 in the cooling/heating mode, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH, as in the single cooling mode. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated. In the high temperature side radiator 25, heat is exchanged between the high temperature side heat medium and the outside air, and the heat of the high temperature side heat medium is radiated to the outside air.

Also, in the low temperature side heat medium circuit 30 in the cooling/heating mode, the first low temperature side heat medium temperature TWL1 approaches the first reference low temperature side heat medium temperature KTWL1, as in the cooling/cooling mode. Then, when the low temperature side heat medium cooled by the chiller 18 flows through the cooling water passage 80a of the battery 80, the battery 80 is cooled.

The low temperature side heat medium pressure-fed from the second low temperature side pump 31b flows into the low temperature side radiator 35 and the bypass passage 38 according to the operating state of the five-way valve 32, as in the cooling cooling mode. As a result, the second low temperature side heat medium temperature TWL2 approaches the second reference low temperature side heat medium temperature KTWL2.

In addition, in the indoor air conditioning unit 40 in the cooling/heating mode, air blown from the indoor blower 42 passes through the indoor evaporator 16 as in the single heating mode. The temperature of the blown air that has passed through the indoor evaporator 16 is adjusted so as to approach the target blowout temperature TAO by adjusting the opening of the air mix door 44 . Then, the temperature-controlled blowing air is blown into the vehicle interior, thereby heating the vehicle interior.

(g) Single Cooling Mode The single cooling mode is an operation mode in which the battery 80 is cooled without air-conditioning the vehicle interior.

In the heat pump cycle 10 in the single cooling mode, the control device 50 fully closes the cooling expansion valve 15a and throttles the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the single cooling mode, as shown in FIG. 12, the refrigerant circuit is switched to the same refrigerant circuit as in the single heating mode.

In addition, the control device 50 controls the operation of the compressor 11 so that the predetermined reference refrigerant discharge capacity for the single cooling mode is exhibited. Further, the controller 50 controls the throttle opening of the cooling expansion valve 15b in the same manner as in the cooling mode.

Also, in the high temperature side heat medium circuit 20 in the independent cooling mode, the control device 50 operates the high temperature side pump 21 so as to exhibit a predetermined reference pumping capability. Further, the control device 50 controls the operation of the high temperature side flow control valve 22 so that the entire flow rate of the high temperature side heat medium that has flowed inside flows out to the high temperature side radiator 25 side.

In addition, in the low temperature side heat medium circuit 30 in the independent cooling mode, the control device 50 operates the first low temperature side pump 31a and the second low temperature side pump 31b so as to exhibit a predetermined reference pumping capability.

Also, the control device 50 controls the operation of the five-way valve 32 in the same manner as in the cooling mode. FIG. 12 shows the flow of the low temperature side heat medium when the five-way valve 32 switches the low temperature side heat medium circuit 30 to a circuit configuration in which a battery cooling circuit and a heat storage circuit are simultaneously formed.

Also, in the indoor air conditioning unit 40 in the independent cooling mode, the control device 50 stops the indoor blower 42 .

Therefore, in the heat pump cycle 10 in the single cooling mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the chiller 18 functions as an evaporator, as in the single heating mode. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the chiller 18, heat is exchanged between the low-pressure refrigerant and the low-temperature side heat medium to cool the low-temperature side heat medium.

Also, in the high temperature side heat medium circuit 20 in the cooling/heating mode, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 flows into the high temperature side radiator 25 . In the high temperature side radiator 25, heat is exchanged between the high temperature side heat medium and the outside air, and the heat of the high temperature side heat medium is radiated to the outside air.

Also, in the low temperature side heat medium circuit 30 in the cooling/heating mode, the first low temperature side heat medium temperature TWL1 approaches the first reference low temperature side heat medium temperature KTWL1, as in the cooling/cooling mode. Then, when the low temperature side heat medium cooled by the chiller 18 flows through the cooling water passage 80a of the battery 80, the battery 80 is cooled.

As described above, according to the heat pump cycle device 1 of the present embodiment, by switching the operation mode, it is possible to perform comfortable air conditioning in the vehicle compartment and appropriate temperature adjustment of the onboard equipment.

