WO2022202307A1 - Refrigeration cycle device - Google Patents

Abstract

The present invention comprises: a compressor (11) that sucks in, compresses, and discharges a refrigerant; a heat dissipation unit (12) that dissipates heat from the refrigerant discharged from the compressor; a first decompression unit (13) and a second decompression unit (16) that decompress the refrigerant from which heat has been dissipated by the heat dissipation unit; a first evaporator (14) that evaporates the refrigerant by causing the refrigerant decompressed by the first decompression unit to absorb heat from the air blown into a space to be air-conditioned; a second evaporator (17) that evaporates the refrigerant by causing the refrigerant decompressed by the second decompression unit to absorb heat from an object to be cooled (33); and a control unit (60) that switches between an energy-saving mode in which the compressor is controlled so that the temperature (TE1) of the first evaporator approaches an energy-saving target temperature (TEOe), and a standard mode that is executed when the target temperature (TBO) of the object to be cooled falls below an energy-saving reference temperature (αe) in the energy-saving mode and in which the compressor is controlled so that the temperature of the first evaporator approaches a standard target temperature (TEOs) that is lower than the energy-saving target temperature.

Description

refrigeration cycle equipment Cross-reference to related applications

This application is based on Japanese Patent Application No. 2021-46982 filed on March 22, 2021, and the content thereof is incorporated herein.

The present disclosure relates to a refrigeration cycle device that cools air and objects to be cooled.

Conventionally, Patent Document 1 describes a refrigeration cycle device having an indoor evaporator and a chiller. The indoor evaporator is a heat exchanger that uses a low-pressure refrigerant to absorb heat from the air blown into the passenger compartment to cool the air. A chiller is a heat exchanger that cools a battery cooling heat medium by absorbing heat with a low-pressure refrigerant.

JP 2020-104604 A

As the cruising range of electric vehicles increases, the number of batteries installed in electric vehicles tends to increase. However, since the temperature of the battery may rise due to high-load driving, rapid charging, etc., improvement of the battery cooling capacity is required.

In view of the above points, an object of the present disclosure is to provide a refrigeration cycle apparatus capable of achieving both energy saving and securing of cooling capacity.

A refrigeration cycle apparatus according to a first aspect of the present disclosure includes a compressor, a heat radiating section, first and second pressure reducing sections, a first evaporating section, a second evaporating section, and a control section.

The compressor sucks in the refrigerant, compresses it, and discharges it. The heat radiating section radiates heat from the refrigerant discharged from the compressor. The first pressure reducing section and the second pressure reducing section reduce the pressure of the refrigerant radiated by the heat radiating section. The first evaporator causes the refrigerant decompressed by the first decompressor to absorb heat from the air blown into the air-conditioned space, thereby evaporating the refrigerant. The second evaporator evaporates the refrigerant by allowing the refrigerant decompressed by the second decompressor to absorb heat from the object to be cooled.

The control unit is executed in an energy-saving mode for controlling the compressor so that the temperature of the first evaporator approaches the energy-saving target temperature, and when the target temperature of the object to be cooled in the energy-saving mode is below the energy-saving reference temperature. Switches to the standard mode in which the compressor is controlled so that the temperature of the evaporator approaches the standard target temperature, which is lower than the energy-saving target temperature.

According to this, the energy saving mode can save energy, and the standard mode can secure the cooling capacity.

A refrigeration cycle device according to a second aspect of the present disclosure includes a compressor, a heat radiating section, a first pressure reducing section and a second pressure reducing section, a first evaporating section, a pressure adjusting section, a second evaporating section, a control and a part.

The compressor sucks in the refrigerant, compresses it, and discharges it. The heat radiating section radiates heat from the refrigerant discharged from the compressor. The first pressure reducing section and the second pressure reducing section reduce the pressure of the refrigerant radiated by the heat radiating section. The first evaporator causes the refrigerant decompressed by the first decompressor to absorb heat from the air blown into the air-conditioned space, thereby evaporating the refrigerant. The pressure adjusting section maintains the pressure of the refrigerant flowing out of the first evaporating section at or above a predetermined pressure. The second evaporator evaporates the refrigerant by allowing the refrigerant decompressed by the second decompressor to absorb heat from the object to be cooled.

The control unit is executed in a standard mode for controlling the compressor so that the temperature of the first evaporator approaches the standard target temperature, and when the target temperature of the object to be cooled is lower than the high cooling reference temperature in the standard mode. 2 Switches to a high cooling mode in which the compressor is controlled so that the temperature of the evaporator approaches a high cooling target temperature that is lower than the standard target temperature.

According to this, the standard mode saves energy, and the high cooling mode ensures cooling capacity.

A refrigeration cycle device according to a third aspect of the present disclosure includes a compressor, a heat radiating section, a first pressure reducing section and a second pressure reducing section, a first evaporating section, a second evaporating section, a cutoff section, and a control section. and

The compressor sucks in the refrigerant, compresses it, and discharges it. The heat radiating section radiates heat from the refrigerant discharged from the compressor. The first pressure reducing section and the second pressure reducing section reduce the pressure of the refrigerant radiated by the heat radiating section. The first evaporator causes the refrigerant decompressed by the first decompressor to absorb heat from the air blown into the air-conditioned space, thereby evaporating the refrigerant. The second evaporator evaporates the refrigerant by allowing the refrigerant decompressed by the second decompressor to absorb heat from the object to be cooled. The blocking section blocks the flow of the refrigerant to the first evaporating section.

The control unit is executed in a standard mode for controlling the compressor so that the temperature of the first evaporator approaches the standard target temperature, and when the cutoff unit cuts off the flow of refrigerant to the first evaporator in the standard mode. , and a single mode in which the compressor is controlled so that the temperature of the second evaporator approaches a single target temperature lower than the temperature of the first evaporator.

According to this, it is possible to save energy in the standard mode and secure cooling capacity in the independent mode.

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.
BRIEF DESCRIPTION OF THE DRAWINGS It is a whole block diagram which shows the refrigerating-cycle apparatus of 1st Embodiment. It is a block diagram which shows the electric-control part of the refrigerating-cycle apparatus of 1st Embodiment. It is an explanatory view explaining operation of an energy-saving mode, a standard mode, and a high cooling mode of a refrigerating cycle device of a 1st embodiment. It is explanatory drawing explaining the operation|movement of the standard mode of the refrigerating-cycle apparatus of 1st Embodiment, and independent mode. 4 is a flowchart showing control processing executed by the control device of the refrigeration cycle apparatus of the first embodiment; It is a whole block diagram which shows the refrigerating-cycle apparatus of 2nd Embodiment.

A plurality of modes for carrying out the present disclosure will be described below with reference to the drawings. In each embodiment, portions corresponding to items described in the preceding embodiment may be denoted by the same reference numerals, and redundant description may be omitted. When only part of the configuration is described in each embodiment, the other embodiments previously described can be applied to other portions of the configuration. Not only the combination of the parts that are specifically stated that the combination is possible in each embodiment, but also the embodiments can be partially combined even if it is not specified unless there is a particular problem with the combination. It is possible.

(First embodiment)
Embodiments will be described below with reference to the drawings. A refrigeration cycle device 10 shown in FIG. 1 is applied to a vehicle air conditioner 1 mounted on an electric vehicle or a hybrid vehicle. An electric vehicle is a vehicle that obtains driving force for running from an electric motor. A hybrid vehicle is a vehicle that obtains driving force for driving the vehicle from an engine (in other words, an internal combustion engine) and an electric motor for driving.

The vehicle air conditioner 1 is an air conditioner with a battery temperature adjustment function. The vehicle air conditioner 1 air-conditions the interior of the vehicle, which is a space to be air-conditioned, and adjusts the temperature of the battery 33 .

The battery 33 is a secondary battery that stores power to be supplied to in-vehicle equipment such as an electric motor. The battery 33 of this embodiment is a lithium ion battery. The battery 33 is a so-called assembled battery formed by stacking a plurality of battery cells (not shown) and electrically connecting the battery cells in series or in parallel.

The output of this type of battery tends to decrease at low temperatures, and deterioration tends to progress at high temperatures. Therefore, the temperature of the battery must be maintained within an appropriate temperature range (15° C. or higher and 55° C. or lower in this embodiment) that allows the battery to fully utilize its charge/discharge capacity. .

Therefore, in the vehicle air conditioner 1 , the cold heat generated by the refrigeration cycle device 10 can cool the battery 33 . Objects to be cooled in the refrigeration cycle apparatus 10 of this embodiment are the air and the battery 33 .

The refrigeration cycle device 10 is a vapor compression refrigeration system comprising a compressor 11, a condenser 12, a first expansion valve 13, a first evaporator 14, a constant pressure valve 15, a second expansion valve 16, a second evaporator 17 and a receiver 18. machine. In the refrigerating cycle device 10 of the present embodiment, a freon-based refrigerant is used as a refrigerant, and a subcritical refrigerating cycle is constructed in which the pressure of the refrigerant on the high-pressure side does not exceed the critical pressure of the refrigerant. Refrigerant oil (specifically, PAG oil) for lubricating the compressor 11 is mixed in the refrigerant. Some of the refrigerating machine oil circulates through the cycle together with the refrigerant.

The compressor 11 is an electric compressor driven by electric power supplied from the battery 33, and sucks, compresses, and discharges the refrigerant of the refrigeration cycle device 10. Compressor 11 may be a variable displacement compressor driven by a belt.

The condenser 12 is a high pressure side refrigerant heat medium heat exchanger that condenses the high pressure side refrigerant by exchanging heat between the high pressure side refrigerant discharged from the compressor 11 and the cooling water of the high temperature cooling water circuit 20 .

The cooling water of the high temperature cooling water circuit 20 is a fluid as a heat medium. The cooling water in the high temperature cooling water circuit 20 is a high temperature heat medium. In this embodiment, as the cooling water for the high-temperature cooling water circuit 20, a liquid containing at least ethylene glycol, dimethylpolysiloxane, or a nanofluid, or an antifreeze liquid is used. The high-temperature cooling water circuit 20 is a high-temperature heat medium circuit in which a high-temperature heat medium circulates.

The receiver 18 is a gas-liquid separation unit that separates the gas-liquid of the refrigerant that has flowed out of the condenser 12 and causes the liquid-phase refrigerant to flow out downstream, and stores surplus refrigerant in the cycle. The flow of the liquid-phase refrigerant that has flowed out of the receiver 18 is branched at the branching portion 10a.

The first expansion valve 13 is a first decompression unit that decompresses and expands the liquid-phase refrigerant that has flowed out of the receiver 18 . The first expansion valve 13 is an electric variable throttle mechanism, and has a valve body and an electric actuator. The valve body is configured to be able to change the degree of opening of the flow path of the refrigerant (in other words, the degree of throttle opening). The electric actuator has a stepping motor that changes the throttle opening of the valve body.

The first expansion valve 13 is composed of a variable throttle mechanism with a fully closing function that fully closes the flow path of the refrigerant. In other words, the first expansion valve 13 has a blocking portion 13a that blocks the flow of the refrigerant by fully closing the flow path of the refrigerant. The operation of the first expansion valve 13 is controlled by control signals output from the control device 60 shown in FIG.

The first evaporator 14 exchanges heat between the refrigerant flowing out of the first expansion valve 13 and the air blown into the vehicle interior, thereby evaporating the refrigerant and cooling the air blown into the vehicle interior. It is a vessel. The first evaporator 14 is an air evaporator that cools air by evaporating a refrigerant. The first evaporator 14 is the first evaporator.

The constant pressure valve 15 is a pressure regulating section (in other words, pressure regulating decompression section) that maintains the pressure of the refrigerant on the outlet side of the first evaporator 14 within a predetermined range. The constant pressure valve 15 suppresses frost formation on the first evaporator 14 by maintaining the pressure of the refrigerant (in other words, the temperature of the refrigerant) in the first evaporator 14 at a predetermined value or higher.

The constant pressure valve 15 is composed of a mechanical variable throttle mechanism. Specifically, when the pressure of the refrigerant on the outlet side of the first evaporator 14 falls below a predetermined value, the constant pressure valve 15 reduces the flow path area of the refrigerant (that is, the opening degree of the throttle). When the pressure of the refrigerant on the outlet side exceeds a predetermined value, the area of the refrigerant flow path (that is, the throttle opening) is increased.

In cases such as when there is little variation in the flow rate of the circulating refrigerant that circulates through the cycle, instead of the constant pressure valve 15, a fixed throttle made up of an orifice, capillary tube, or the like may be employed.

The second expansion valve 16 and the second evaporator 17 are arranged in parallel with the first expansion valve 13, the first evaporator 14 and the constant pressure valve 15 in the refrigerant flow.

The second expansion valve 16 is a second decompression section that decompresses and expands the liquid-phase refrigerant that has flowed out of the condenser 12 . The second expansion valve 16 is an electric variable throttle mechanism, and has a valve body and an electric actuator. The valve body is configured to be able to change the degree of opening of the flow path of the refrigerant (in other words, the degree of throttle opening). The electric actuator has a stepping motor that changes the throttle opening of the valve body.

The second expansion valve 16 is composed of a variable throttle mechanism with a fully closing function that fully closes the refrigerant passage. That is, the second expansion valve 16 can block the flow of the refrigerant by fully closing the flow path of the refrigerant. The operation of the second expansion valve 16 is controlled by control signals output from the controller 60 .

The second evaporator 17 performs heat exchange between the low-pressure refrigerant flowing out of the second expansion valve 16 and the cooling water in the low-temperature cooling water circuit 30 to evaporate the refrigerant and cool the cooling water. It is a vessel. The second evaporator 17 is a cooling evaporator that evaporates refrigerant to cool cooling water. The second evaporator 17 is a second evaporator.

The vapor-phase refrigerant evaporated in the second evaporator 17 joins the refrigerant flowing out of the constant pressure valve 15 at the confluence portion 10b, and then is sucked into the compressor 11 and compressed.

The cooling water of the low-temperature cooling water circuit 30 is a fluid as a heat medium. The cooling water in the low-temperature cooling water circuit 30 is a low-temperature heat medium. In this embodiment, as the cooling water for the low-temperature cooling water circuit 30, a liquid containing at least ethylene glycol, dimethylpolysiloxane, or a nanofluid, or an antifreeze liquid is used. The low-temperature cooling water circuit 30 is a low-temperature heat medium circuit in which a low-temperature heat medium circulates.

A condenser 12, a high temperature side pump 21, a heater core 22, a high temperature side radiator 23, an on-off valve 24 and an electric heater 25 are arranged in the high temperature cooling water circuit 20.

The high temperature side pump 21 is a heat medium pump that sucks and discharges cooling water. The high temperature side pump 21 is an electric pump. The high-temperature side pump 21 is a high-temperature side flow rate adjusting section that adjusts the flow rate of cooling water circulating in the high-temperature cooling water circuit 20 .

The heater core 22 is an air heating heat exchanger that heats the air blown into the vehicle interior by exchanging heat between the cooling water of the high-temperature cooling water circuit 20 and the air blown into the vehicle interior. In the heater core 22, the cooling water radiates heat to the air blown into the vehicle interior. The condenser 12, the high-temperature cooling water circuit 20, and the heater core 22 are heat radiating units that exchange heat between the refrigerant discharged from the compressor 11 and the air blown into the vehicle interior, and radiate heat to the air.

The high-temperature side radiator 23 is a high-temperature heat medium outside air heat exchanger that exchanges heat between the cooling water of the high-temperature cooling water circuit 20 and outside air. The high temperature side radiator 23 and the on-off valve 24 are arranged in parallel with the heater core 22 in the flow of the high temperature side cooling water.