By the way, in the heat pump cycle device 1, the low temperature side radiator 35 of the low temperature side heat medium circuit 30 causes the low temperature side heat medium to absorb the heat of the outside air in the single dehumidifying and heating mode and the single heating mode. Then, in the chiller 18 of the heat pump cycle 10, the heat of the low temperature side heat medium is absorbed by the refrigerant, and in the water-refrigerant heat exchanger 12, the heat absorbed by the refrigerant is radiated to the high temperature side heat medium. Furthermore, the heater core 23 of the high-temperature-side heat medium circuit 20 radiates the heat of the high-temperature-side heat medium to the air to heat the air.

In other words, the heat pump cycle device 1 uses the heat of the outside air as a heat source for the blown air in the single dehumidifying and heating mode and the single heating mode. Therefore, if the single dehumidifying/heating mode or the single heating mode is executed when the outside temperature Tam is 0° C. or lower, the low temperature side radiator 35 may be frosted.

If frost forms on the low-temperature side radiator 35 during the individual dehumidification and heating mode and the individual heating mode, the heat exchange performance of the low-temperature side radiator 35 is reduced, and the heat of the outside air is sufficiently transferred to the low-temperature side heat medium. I can't make it absorb heat. As a result, the heater core 23 may become unable to heat the blown air.

On the other hand, in the heat pump cycle device 1 of the present embodiment, the control flow shown in FIG. Carry out frost operation.

The control flow shown in FIG. 13 is a subroutine that is executed at predetermined intervals when the single dehumidifying/heating mode or the single heating mode is selected in the main routine of the control program. Each control step shown in the flow chart of FIG. 13 is a function implementation part of the control device 50 .

First, in step S1 of FIG. 13, it is determined whether or not there is a defrosting request for the low temperature side radiator 35 that forms the heat absorbing portion.

More specifically, in step S1 of the present embodiment, when the third low temperature side heat medium temperature TWL3 detected by the third low temperature side heat medium temperature sensor 67c is lower than the reference defrost temperature KTWL, , it is determined that the low-temperature side radiator 35 is in a frosted state in which frost may occur. Further, in step S1, it is determined that there is a defrosting request when the frosted state time is equal to or longer than a predetermined reference frosting time KTmfr. In this embodiment, the reference frost formation time KTmfr is set to 10 seconds.

As shown in the control characteristic diagram of FIG. 14, the reference defrost temperature KTWL is determined to increase as the outside temperature Tam rises when the outside temperature Tam is below 0°C. In FIG. 14, when the point determined by the outside air temperature Tam and the third low-temperature heat medium temperature TWL3 is in the dotted hatched area, it is determined that the frost is formed.

If it is determined in step S1 that there is a defrosting request, the process proceeds to step S3. Moreover, when it is determined that there is no defrosting request in step S1, the defrosting operation is not executed and the process returns to the main routine.

In step S2, it is determined whether or not a condition for permitting execution of the defrosting operation is satisfied. Specifically, in step S2 of the present embodiment, when the defrosting permission switch 70a of the operation panel 70 is turned on (ON), it is determined that the permission condition is established.

When it is determined in step S2 that the permission condition is satisfied, the process proceeds to step S6, and the defrosting operation is performed. If it is determined in step S2 that the permission condition is not satisfied, the process proceeds to step S3.

In step S3, the storage circuit of the control device 50 is referenced to determine whether or not it is the first defrosting operation since the user started the vehicle system. In other words, in step S3, the storage circuit of the control device 50 is referred to, and it is determined whether or not the defrosting operation is performed for the first time after the so-called IG switch is turned on (turned on).

If it is determined in step S3 that it is the first defrosting operation, proceed to step S4. Moreover, when it determines with it not being the first defrosting operation in step S4, it progresses to step S5.

In step S4, it is determined whether or not the activation elapsed time Tm1 is greater than or equal to a predetermined activation standby time Tmi1.

The startup standby time Tmi1 is a value set to allow the low temperature side heat medium circulating in the heat storage circuit of the low temperature side heat medium circuit 30 to store the heat generated by the high power system device 81, which is the heat generating portion. Furthermore, the startup standby time Tmi1 is a value set so that the low-temperature side heat medium can store an amount of heat that can melt and remove frost on the low-temperature side radiator 35 . In this embodiment, the startup standby time Tmi1 is set to 10 minutes.

In other words, if the activation elapsed time Tm1 after the vehicle system is activated is equal to or longer than the activation waiting time Tmi1, the low-temperature side heat medium circulating in the heat storage circuit is caused to flow into the low-temperature side radiator 35. Frost on the radiator 35 can be melted and removed. The startup waiting time Tmi1 is a value obtained by experimental or experimental means.

If it is determined in step S4 that the startup elapsed time Tm1 is equal to or longer than the startup standby time Tmi1, the process proceeds to step S6 and the defrosting operation is performed. If it is not determined in step S4 that the activation elapsed time Tm1 is greater than or equal to the activation waiting time Tmi1, the process returns to the main routine. That is, even if it is determined in step S1 that there is a defrosting request, execution of the defrosting operation is prohibited.

In step S5, it is determined whether the defrost elapsed time Tm2 is equal to or longer than a predetermined defrost standby time Tmi2.

During the defrost standby time Tmi2, similarly to the startup standby time Tmi1, the low temperature side heat medium circulating in the heat storage circuit of the low temperature side heat medium circuit 30 can melt and remove frost adhered to the low temperature side radiator 35. This value is set so that the amount of heat can be stored.

In other words, if the defrosting elapsed time Tm2 from the end of the previous defrosting operation is equal to or longer than the defrosting standby time Tmi2, the low temperature side heat medium circulating in the heat storage circuit is caused to flow into the low temperature side radiator 35. As a result, the frost on the low-temperature side radiator 35 can be melted and removed. Furthermore, the defrosting standby time Tmi2 is set to be longer than the activation standby time Tmi1. In this embodiment, the defrosting standby time Tmi2 is set to 30 minutes.

When it is determined in step S5 that the defrosting elapsed time Tm2 is equal to or longer than the defrosting standby time Tmi2, the process proceeds to step S6 and the defrosting operation is performed. If it is not determined in step S5 that the defrost elapsed time Tm2 is equal to or longer than the defrost standby time Tmi2, the process returns to the main routine. That is, even if it is determined in step S1 that there is a defrosting request, execution of the defrosting operation is prohibited.

In step S6, defrosting operation is performed. A detailed operation of the defrosting operation will be described later. Subsequently, in step S7, it is determined whether or not a defrosting end condition for ending defrosting is satisfied.

Specifically, in step S7 of the embodiment, when the third low-temperature-side heat medium temperature TWL3 is equal to or higher than the reference defrosting temperature KTWL, the defrosting operation can be terminated. I judge. Further, it is determined that the defrosting end condition is met when the time during which the defrosting is possible is equal to or longer than the predetermined reference end time KTme. In this embodiment, the reference end time KTme is set to 10 seconds.

Also, in step S7 of the present embodiment, it is determined that the defrosting end condition is met when the outside air temperature Tam is equal to or higher than the reference end outside temperature KTam. In this embodiment, the reference end outside temperature KTam is set at 10°C. Further, in step S7 of the present embodiment, when the defrosting time Tmd becomes equal to or longer than a predetermined reference defrosting time KTmd, it is determined that the defrosting end condition is met. In this embodiment, the reference defrost time KTmd is set to 5 minutes.

If it is determined in step S7 that the defrosting end condition is met, the process returns to the main routine. Moreover, when it is not determined in step S7 that the defrosting end condition is satisfied, the process returns to step S6, and the defrosting operation is continued.

As is clear from the above description, step S1 of the present embodiment is a frost formation determination unit that determines whether frost has formed on the low-temperature side radiator 35 that forms the heat absorption unit. Further, steps S6 and S7 are a defrosting operation executing section that executes a defrosting operation for defrosting the heat absorbing portion. Further, steps S4 and S5 form a defrosting operation prohibition section that prohibits execution of the defrosting operation. Further, step S2 forms a defrosting operation permitting section that causes the defrosting operation executing section to execute the defrosting operation regardless of whether or not the defrosting operation prohibiting section prohibits execution of the defrosting operation.