The on-off valve 24 is an electromagnetic valve that opens and closes the coolant flow path on the high temperature side radiator 23 side. The operation of the on-off valve 24 is controlled by the controller 60 . The on-off valve 24 is a high-temperature switching unit that switches the flow of cooling water in the high-temperature cooling water circuit 20 .

The on-off valve 24 may be a thermostat. A thermostat is a cooling water temperature responsive valve having a mechanical mechanism that opens and closes a cooling water flow path by displacing a valve body with thermowax whose volume changes with temperature.

The electric heater 25 is an auxiliary heating unit that auxiliary heats the cooling water of the high-temperature cooling water circuit 20 . The electric heater 25 is an auxiliary heat source for heating the air with the heater core 22 . As the electric heater 25, a PTC heater or the like that generates heat when supplied with electric power can be used. The electric heater 25 is a Joule heat generator that generates Joule heat. The amount of heat generated by the electric heater 25 is controlled by a control voltage output from the controller 60 .

A second evaporator 17, a low temperature side pump 31, a low temperature side radiator 32, a battery 33 and a three-way valve 38 are arranged in the low temperature cooling water circuit 30.

The low temperature side pump 31 is a heat medium pump that sucks and discharges cooling water. The low temperature side pump 31 is an electric pump. The low-temperature side pump 31 is a low-temperature side flow rate adjusting section that adjusts the flow rate of cooling water circulating in the low-temperature cooling water circuit 30 . The low-temperature side radiator 32 is a low-temperature heat medium outside air heat exchanger that exchanges heat between the cooling water of the low-temperature cooling water circuit 30 and the outside air.

The battery 33 is an in-vehicle device mounted in a vehicle, and is a heat-generating device that generates heat as it operates. The battery 33 radiates waste heat generated during operation to the cooling water of the low-temperature cooling water circuit 30 . In other words, the battery 33 supplies heat to the cooling water of the low temperature cooling water circuit 30 .

The low temperature side radiator 32 and the battery 33 are arranged in parallel with each other in the flow of the low temperature side cooling water. The three-way valve 38 switches the flow of the low temperature side cooling water to the low temperature side radiator 32 and the battery 33 . Actuation of the three-way valve 38 is controlled by a controller 60 .

The first evaporator 14 and the heater core 22 are housed in a casing 51 (hereinafter referred to as an air conditioning casing) of the indoor air conditioning unit 50. The indoor air conditioning unit 50 is arranged inside a not-shown instrument panel in the front part of the passenger compartment. The air conditioning casing 51 is an air passage forming member that forms an air passage.

The heater core 22 is arranged downstream of the first evaporator 14 in the air passage in the air conditioning casing 51 . An inside/outside air switching box 52 and an indoor fan 53 are arranged in the air conditioning casing 51 . The inside/outside air switching box 52 has an inside/outside air switching door 52a. The inside/outside air switching door 52 a is an inside/outside air switching portion that switches between introducing inside air and outside air into the air passage in the air conditioning casing 51 . The inside/outside air switching door 52 a is an inside/outside air adjustment unit that adjusts the ratio between the inside air and the outside air introduced into the air passage in the air conditioning casing 51 .

The indoor air blower 53 draws in the inside air and the outside air introduced into the air passage in the air conditioning casing 51 through the inside/outside air switching box 52 and blows the air. The inside/outside air switching door 52 a and the indoor blower 53 are controlled by the control device 60 .

An air mix door 54 is arranged between the first evaporator 14 and the heater core 22 in the air passage in the air conditioning casing 51 . The air mix door 54 adjusts the air volume ratio between the cold air flowing into the heater core 22 and the cold air flowing through the cold air bypass passage 55 among the cold air that has passed through the first evaporator 14 .

The cold air bypass passage 55 is an air passage through which the cold air that has passed through the first evaporator 14 bypasses the heater core 22 .

The air mix door 54 is a rotary door having a rotating shaft rotatably supported with respect to the air conditioning casing 51 and a door base plate portion coupled to the rotating shaft. By adjusting the opening position of the air mix door 54, the temperature of the air-conditioned air blown out from the air-conditioning casing 51 into the passenger compartment can be adjusted to a desired temperature.

The rotating shaft of the air mix door 54 is driven by a servomotor. The operation of the servo motors is controlled by controller 60 .

The air mix door 54 may be a sliding door that slides in a direction substantially perpendicular to the air flow. The sliding door may be a plate-shaped door made of a rigid body. A film door formed of a flexible film material may be used.

The air-conditioned air whose temperature has been adjusted by the air mix door 54 is blown into the vehicle interior through the outlet 56 formed in the air-conditioning casing 51 .

The control device 60 shown in FIG. 2 is composed of a well-known microcomputer including CPU, ROM, RAM, etc. and its peripheral circuits. The control device 60 performs various calculations and processes based on control programs stored in the ROM. Various devices to be controlled are connected to the output side of the control device 60 . The control device 60 is a control unit that controls the operation of various controlled devices.

Equipment to be controlled by the control device 60 includes the compressor 11, the first expansion valve 13, the second expansion valve 16, the high temperature side pump 21, the on-off valve 24, the electric heater 25, the low temperature side pump 31, the three-way valve 38, They are the inside/outside air switching door 52a, the indoor blower 53, and the like.

The software and hardware for controlling the electric motor of the compressor 11 in the control device 60 is a refrigerant discharge capacity control section. Software and hardware for controlling the first expansion valve 13 in the control device 60 are a first throttle control section. The software and hardware for controlling the second expansion valve 16 in the control device 60 is a second throttle control section.

The software and hardware for controlling the high temperature side pump 21 in the control device 60 is a high temperature heat medium flow control unit. Software and hardware for controlling the on-off valve 24 in the control device 60 is an on-off valve control unit.

The software and hardware for controlling the electric heater 25 in the control device 60 is an auxiliary heating control section. The software and hardware for controlling the low-temperature side pump 31 in the control device 60 is a low-temperature heat medium flow rate controller. Software and hardware for controlling the three-way valve 38 in the control device 60 is a three-way valve control section.

The input side of the control device 60 includes an inside air temperature sensor 61, an outside air temperature sensor 62, a solar radiation sensor 63, a first evaporator temperature sensor 64, a second evaporator temperature sensor 65, a heater core temperature sensor 66, and a high pressure refrigerant pressure sensor 67. , high-temperature cooling water temperature sensor 68, first low-pressure refrigerant pressure sensor 69, first low-pressure refrigerant temperature sensor 70, second low-pressure refrigerant pressure sensor 71, second low-pressure refrigerant temperature sensor 72, battery temperature sensor 73, etc. A group of sensors is connected.

The inside air temperature sensor 61 detects the vehicle interior temperature Tr. An outside air temperature sensor 62 detects outside air temperature Tam. The solar radiation sensor 63 detects the solar radiation As in the passenger compartment.

The first evaporator temperature sensor 64 is a temperature detection unit that detects the temperature TE1 of the first evaporator 14 (hereinafter referred to as the first evaporator temperature). The first evaporator temperature sensor 64 is, for example, a fin thermistor that detects the temperature of the heat exchange fins of the first evaporator 14, a refrigerant temperature sensor that detects the temperature of refrigerant flowing through the first evaporator 14, or the like.

The second evaporator temperature sensor 65 is a temperature detection unit that detects the temperature TE2 of the second evaporator 17 (hereinafter referred to as the second evaporator temperature). The second evaporator temperature sensor 65 is, for example, a refrigerant temperature sensor or the like that detects the temperature of refrigerant flowing through the second evaporator 17 .

The heater core temperature sensor 66 is a temperature detection unit that detects the temperature TH of the heater core 22 (hereinafter referred to as heater core temperature). The heater core temperature sensor 66 includes, for example, a fin thermistor that detects the temperature of the heat exchange fins of the heater core 22, a coolant temperature sensor that detects the temperature of cooling water flowing through the heater core 22, and an air temperature sensor that detects the temperature of air flowing out of the heater core 22. A temperature sensor or the like.