Next, the detailed operation of the defrosting operation will be explained. The defrosting operation includes a dehumidifying/heating defrosting mode and a heating defrosting mode. The dehumidifying/heating defrosting mode is a defrosting operation that is performed when frost forms on the low-temperature side radiator 35 during execution of the single dehumidifying/heating mode. The heating defrosting mode is a defrosting operation that is performed when frost forms on the low-temperature side radiator 35 during execution of the single heating mode.

(h-1) Dehumidification/heating defrost mode In the heat pump cycle 10 in the dehumidification/heating defrost mode, the controller 50 throttles the cooling expansion valve 15a and fully closes the cooling expansion valve 15b.

Therefore, in the heat pump cycle 10 in the dehumidifying/heating/defrosting mode, the refrigerant circuit is switched to the same refrigerant circuit as in the independent cooling mode, as indicated by the thick dashed line in FIG.

In addition, the control device 50 controls the refrigerant discharge capacity of the compressor 11 and the throttle opening of the cooling expansion valve 15a in the same manner as in the single cooling mode.

In addition, in the high-temperature side heat medium circuit 20 in the dehumidifying/heating/defrosting mode, the control device 50 operates the high-temperature side pump 21 so as to exhibit a predetermined reference pumping capability. 15, the control device 50 operates the high temperature side flow control valve 22 so that the entire flow rate of the high temperature side heat medium pressure-fed from the high temperature side pump 21 flows out to the heater core 23 side. Control.

In addition, the control device 50 controls the operation of the high voltage heater 26 so that the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH.

In addition, in the low temperature side heat medium circuit 30 in the dehumidification/heating defrost mode, the control device 50 stops the first low temperature side pump 31a and operates the second low temperature side pump 31b so as to exhibit a predetermined reference pumping capability. activate. Further, the control device 50 controls the operation of the five-way valve 32 so that a device cooling circuit is formed as shown in FIG.

In addition, in the indoor air conditioning unit 40 in the dehumidification/heating defrost mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the blowout mode door in the same manner as in the single cooling mode. Controls the operation of the electric actuator.

Therefore, in the heat pump cycle 10 in the dehumidifying/heating/defrosting mode, a vapor compression refrigeration cycle is formed in which the water-refrigerant heat exchanger 12 functions as a radiator and the indoor evaporator 16 functions as an evaporator. In the water-refrigerant heat exchanger 12, heat is exchanged between the high pressure refrigerant and the high temperature side heat medium to heat the high temperature side heat medium. In the indoor evaporator 16, heat is exchanged between the low-pressure refrigerant and the blown air to cool the blown air.

In addition, in the high temperature side heat medium circuit 20 in the dehumidifying/heating/defrosting mode, the high temperature side heat medium heated by the water-refrigerant heat exchanger 12 is heated by the high voltage heater 26 . As a result, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated.

In addition, in the low-temperature side heat medium circuit 30 in the dehumidification/heating defrost mode, the low-temperature side heat medium pressure-fed from the second low-temperature side pump 31b is sent to the low-temperature side radiator 35 via the cooling water passage of the high-voltage equipment 81. influx. In the low temperature side radiator 35, frost is melted and removed from the low temperature side radiator 35 by the heat stored in the low temperature side heat medium. That is, the low-temperature side radiator 35 is defrosted using the low-temperature side heat medium heated when passing through the cooling water passage of the high-voltage equipment 81 as a heat source.

In addition, in the indoor air conditioning unit 40 in the dehumidification/heating defrost mode, the air blown from the indoor blower 42 is cooled by the indoor evaporator 16 and dehumidified. The temperature of the air cooled and dehumidified by the indoor evaporator 16 is adjusted by adjusting the opening of the air mix door 44 so as to approach the target blowout temperature TAO. Then, the dehumidification and heating of the vehicle interior are continued by blowing out the temperature-controlled blown air into the vehicle interior.