The high-pressure refrigerant pressure sensor 67 is a high-pressure refrigerant pressure detection section that detects the pressure of the high-pressure refrigerant on the outlet side of the receiver 18 .

The high-temperature cooling water temperature sensor 68 is a temperature detection unit that detects the temperature TW of the cooling water in the high-temperature cooling water circuit 20 . For example, hot coolant temperature sensor 68 detects the temperature of the coolant in condenser 12 .

The first low-pressure refrigerant pressure sensor 69 is a first low-pressure refrigerant pressure detection section that detects the pressure of the low-pressure refrigerant on the outlet side of the first evaporator 14 . The first low-pressure refrigerant temperature sensor 70 is a first low-pressure refrigerant pressure detection section that detects the temperature of the low-pressure refrigerant on the outlet side of the first evaporator 14 .

The second low-pressure refrigerant pressure sensor 71 is a second low-pressure refrigerant pressure detection section that detects the pressure of the low-pressure refrigerant on the outlet side of the second evaporator 17 . The second low-pressure refrigerant temperature sensor 72 is a second low-pressure refrigerant pressure detection section that detects the temperature of the low-pressure refrigerant on the outlet side of the second evaporator 17 .

The battery temperature sensor 73 is a battery temperature detection unit that detects the temperature TB of the battery 33. The battery temperature sensor 73 is desirably composed of a plurality of temperature sensors that detect temperatures at a plurality of locations on the battery 33 .

Various operation switches provided on the operation panel 75 are connected to the input side of the control device 60 . Various operation switches are operated by the passenger. The operation panel 75 is arranged near the instrument panel in the front part of the passenger compartment. Operation signals from various operation switches are input to the control device 60 .

Various operation switches are air conditioner switches, temperature setting switches, etc. The air conditioner switch is a switch for setting whether or not the indoor air conditioning unit 50 cools the air. The temperature setting switch is a switch for setting the preset temperature in the vehicle compartment.

Next, the operation of the above configuration will be explained. The control device 60 switches the operation mode of the air conditioning between the air conditioning mode, the standard mode, the high cooling mode, the energy saving mode, and the independent mode based on the target outlet temperature TAO and the like.

The air-conditioning mode is an operation mode (in other words, air-conditioning only mode) that is switched when air-conditioning the vehicle interior without cooling the battery 33 .

The standard mode is an operation mode (in other words, standard air conditioning battery mode) that is switched when air-conditioning the vehicle interior and cooling the battery.

The high cooling mode is an operation mode (in other words, high cooling air conditioning battery mode) that can be switched when air-conditioning the vehicle interior and cooling the battery with a higher capacity than in the standard mode.

The energy-saving mode is an operation mode (in other words, an energy-saving air-conditioning battery mode) that can be switched when air-conditioning the vehicle interior and cooling the battery with lower capacity than the standard mode.

The stand-alone mode is an operation mode (in other words, stand-alone battery mode) that is switched when cooling the battery 33 without air-conditioning the interior of the vehicle.

In the air conditioning mode, the control device 60 operates the compressor 11, the high temperature side pump 21, and the indoor fan 53 to throttle the first expansion valve 13 and fully close the second expansion valve 16.

The control device 60 determines the operating states of various control devices connected to the control device 60 (control signals to be output to various control devices) based on the target blowout temperature TAO, detection signals from the sensor group, and the like.

The target blowout temperature TAO is the target temperature of the blown air blown into the vehicle compartment. The target blowout temperature TAO is an index indicating the air conditioning load (in other words, air conditioning heat load) required of the vehicle air conditioner 1 . The control device 60 calculates the target outlet temperature TAO based on the following formula F1.
TAO=Kset×Tset−Kr×Tr−Kam×Tam−Ks×As+C (F1)
In this formula, Tset is the vehicle interior set temperature set by the temperature setting switch on the operation panel 75, Tr is the inside temperature detected by the inside temperature sensor 61, Tam is the outside temperature detected by the outside temperature sensor 62, and As is It 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.

Regarding the control signal output to the compressor 11 (in other words, the rotation speed of the compressor 11), the second 1 The temperature TE1 of the evaporator 14 is determined so as to approach the standard target temperature TEOs.

The standard target temperature TEOs is determined by referring to the control map stored in the control device 60 based on the target outlet temperature TAO. In the control map of this embodiment, the standard target temperature TEOs is determined to rise as the target outlet temperature TAO rises.

Regarding the control signal output to the first expansion valve 13 (in other words, the throttle opening of the first expansion valve 13), the degree of superheat of the refrigerant at the outlet of the first evaporator 14 is the coefficient of performance (so-called COP) of the cycle. is determined to approach a first target degree of superheat that is predetermined to approach a maximum value.

The degree of superheat of the outlet refrigerant of the first evaporator 14 is the pressure of the low-pressure refrigerant on the outlet side of the first evaporator 14 detected by the first low-pressure refrigerant pressure sensor 69 and the first low-pressure refrigerant temperature sensor 70. and the temperature of the low-pressure refrigerant on the outlet side of the first evaporator 14 .

The control signal output to the indoor fan 53 (in other words, the air volume of the indoor fan 53) is determined based on the target outlet temperature TAO. For example, the control signal output to the indoor fan 53 is determined so that the air volume of the indoor fan 53 increases in the high temperature range and low temperature range of the target air temperature TAO.

Control signals output to the servomotor of the air mix door 54 include the target outlet temperature TAO, the first evaporator temperature TE1 detected by the first evaporator temperature sensor 64, the heater core temperature TH detected by the heater core temperature sensor 66, and the , the air mix opening degree SW is determined. Then, the control signal to be output to the electric actuator 44a for the air mix door is determined so that the determined air mix opening degree SW is obtained. The air mix opening degree SW is determined so that the temperature of the air blown into the vehicle interior approaches the target air temperature TAO.

The control signal output to the on-off valve 24 is determined so that the temperature TW of the coolant in the high-temperature coolant circuit 20 detected by the high-temperature coolant temperature sensor 68 approaches the target outlet temperature TAO. That is, when the temperature TW of the coolant in the high-temperature coolant circuit 20 is higher than the target blowout temperature TAO, the on-off valve 24 is opened. As a result, in the high temperature cooling water circuit 20, the cooling water circulates through the high temperature side radiator 23, and the radiator 23 radiates heat from the cooling water to the outside air. When the temperature TW of the coolant in the high-temperature coolant circuit 20 is lower than the target blowout temperature TAO, the on-off valve 24 is closed. As a result, in the high temperature cooling water circuit 20 , the cooling water does not circulate through the high temperature side radiator 23 and the radiator 23 does not radiate heat from the cooling water to the outside air.

　In the refrigeration cycle device 10 in the air conditioning mode, the state of the refrigerant circulating in the cycle changes as follows.

That is, the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12 . The refrigerant that has flowed into the condenser 12 releases heat to the cooling water in the high-temperature cooling water circuit 20 . As a result, the refrigerant is cooled and condensed in the condenser 12 .

The refrigerant that has flowed out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the first evaporator 14, absorbs heat from the air blown into the vehicle interior, and evaporates. This cools the air blown into the vehicle interior.

Then, the refrigerant that has flowed out of the first evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11 .

The cooling water in the high-temperature cooling water circuit 20 radiated from the refrigerant in the condenser 12 is circulated to the heater core 22 . In the heater core 22 , the air cooled by the first evaporator 14 is heated by the cooling water of the high temperature cooling water circuit 20 .

As described above, in the air conditioning mode, the first evaporator 14 allows the low-pressure refrigerant to absorb heat from the air, cools the air, heats the cooled air with the heater core 22, and blows it into the vehicle interior. This makes it possible to air-condition the passenger compartment.

In the standard mode, the control device 60 operates the compressor 11, the high-temperature side pump 21, the low-temperature side pump 31, and the indoor fan 53 to throttle the first expansion valve 13 and throttle the second expansion valve 16. .

The control device 60 determines the operating states of various control devices connected to the control device 60 (control signals to be output to various control devices) based on the target blowout temperature TAO, detection signals from the sensor group, and the like.

Regarding the control signal output to the compressor 11 (in other words, the rotation speed of the compressor 11), the second 1 The temperature TE1 of the evaporator 14 is determined so as to approach the standard target temperature TEOs.

Regarding the control signal output to the first expansion valve 13 (in other words, throttle opening degree of the first expansion valve 13), as in the air conditioning mode, the degree of superheat of the refrigerant at the outlet of the first evaporator 14 is determined by the cycle. The coefficient of performance (so-called COP) is determined so as to approach the first target degree of superheat, which is predetermined so as to approach the maximum value.

Regarding the control signal output to the second expansion valve 16 (in other words, the throttle opening degree of the second expansion valve 16), the degree of superheat of the refrigerant at the outlet of the second evaporator 17 is the coefficient of performance (so-called COP) of the cycle. is determined to approach a second target degree of superheat which is predetermined to approach a maximum value.

The degree of superheat of the outlet refrigerant of the second evaporator 17 is the pressure of the low-pressure refrigerant on the outlet side of the second evaporator 17 detected by the second low-pressure refrigerant pressure sensor 71 and the second low-pressure refrigerant temperature sensor 72. and the temperature of the low-pressure refrigerant on the outlet side of the second evaporator 17 .

The control signal output to the indoor fan 53 (in other words, the air volume of the indoor fan 53) is determined based on the target outlet temperature TAO, as in the air conditioning mode.

Regarding the control signal (in other words, the air mix opening degree SW) output to the servo motor of the air mix door 54, the target outlet temperature TAO and the first evaporator temperature sensor 64 detected by the first evaporator temperature sensor 64 1 Based on the evaporator temperature TE1 and the heater core temperature TH detected by the heater core temperature sensor 66, the temperature of the air blown into the passenger compartment is determined so as to approach the target air temperature TAO.

As in the air conditioning mode, the control signal output to the on-off valve 24 is determined so that the temperature TW of the coolant in the high-temperature coolant circuit 20 detected by the high-temperature coolant temperature sensor 68 approaches the target outlet temperature TAO. .

　In the refrigeration cycle device 10 in the standard mode, the state of the refrigerant circulating in the cycle changes in the same way as in the air conditioning mode.

That is, the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12 . The refrigerant that has flowed into the condenser 12 releases heat to the cooling water in the high-temperature cooling water circuit 20 . As a result, the refrigerant is cooled and condensed in the condenser 12 .

The refrigerant that has flowed out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the first evaporator 14, absorbs heat from the air blown into the vehicle interior, and evaporates. This cools the air blown into the vehicle interior.

Then, the refrigerant that has flowed out of the first evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11 .

The cooling water in the high-temperature cooling water circuit 20 radiated from the refrigerant in the condenser 12 is circulated to the heater core 22 . In the heater core 22 , the air cooled by the first evaporator 14 is heated by the cooling water of the high temperature cooling water circuit 20 .

As described above, in the standard mode, the first evaporator 14 allows the low-pressure refrigerant to absorb heat from the air, cools the air, heats the cooled air with the heater core 22, and blows it into the passenger compartment. This makes it possible to air-condition the passenger compartment.

Furthermore, in the standard mode, the refrigerant that has flowed out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the second evaporator 17, absorbs heat from the cooling water in the low-temperature cooling water circuit 30, and evaporates. Thereby, the cooling water in the low-temperature cooling water circuit 30 is cooled. The cooling water of the low-temperature cooling water circuit 30 cooled by the second evaporator 17 flows into the battery 33 and absorbs heat from the battery 33 . Thereby, the battery 33 is cooled.

In the high cooling mode, as in the standard mode, the control device 60 operates the compressor 11, the high temperature side pump 21, the low temperature side pump 31, and the indoor fan 53, throttles the first expansion valve 13, and sets the second expansion The valve 16 is put in the throttling state.

The control device 60 determines the operating states of various control devices connected to the control device 60 (control signals to be output to various control devices) based on the target blowout temperature TAO, detection signals from the sensor group, and the like.

Regarding the control signal output to the compressor 11 (in other words, the rotation speed of the compressor 11), based on the deviation between the high cooling target temperature TEOc and the temperature TE2 of the second evaporator 17, by a feedback control method, The temperature TE2 of the second evaporator 17 is determined so as to approach the high cooling target temperature TEOc. As shown in FIG. 3, the high cooling target temperature TEOc is determined to be lower than the standard target temperature TEOs. As a result, the rotation speed of the compressor 11 is higher in the high cooling mode than in the standard mode.

Regarding the control signal output to the second expansion valve 16 (in other words, the throttle opening degree of the second expansion valve 16), as in the standard mode, the degree of superheat of the refrigerant at the outlet of the second evaporator 17 is determined by the cycle. The coefficient of performance (so-called COP) is determined so as to approach a predetermined second target degree of superheat so as to approach the maximum value.

The control signal output to the indoor fan 53 (in other words, the air volume of the indoor fan 53) is determined based on the target outlet temperature TAO, as in the air conditioning mode.

Regarding the control signal (in other words, the air mix opening degree SW) output to the servo motor of the air mix door 54, the target outlet temperature TAO and the first evaporator temperature sensor 64 detected by the first evaporator temperature sensor 64 1 Based on the evaporator temperature TE1 and the heater core temperature TH detected by the heater core temperature sensor 66, the temperature of the air blown into the passenger compartment is determined so as to approach the target air temperature TAO.

As in the standard mode, the control signal output to the on-off valve 24 is determined so that the temperature TW of the coolant in the high-temperature coolant circuit 20 detected by the high-temperature coolant temperature sensor 68 approaches the target outlet temperature TAO. .

　In the refrigeration cycle device 10 in the high cooling mode, the state of the refrigerant circulating in the cycle changes in the same way as in the standard mode.

That is, the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12 . The refrigerant that has flowed into the condenser 12 releases heat to the cooling water in the high-temperature cooling water circuit 20 . As a result, the refrigerant is cooled and condensed in the condenser 12 .

The refrigerant that has flowed out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the first evaporator 14, absorbs heat from the air blown into the vehicle interior, and evaporates. This cools the air blown into the vehicle interior. At this time, since the pressure of the first evaporator 14 is maintained within a predetermined range by the constant pressure valve 15, the temperature of the first evaporator 14 is maintained at the standard target temperature TEOs as in the standard mode. Thereby, frost formation on the first evaporator 14 is suppressed.

Then, the refrigerant that has flowed out of the first evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11 .

The cooling water in the high-temperature cooling water circuit 20 radiated from the refrigerant in the condenser 12 is circulated to the heater core 22 . In the heater core 22 , the air cooled by the first evaporator 14 is heated by the cooling water of the high temperature cooling water circuit 20 .

As described above, in the high cooling mode, the first evaporator 14 allows the low-pressure refrigerant to absorb heat from the air, cools the air, heats the cooled air with the heater core 22, and blows it into the passenger compartment. This makes it possible to air-condition the passenger compartment.

Furthermore, in the high cooling mode, the refrigerant that has flowed out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the second evaporator 17, absorbs heat from the cooling water in the low-temperature cooling water circuit 30, and evaporates. Thereby, the cooling water in the low-temperature cooling water circuit 30 is cooled. The cooling water of the low-temperature cooling water circuit 30 cooled by the second evaporator 17 flows into the battery 33 and absorbs heat from the battery 33 . Thereby, the battery 33 is cooled.

In the high cooling mode, the rotation speed of the compressor 11 is increased and the temperature TE2 of the second evaporator 17 is lowered compared to the standard mode, so the battery can be cooled with a higher capacity compared to the standard mode.