(h-2) Heating defrost mode In the heat pump cycle 10 in the heating defrost mode, the controller 50 stops the compressor 11 . Therefore, the refrigerant does not circulate in the heat pump cycle 10 in the defrosting operation that is performed in the single heating mode.

In addition, in the high temperature side heat medium circuit 20 in the heating defrost mode, the control device 50 operates the high temperature side pump 21, the high temperature side flow control valve 22, and the high voltage heater 26 in the same manner as in the dehumidification and heating defrost mode. to control. Therefore, in the high temperature side heat medium circuit 20 in the heating defrost mode, as shown in FIG. 14, the high temperature side heat medium circulates in the same manner as in the dehumidifying heating defrosting mode.

In addition, in the low temperature side heat medium circuit 30 in the heating defrost mode, the control device 50 stops the first low temperature side pump 31a, and stops the second low temperature side pump 31b and the five-way Controls actuation of valve 32 . Therefore, the low-temperature side heat medium circulates in the same manner as in the dehumidifying/heating defrosting mode.

In addition, in the indoor air conditioning unit 40 in the heating defrost mode, the control device 50 controls the indoor fan 42, the electric actuator for the air mix door, the inside/outside air switching device 43, and the electric actuator for the blowout mode door, as in the single cooling mode. Controls the actuation of the actuator.

Therefore, in the high temperature side heat medium circuit 20 in the heating defrost mode, the high temperature side heat medium is heated by the high voltage heater 26 . As a result, the high temperature side heat medium temperature TWH approaches the reference high temperature side heat medium temperature KTWH. In the heater core 23, heat is exchanged between the high-temperature side heat medium and the blown air according to the opening degree of the air mix door 44, and the blown air is heated.

In addition, in the low-temperature side heat medium circuit 30 in the dehumidification/heating defrost mode, the low-temperature side heat medium heated when passing through the cooling water passage of the high-voltage equipment 81 is used as a heat source, as in the heating defrost mode. The low temperature side radiator 35 is defrosted.

As described above, according to the heat pump cycle device 1 of the present embodiment, even if frost forms on the low temperature side radiator 35 during execution of the single dehumidifying heating mode and the single heating mode, the frost on the low temperature side radiator 35 is removed. be able to.

Here, as in the heat pump cycle device 1 of the present embodiment, defrosting of the low-temperature side radiator 35 using the low-temperature side heat medium heated by the high-power system device 81 as a heat source causes insufficient defrosting. There is a possibility that The reason for this is that the high-voltage equipment 81 does not generate sufficient heat, and the low-temperature side heat medium may not store enough heat to melt and remove the frost on the low-temperature side radiator 35. because there is

On the other hand, in the heat pump cycle device 1 of the present embodiment, the next defrosting operation is continued until the startup elapsed time Tm1 becomes equal to or longer than the startup waiting time Tmi1 or until the defrosting elapsed time Tm2 becomes equal to or longer than the defrosting waiting time Tmi2. Execution of frost operation is prohibited. Therefore, while the execution of the defrosting operation is prohibited, the heat generated by the high-voltage equipment 81 can be stored in the low temperature side heat medium.

Furthermore, the startup standby time Tmi1 and the defrost standby time Tmi2 are set so that the low-temperature side heat medium can store an amount of heat that can melt and remove frost on the low-temperature side radiator 35 . Therefore, in the defrosting operation of the heat pump cycle device 1, the low temperature side radiator 35 can be reliably defrosted.

Therefore, it is possible to prevent a situation in which the defrosting becomes insufficient and it is determined that the low temperature side radiator 35 is frosted again immediately after the defrosting operation ends. As a result, according to the heat pump cycle device 1 of the present embodiment, frequent execution of the defrosting operation can be suppressed.

Also, in the heat pump cycle device 1 of the present embodiment, as described in step S7, the defrosting operation is terminated when the third low temperature side heat medium temperature TWL3 is equal to or higher than the reference defrosting temperature KTWL. According to this, since the temperature of the low-temperature-side heat medium immediately after flowing out from the low-temperature-side radiator 35 is used, it is possible to accurately determine that the defrosting of the low-temperature-side radiator 35 is completed, and to appropriately perform the defrosting operation. can be terminated.

Also, in the heat pump cycle device 1 of the present embodiment, as described in step S7, the defrosting operation is terminated when the defrosting time Tmd becomes equal to or longer than the reference defrosting time KTmd. According to this, even if the defrosting of the low temperature side radiator 35 is not completed, the defrosting operation can be terminated.

During the defrosting operation, the high-voltage heater 26, which consumes more energy than the heat pump cycle 10, is energized to heat the high temperature side heat medium. Therefore, by forcibly terminating the defrosting operation, it is possible to reduce the increase in energy consumption due to the execution of the defrosting operation. Furthermore, in the heat pump cycle device 1 of the present embodiment, shortening of the vehicle cruising distance can be suppressed.

Also, in the heat pump cycle device 1 of the present embodiment, the startup standby time Tmi1 is set shorter than the defrosting standby time Tmi2. Therefore, the first defrosting operation can be performed relatively quickly after starting the vehicle system. Furthermore, regarding the defrosting operation performed after the second time, it is possible not only to achieve reliable defrosting of the low-temperature side radiator 35, but also to effectively suppress the frequent execution of the defrosting operation. can. That is, shortening of the vehicle cruising distance can be effectively suppressed.

Also, the heat pump cycle device 1 of the present embodiment includes a defrosting operation permitting section, as described in step S7. According to this, the defrosting operation can be performed while the vehicle is parked without the passenger on board. Then, when the passenger gets on the vehicle again, the operation in the independent dehumidifying/heating mode and the independent heating mode can be quickly executed.

The present disclosure is not limited to the above-described embodiments, and can be variously modified as follows without departing from the scope of the present disclosure.

In the above-described embodiment, an example in which the heat pump cycle device 1 according to the present disclosure is applied to an electric vehicle has been described, but application of the heat pump cycle device 1 is not limited to this. It can be widely applied to a device that performs a defrosting operation using a heat medium heated by a heat generating part different from the heat pump cycle 10 as a heat source when defrosting the heat absorbing part. For example, it may be applied to a stationary air conditioner. Moreover, it may be applied to a water heater for heating domestic water or the like as a fluid to be heated.

The configuration of the heat pump cycle device 1 is not limited to the configuration disclosed in the above embodiments.

In the above-described embodiment, an example in which the high-voltage device 81 is used as the heat generating unit has been described, but the present invention is not limited to this. When applied to a stationary air conditioner or water heater, other stationary electric appliances may be used. Further, when applied to a vehicle, a motor generator, an inverter, a control device for ADAS, and a charging device may be adopted as the heavy-current system device 81 and used as a heat generating portion.
The motor generator functions as an electric motor that outputs driving force for running when supplied with electric power, and functions as a power generating device that generates regenerative power when the vehicle is decelerating or running downhill. The inverter is a power conversion device that converts the frequency of power supplied from the battery 80 to the motor generator, converts AC power generated by the motor generator into DC power, and outputs the DC power to the battery 80 side. A control device for ADAS is a control device for a so-called advanced driver assistance system. An advanced driving assistance system is a system that assists a driver's driving operation. The charging device is an in-vehicle charger that charges the battery 80 with regenerated power or the like.

Further, in the above-described embodiment, an example in which the heating section is formed by the water-refrigerant heat exchanger 12 of the heat pump cycle 10 and the heater core 23 of the high temperature side heat medium circuit 20 has been described, but the present invention is not limited to this. The water-refrigerant heat exchanger 12 and the high temperature side heat medium circuit 20 may be eliminated, and an indoor condenser may be employed as the heating unit.

The indoor condenser is a heat exchange section that heats the air by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and the air. The indoor condenser may be arranged in the air conditioning case 41 of the indoor air conditioning unit 40, similarly to the heater core 23. FIG.