In the energy saving mode, as in the standard mode, the control device 60 operates the compressor 11, the high temperature side pump 21, the low temperature side pump 31, and the indoor fan 53 to throttle the first expansion valve 13 and the second expansion valve. 16 is the aperture state.

The control device 60 determines the operating states of various control devices connected to the control device 60 (control signals to be output to various control devices) based on the target blowout temperature TAO, detection signals from the sensor group, and the like.

Regarding the control signal output to the compressor 11 (in other words, the rotation speed of the compressor 11), the second 1 The temperature TE1 of the evaporator 14 is determined so as to approach the energy-saving target temperature TEOe. As shown in FIG. 3, the energy-saving target temperature TEOe is determined to be higher than the standard target temperature TEOs. As a result, in the energy saving mode, the rotational speed of the compressor 11 is lower than in the standard mode.

Regarding the control signal output to the first expansion valve 13 (in other words, the throttle opening degree of the first expansion valve 13), as in the standard mode, the degree of superheat of the refrigerant at the outlet of the first evaporator 14 is determined by the cycle. The coefficient of performance (so-called COP) is determined so as to approach the first target degree of superheat, which is predetermined so as to approach the maximum value.

Regarding the control signal output to the second expansion valve 16 (in other words, the throttle opening degree of the second expansion valve 16), as in the standard mode, the degree of superheat of the refrigerant at the outlet of the second evaporator 17 is determined by the cycle. The coefficient of performance (so-called COP) is determined so as to approach a predetermined second target degree of superheat so as to approach the maximum value.

The control signal output to the indoor fan 53 (in other words, the air volume of the indoor fan 53) is determined based on the target outlet temperature TAO, as in the standard mode.

Regarding the control signal (in other words, the air mix opening SW) output to the servomotor of the air mix door 54, the target outlet temperature TAO and the first evaporator temperature sensor 64 detected by the first evaporator temperature sensor 64 1 Based on the evaporator temperature TE1 and the heater core temperature TH detected by the heater core temperature sensor 66, the temperature of the air blown into the passenger compartment is determined so as to approach the target air temperature TAO.

As in the standard mode, the control signal output to the on-off valve 24 is determined so that the temperature TW of the coolant in the high-temperature coolant circuit 20 detected by the high-temperature coolant temperature sensor 68 approaches the target outlet temperature TAO. .

　In the refrigeration cycle device 10 in the energy saving mode, the state of the refrigerant circulating in the cycle changes in the same way as in the standard mode.

That is, the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12 . The refrigerant that has flowed into the condenser 12 releases heat to the cooling water in the high-temperature cooling water circuit 20 . As a result, the refrigerant is cooled and condensed in the condenser 12 .

The refrigerant that has flowed out of the condenser 12 flows into the first expansion valve 13 and is decompressed and expanded by the first expansion valve 13 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the first expansion valve 13 flows into the first evaporator 14, absorbs heat from the air blown into the vehicle interior, and evaporates. This cools the air blown into the vehicle interior.

Then, the refrigerant that has flowed out of the first evaporator 14 flows to the suction side of the compressor 11 and is compressed again by the compressor 11 .

The cooling water in the high-temperature cooling water circuit 20 radiated from the refrigerant in the condenser 12 is circulated to the heater core 22 . In the heater core 22 , the air cooled by the first evaporator 14 is heated by the cooling water of the high temperature cooling water circuit 20 .

As described above, in the energy-saving mode, the first evaporator 14 allows the low-pressure refrigerant to absorb heat from the air, cools the air, heats the cooled air with the heater core 22, and blows it into the passenger compartment. This makes it possible to air-condition the passenger compartment.

Furthermore, in the energy saving mode, the refrigerant that has flowed out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the second evaporator 17, absorbs heat from the cooling water in the low-temperature cooling water circuit 30, and evaporates. Thereby, the cooling water in the low-temperature cooling water circuit 30 is cooled. The cooling water of the low-temperature cooling water circuit 30 cooled by the second evaporator 17 flows into the battery 33 and absorbs heat from the battery 33 . Thereby, the battery 33 is cooled.

In the energy-saving mode, the rotation speed of the compressor 11 is made lower than in the standard mode, so power saving (that is, energy saving) of the compressor 11 can be achieved compared to the standard mode.

In the independent mode, the control device 60 operates the compressor 11, the high-temperature side pump 21, and the low-temperature side pump 31, stops the indoor fan 53, fully closes the first expansion valve 13, and closes the second expansion valve 16. Aperture state.

The control device 60 determines the operating states of various control devices connected to the control device 60 (control signals to be output to various control devices) based on the target battery temperature TBO, detection signals from the sensor group, and the like.

Regarding the control signal output to the compressor 11 (in other words, the rotation speed of the compressor 11), the second The temperature TE2 of the second evaporator 17 is determined so as to approach the single target temperature TEOa.

The independent target temperature TEOa is determined by referring to the control map stored in the control device 60 based on the target battery temperature TBO and the like. The target battery temperature TBO is the target temperature of the battery 33 . For example, the target battery temperature TBO is determined by referring to a control map stored in the control device 60 based on the amount of heat generated by the battery 33, the outside air temperature Tam, and the like. In the control map of this embodiment, the target battery temperature TBO is determined to decrease as the amount of heat generated by the battery 33 increases. In the control map of the present embodiment, the target battery temperature TBO is determined to decrease as the outside air temperature Tam increases.

In the control map of the present embodiment, the single target temperature TEOa is determined to decrease as the target battery temperature TBO decreases. As shown in FIG. 4, the single target temperature TEOa is determined to be lower than the ambient temperature of the first evaporator 14 (in this example, approximately the first evaporator temperature TE1 is used). As a result, in the single mode, the pressure in the first evaporator 14 is higher than the pressure of the refrigerant at the outlet of the second evaporator 17, so that the refrigerant is prevented from stagnating in the first evaporator 14.

Regarding the control signal output to the second expansion valve 16 (in other words, the throttle opening degree of the second expansion valve 16), as in the standard mode, the degree of superheat of the refrigerant at the outlet of the second evaporator 17 is determined by the cycle. The coefficient of performance (so-called COP) is determined so as to approach a predetermined second target degree of superheat so as to approach the maximum value.

In the independent mode, the on-off valve 24 is opened, so the cooling water circulates in the high-temperature side radiator 23, and the radiator 23 radiates heat from the cooling water to the outside air.

　In the refrigeration cycle device 10 in the single mode, the state of the refrigerant circulating in the cycle changes as follows.

That is, the high pressure refrigerant discharged from the compressor 11 flows into the condenser 12 . The refrigerant that has flowed into the condenser 12 releases heat to the cooling water in the high-temperature cooling water circuit 20 . As a result, the refrigerant is cooled and condensed in the condenser 12 .

The refrigerant that has flowed out of the condenser 12 flows into the second expansion valve 16 and is decompressed and expanded by the second expansion valve 16 until it becomes a low-pressure refrigerant. The low-pressure refrigerant decompressed by the second expansion valve 16 flows into the second evaporator 17, absorbs heat from the cooling water in the low-temperature cooling water circuit 30, and evaporates. Thereby, the cooling water in the low-temperature cooling water circuit 30 is cooled. The cooling water of the low-temperature cooling water circuit 30 cooled by the second evaporator 17 flows into the battery 33 and absorbs heat from the battery 33 . Thereby, the battery 33 is cooled.

Then, the refrigerant flowing out of the second evaporator 17 flows to the suction side of the compressor 11 and is compressed by the compressor 11 again.

In the single mode, the pressure inside the first evaporator 14 is higher than the pressure of the refrigerant at the outlet of the second evaporator 17, so the refrigerant can be prevented from stagnating inside the first evaporator 14.

That is, it is suppressed that part of the refrigerant flowing out of the second evaporator 17 and flowing to the suction side of the compressor 11 flows back from the outlet side of the first evaporator 14 and stays in the first evaporator 14. can.