Also, in the heat pump cycle 10 of the above-described embodiment, an example in which the water-refrigerant heat exchanger 12 and the receiver 13 are employed has been described, but the present invention is not limited to this. For example, it has a condensing part that condenses the refrigerant, a liquid receiving part that separates the refrigerant condensed in the condensing part into gas and liquid and stores the liquid phase refrigerant, and a supercooling part that supercools the liquid phase refrigerant flowing out from the liquid receiving part. , a so-called subcool type heat exchanger may be employed.

Also, in the heat pump cycle 10 of the above-described embodiment, an example in which a mechanical mechanism is employed as the evaporation pressure regulating valve 17 has been described, but the present invention is not limited to this. An electric variable throttle mechanism having the same configuration as the cooling expansion valve 15a and the like may be employed.

Also, in the above-described embodiment, an example in which R1234yf is used as the refrigerant for the heat pump cycle 10 has been described, but the refrigerant is not limited to this. For example, R134a, R600a, R410A, R404A, R32, R407C, etc. may be employed. Alternatively, a mixed refrigerant or the like in which a plurality of types of these refrigerants are mixed may be adopted. Furthermore, a supercritical refrigerating cycle may be constructed in which carbon dioxide is employed as the refrigerant and the pressure of the refrigerant on the high pressure side is equal to or higher than the critical pressure of the refrigerant.

Also, in the high temperature side heat medium circuit 20 and the low temperature side heat medium circuit 30 of the above-described embodiment, an example in which a PTC heater is employed as the high voltage heater 26 and the battery heater 36, respectively, has been described, but the present invention is not limited to this. For example, a nichrome wire, a carbon fiber heater, or the like may be employed.

Further, in the high-temperature side heat medium circuit 20 and the low-temperature side heat medium circuit 30 of the above-described embodiment, an example in which an ethylene glycol aqueous solution is employed as the high-temperature side heat medium and the low-temperature side heat medium, respectively, has been described, but the present invention is not limited to this. . As the heat medium on the high temperature side and the heat medium on the low temperature side, a solution containing dimethylpolysiloxane or a nanofluid, an antifreeze liquid, a water-based liquid refrigerant containing alcohol, or a liquid medium containing oil may be used.

Further, in the high-temperature side heat medium circuit 20 and the low-temperature side heat medium circuit 30 of the above-described embodiment, the heat exchange fins 25a are employed in order to integrate the high-temperature side radiator 25 and the low-temperature side radiator 35 so that heat can be transferred to each other. Examples have been given, but are not limited to. For example, a so-called tank-and-tube type heat exchanger may be employed as the high-temperature side radiator 25 and the low-temperature side radiator 35, and heat transfer between them may be made possible by forming the respective tank portions from a common member.

The control mode of the heat pump cycle device 1 is not limited to the modes disclosed in the above-described embodiments.

For example, in the above-described embodiment, during the defrosting operation, the high temperature side flow control valve 22 is controlled so that the entire flow rate of the high temperature side heat medium pressure-fed from the high temperature side pump 21 flows out to the heater core 23 side. Illustrated, but not limited to. For example, as shown in FIG. 16, a predetermined amount of the high temperature side heat medium pressure-fed from the high temperature side pump 21 may flow out to the high temperature side radiator 25 side.

According to this, the heat of the high-temperature side heat medium can be transferred to the low-temperature side radiator 35 via the heat exchange fins 25a, and defrosting of the low-temperature side radiator 35 can be promoted. Therefore, as shown in FIG. 16, when defrosting operation is performed by causing the high temperature side heat medium to flow out from the high temperature side flow control valve 22 to the high temperature side radiator 25 side, the reference defrosting time KTmd described in step S7 is set to It can be shortened.

Further, in step S2 of the above-described embodiment, it is determined that the permission condition is met when the defrosting permission switch 70a is turned on (ON), but the present invention is not limited to this.
For example, it may be determined that the permission condition is satisfied when it is determined that the vehicle is parked. Alternatively, it may be determined that the permission condition is met when the service tool is connected. The service tool does not have to be always installed in the vehicle, and may be prepared at a maintenance shop or the like where cooling water injection work is performed. Furthermore, it may be determined that the permission condition is met when an existing switch is pressed for a long time or when a plurality of switches are pressed simultaneously.

Further, as the operation mode of the heat pump cycle device 1, another operation mode may be provided. For example, a startup warm-up mode may be added. The startup warm-up mode is executed to warm up battery 80 when battery temperature TB is equal to or lower than a predetermined reference lower limit temperature KTBL when the vehicle system is started.

In the startup warm-up mode, the controller 50 stops the compressor 11. In addition, the control device 50 operates the first low temperature side pump 31a so as to exhibit a predetermined reference pumping capability. The controller 50 also controls the operation of the five-way valve 32 so that a battery cooling circuit is formed. Then, the controller 50 supplies electric power to the battery heater 36 so as to exhibit a predetermined heating capacity. According to this, the battery 80 can be warmed up to an appropriate temperature before the vehicle runs.

Also, in the single cooling mode of the above embodiment, the second low temperature side pump 31b may be stopped.

Although the present disclosure has been described with reference to examples, it is understood that the present disclosure is not limited to those examples or structures. The present disclosure also includes various modifications and modifications within the equivalent range. In addition, various combinations and configurations, as well as other combinations and configurations, including single elements, more, or less, are within the scope and spirit of this disclosure.

Claims (5)

1. a compressor (11) for compressing a refrigerant;
   a heating unit (12, 23) for heating a fluid to be heated by radiating heat from the refrigerant discharged from the compressor;
   a decompression unit (15b) for decompressing the refrigerant flowing out of the heating unit;
   a heat absorption part (18, 35) for absorbing heat of outside air into the refrigerant decompressed by the decompression part;
   a frost formation determination unit (S1) that determines that frost has formed on the heat absorption unit;
   a defrosting operation executing unit (S6, S7) for executing a defrosting operation for defrosting the heat absorbing unit when the frost formation determination unit determines that frost has formed on the heat absorbing unit;
   A defrosting operation prohibiting unit (S4, S5) that prohibits the defrosting operation execution unit from executing the defrosting operation,
   The heat absorption section includes a heat medium heat exchange section (18) for exchanging heat between the refrigerant decompressed by the decompression section and a heat medium, and an outside air heat exchange section (35) for exchanging heat between the heat medium and outside air. has a heat medium circuit (30) connected to
   A heat generating part (81) for heating the heat medium is arranged in the heat medium circuit,
   When the defrosting operation is executed, the defrosting operation execution unit defrosts the outside air heat exchange unit using the heat medium heated by the heat generating unit as a heat source,
   The defrosting operation prohibition unit (S5) continues until the defrosting elapsed time (Tm2), which is the elapsed time from the end of the previous defrosting operation, becomes equal to or longer than a predetermined defrosting standby time (Tmi2). A heat pump cycle device that prohibits execution of the next defrosting operation.
2. The defrosting operation execution unit terminates the defrosting operation when the temperature (TWL3) of the heat medium flowing out from the outside air heat exchange unit becomes equal to or higher than a predetermined reference defrosting temperature (KTWL). Item 1. The heat pump cycle device according to item 1.
3. The defrosting operation execution unit performs the defrosting operation when the defrosting time (Tmd), which is the elapsed time from the start of the defrosting operation, becomes equal to or longer than a predetermined reference defrosting time (KTmd). 3. The heat pump cycle device according to claim 1 or 2, wherein the heat pump cycle device is terminated.
4. A heat pump cycle device applied to a vehicle,
   The defrosting operation prohibition unit (S4) prohibits the defrosting operation until the elapsed activation time (Tm1), which is the elapsed time after the vehicle system is activated, becomes equal to or longer than a predetermined activation waiting time (Tmi1). prohibit the execution of
   The heat pump cycle device according to any one of claims 1 to 3, wherein the startup standby time is set shorter than the defrosting standby time.
5. A defrosting operation permitting unit (S2) that causes the defrosting operation execution unit to perform the defrosting operation regardless of whether or not the defrosting operation prohibiting unit prohibits execution of the defrosting operation. 5. The heat pump cycle device according to any one of 1 to 4.

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