The control device 60 switches between the air conditioning mode, the standard mode, the energy saving mode, and the independent mode by executing the control processing shown in the flowchart of FIG.

In step S100, it is determined whether or not the battery 33 needs to be cooled. For example, when the temperature TB of the battery 33 detected by the battery temperature sensor 73 exceeds the cooling reference temperature RTB, it is determined that the battery 33 needs to be cooled.

If it is determined in step S100 that the battery 33 does not need to be cooled, the process proceeds to step S110 and switches to the air conditioning mode.

If it is determined in step S100 that the battery 33 needs to be cooled, the process proceeds to step S120 to determine whether it is necessary to dehumidify the vehicle interior. Specifically, when the air conditioner switch on the operation panel 75 is turned on, it is determined that it is necessary to dehumidify the vehicle interior. That is, when the air conditioner switch on the operation panel 75 is turned on, it is determined that the first evaporator 14 needs to cool and dehumidify the air.

If it is determined in step S120 that it is not necessary to dehumidify the vehicle interior, the process proceeds to step S130 and is switched to the single mode.

When it is determined in step S120 that it is necessary to dehumidify the vehicle interior, the process proceeds to step S140, in which it is determined whether or not the target battery temperature TBO exceeds the energy saving reference temperature αe. The energy-saving reference temperature αe is a value higher than the high cooling target temperature TEOc.

If it is determined in step S140 that the target battery temperature TBO is higher than the energy saving reference temperature αe, the process proceeds to step S150 to switch to the energy saving mode.

If it is determined in step S140 that the target battery temperature TBO does not exceed the energy saving reference temperature αe, the process proceeds to step S160 to determine whether or not the target battery temperature TBO exceeds the high cooling reference temperature αc. The high cooling reference temperature αc is higher than the high cooling target temperature TEOc and lower than the energy saving reference temperature αe.

If it is determined in step S160 that the target battery temperature TBO is higher than the high cooling reference temperature αc, the process proceeds to step S170 to switch to the standard mode.

If it is determined in step S160 that the target battery temperature TBO does not exceed the high cooling reference temperature αc, the process advances to step S180 to switch to the high cooling mode.

In this embodiment, the control device 60 has an energy saving mode for controlling the compressor 11 so that the temperature TE1 of the first evaporator 14 approaches the energy saving target temperature TEOe, and in the energy saving mode, the target temperature TBO of the battery 33 is the energy saving reference temperature. When the temperature falls below αe, the temperature TE1 of the first evaporator 14 switches to the standard mode in which the compressor 11 is controlled so as to approach the standard target temperature TEOs, which is lower than the energy-saving target temperature TEOe.

According to this, the energy saving mode can save energy, and the standard mode can secure the cooling capacity.

In this embodiment, the controller 60 controls the compressor 11 so that the temperature TE1 of the first evaporator 14 approaches the standard target temperature TEOs, and in the standard mode, the target temperature TBO of the battery 33 is set to the high cooling standard. When the temperature falls below the temperature αc, the temperature TE2 of the second evaporator 17 switches to a high cooling mode that controls the compressor 11 so as to approach the high cooling target temperature TEOc that is lower than the standard target temperature TEOs.

According to this, the standard mode saves energy, and the high cooling mode ensures cooling capacity.

In the present embodiment, the control device 60 has a standard mode for controlling the compressor 11 so that the temperature TE1 of the first evaporator 14 approaches the standard target temperature TEOs, and in the standard mode, the first expansion valve 13 is set to the first evaporator. 14, and controls the compressor 11 so that the temperature TE2 of the second evaporator 17 approaches the single target temperature TEOa that is lower than the temperature TE1 of the first evaporator 14. Switch to and from solo mode.

According to this, it is possible to save energy in the standard mode and secure cooling capacity in the independent mode.

In this embodiment, the control device 60 switches to the energy saving mode when the target temperature TBO of the battery 33 exceeds the energy saving reference temperature αe in the standard mode. As a result, it is possible to appropriately switch between the standard mode and the energy saving mode to achieve both energy saving and securing of cooling capacity.

In this embodiment, the control device 60 switches to the standard mode when the target temperature TBO of the battery 33 exceeds the high cooling reference temperature αc in the high cooling mode. As a result, it is possible to appropriately switch between the high cooling mode and the standard mode to achieve both energy saving and securing of cooling capacity.

In this embodiment, the control device 60 switches to the standard mode when the first expansion valve 13 causes the refrigerant to flow to the first evaporator 14 in the independent mode. As a result, it is possible to appropriately switch between the independent mode and the standard mode to achieve both energy saving and securing of cooling capacity.

In the present embodiment, when the target temperature TBO of the battery 33 is lower than the high cooling reference temperature αc in the standard mode, the control device 60 sets the temperature of the second evaporator 17 to the high cooling target temperature lower than the standard target temperature TEOs. Switch to a high cooling mode that controls the compressor 11 to approach TEOc. As a result, the energy saving mode, the standard mode, and the high cooling mode can be appropriately switched to achieve both energy saving and securing of cooling capacity.

In the present embodiment, when the target temperature TBO of the battery 33 exceeds the energy-saving reference temperature αe in the standard mode, the control device 60 sets the temperature TE1 of the first evaporator 14 to the energy-saving target temperature TEOe higher than the standard target temperature TEOs. is switched to an energy-saving mode that controls the compressor 11 so as to approach

As a result, it is possible to appropriately switch between standard mode, high cooling mode, and energy saving mode to achieve both energy saving and cooling capacity.

In the present embodiment, in the energy saving mode, the control device 60 controls the first expansion valve 13 based on the degree of superheat of the refrigerant flowing out of the first evaporator 14, and superheats the refrigerant flowing out of the second evaporator 17. In the standard mode, the first expansion valve 13 is controlled based on the degree of superheat of the refrigerant flowing out of the first evaporator 14 and outflowing from the second evaporator 17 The second expansion valve 16 is controlled based on the degree of superheat of the refrigerant. Thereby, good cycle efficiency can be obtained in the energy saving mode and the standard mode.

In the present embodiment, in the standard mode, the control device 60 controls the first expansion valve 13 based on the degree of superheat of the refrigerant flowing out of the first evaporator 14, and superheats the refrigerant flowing out of the second evaporator 17. In the high cooling mode, the second expansion valve 16 is controlled based on the degree of superheat of the refrigerant flowing out of the second evaporator 17 . Thereby, good cycle efficiency can be obtained in the standard mode and the high cooling mode.

In the present embodiment, in the standard mode, the control device 60 controls the first expansion valve 13 based on the degree of superheat of the refrigerant flowing out of the first evaporator 14, and superheats the refrigerant flowing out of the second evaporator 17. In the independent mode, the second expansion valve 16 is controlled based on the degree of superheat of the refrigerant flowing out of the second evaporator 17 . Thereby, good cycle efficiency can be obtained in the standard mode and the independent mode.

In this embodiment, the first expansion valve 13 and the first evaporator 14, and the second expansion valve 16 and the second evaporator 17 are arranged in parallel with each other in the refrigerant flow. Thereby, pressure loss can be reduced and good performance can be obtained.

(Second embodiment)
In the above embodiment, the first evaporator 14 and the second evaporator 17 are arranged in parallel with each other in the refrigerant flow of the refrigeration cycle device 10, but in this embodiment, as shown in FIG. The evaporator 14 and the second evaporator 17 are arranged in series with each other in the refrigerant flow of the refrigeration cycle device 10 .

The second expansion valve 16 and the second evaporator 17 are arranged downstream of the first evaporator 14 in the refrigerant flow.

The refrigeration cycle device 10 has a bypass flow path 40 . The bypass flow path 40 is a refrigerant flow path through which the refrigerant flowing out of the receiver 18 bypasses the first expansion valve 13 and the first evaporator 14 and flows to the second expansion valve 16 . A bypass opening/closing valve 41 is arranged in the bypass flow path 40 . The bypass opening/closing valve 41 is an electromagnetic valve that opens and closes the bypass flow path 40 and is controlled by the controller 60 .

When switching to the air conditioning mode, the controller 60 closes the bypass on-off valve 41, so the refrigerant absorbs heat from the air and evaporates in the first evaporator 14. In the air conditioning mode, the control device 60 fully opens the second expansion valve 16 and stops the low temperature side pump 31, so that heat exchange between the refrigerant and the cooling water of the low temperature cooling water circuit 30 is not performed in the second evaporator 17. rarely done.

When switching to the standard mode, the high cooling mode, and the energy saving mode, the control device 60 closes the bypass on-off valve 41, so the refrigerant absorbs heat from the air in the first evaporator 14 and evaporates, and the refrigerant in the second evaporator 17 It absorbs heat from the cooling water in the low-temperature cooling water circuit 30 and evaporates.

When switching to the independent mode, the control device 60 opens the bypass on-off valve 41 and closes the first expansion valve 13, so that heat exchange between the refrigerant and the air is not performed in the first evaporator 14, and the second evaporator At 17, the refrigerant absorbs heat from the cooling water in the low-temperature cooling water circuit 30 and evaporates.

The air conditioning mode, standard mode, high cooling mode, energy saving mode, and single mode are switched under the same switching conditions as in the first embodiment, and the standard mode, high cooling mode, energy saving mode, and single mode are switched in the same manner as in the first embodiment. By controlling the compressor 11, the first expansion valve 13, the second expansion valve 16, etc., the same effects as those of the first embodiment can be obtained.

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.

Although cooling water is used as the heat medium in the above embodiment, various media such as oil may be used as the heat medium. A nanofluid may be used as a heat carrier. A nanofluid is a fluid mixed with nanoparticles having a particle size on the order of nanometers.

In the refrigeration cycle apparatus 10 of the above-described embodiment, a freon-based refrigerant is used as a refrigerant, but the type of refrigerant is not limited to this, and natural refrigerants such as carbon dioxide, hydrocarbon-based refrigerants, etc. may be used. good.

Further, the refrigerating cycle device 10 of the above embodiment constitutes a subcritical refrigerating cycle in which the high pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant, but a supercritical refrigerating cycle in which the high pressure side refrigerant pressure exceeds the critical pressure of the refrigerant. may constitute

In the above embodiment, the high temperature side radiator 23 and the low temperature side radiator 32 are separate radiators, but the high temperature side radiator 23 and the low temperature side radiator 32 may be configured as a single radiator.

For example, the tank of the high temperature side radiator 23 and the tank of the low temperature side radiator 32 may be integrated with each other so that the high temperature side radiator 23 and the low temperature side radiator 32 are configured as one radiator.

In the above-described embodiment, the first expansion valve 13 is configured integrally with the decompression portion for decompressing the refrigerant and the shutoff portion 13a for shutting off the flow of the refrigerant by fully closing the flow path of the refrigerant. However, the cutoff portion 13a may be separate from the first expansion valve 13 .

The condenser 12 in the above embodiment is a heat exchanger that exchanges heat between refrigerant and cooling water, but the condenser 12 may be a heat exchanger that exchanges heat between refrigerant and air.

In the above embodiment, the battery 33 is cooled by cooling water cooled by the refrigerant in the second evaporator 17, but the battery 33 may be directly cooled by the refrigerant or cooled by air cooled by the refrigerant. may be

Although the refrigeration cycle device 10 is a receiver cycle having the receiver 18 in the above embodiment, the refrigeration cycle device 10 may be an accumulator cycle having an accumulator.

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 (12)

1. a compressor (11) that sucks, compresses, and discharges refrigerant;
   a heat radiating section (12) for radiating heat from the refrigerant discharged from the compressor;
   a first decompression section (13) and a second decompression section (16) for decompressing the refrigerant radiated by the heat radiation section;
   a first evaporator (14) that evaporates the refrigerant decompressed by the first decompressor by causing the refrigerant to absorb heat from the air that is blown into the air-conditioned space;
   a second evaporator (17) for evaporating the refrigerant by allowing the refrigerant decompressed by the second decompression unit to absorb heat from an object (33) to be cooled;
   an energy saving mode for controlling the compressor so that the temperature (TE1) of the first evaporator approaches the energy saving target temperature (TEOe); αe), and the temperature of the first evaporator switches to the standard mode that controls the compressor so that it approaches a standard target temperature (TEOs) that is lower than the energy saving target temperature ( 60).
2. a compressor (11) that sucks, compresses, and discharges refrigerant;
   a heat radiating section (12) for radiating heat from the refrigerant discharged from the compressor;
   a first decompression section (13) and a second decompression section (16) for decompressing the refrigerant radiated by the heat radiation section;
   a first evaporator (14) that evaporates the refrigerant decompressed by the first decompressor by causing the refrigerant to absorb heat from the air that is blown into the air-conditioned space;
   a pressure adjusting section (15) for maintaining the pressure of the refrigerant flowing out of the first evaporating section at a predetermined pressure or higher;
   a second evaporator (17) for evaporating the refrigerant by allowing the refrigerant decompressed by the second decompression unit to absorb heat from an object (33) to be cooled;
   a standard mode for controlling the compressor so that the temperature (TE1) of the first evaporator approaches the standard target temperature (TEOs); (αc), the temperature of the second evaporator (TE2) controls the compressor to approach a high cooling target temperature (TEOc) that is lower than the standard target temperature. A refrigeration cycle apparatus comprising a control unit (60) for switching between and.
3. a compressor (11) that sucks, compresses, and discharges refrigerant;
   a heat radiating section (12) for radiating heat from the refrigerant discharged from the compressor;
   a first decompression section (13) and a second decompression section (16) for decompressing the refrigerant radiated by the heat radiation section;
   a first evaporator (14) that evaporates the refrigerant decompressed by the first decompressor by causing the refrigerant to absorb heat from the air that is blown into the air-conditioned space;
   a second evaporator (17) for evaporating the refrigerant by allowing the refrigerant decompressed by the second decompression unit to absorb heat from an object (33) to be cooled;
   a blocking portion (13a) for blocking circulation of the refrigerant to the first evaporating portion;
   a standard mode in which the compressor is controlled so that the temperature (TE1) of the first evaporator approaches a standard target temperature (TEOs); is shut off, and the temperature of the second evaporator (TE2) controls the compressor so that it approaches a single target temperature (TEOa) lower than the temperature of the first evaporator; A refrigeration cycle device comprising a control unit (60) for switching between.
4. The refrigeration cycle apparatus according to claim 1, wherein the control unit switches to the energy saving mode when the target temperature of the object to be cooled exceeds the energy saving reference temperature in the standard mode.
5. The refrigeration cycle apparatus according to claim 2, wherein the control unit switches to the standard mode when the target temperature of the object to be cooled exceeds the high cooling reference temperature in the high cooling mode.
6. 4. The refrigeration cycle apparatus according to claim 3, wherein the control unit switches to the standard mode when the cutoff unit causes the refrigerant to flow to the first evaporator in the independent mode.
7. a pressure adjusting unit (15) for maintaining the pressure of the refrigerant flowing out of the first evaporating unit at a predetermined pressure or higher;
   When the target temperature of the object to be cooled falls below a high cooling reference temperature in the standard mode, the control unit sets the temperature of the second evaporator to a high cooling target temperature (TEOc) lower than the standard target temperature. 2. The refrigeration cycle apparatus according to claim 1, wherein the refrigeration cycle apparatus is switched to a high cooling mode in which the compressor is controlled to approach.
8. When the target temperature of the object to be cooled exceeds the energy-saving reference temperature in the standard mode, the control unit sets the temperature (TE1) of the first evaporator to an energy-saving target temperature (TEOe) higher than the standard target temperature. 3. The refrigeration cycle apparatus according to claim 2, wherein the switching is made to an energy saving mode in which the compressor is controlled so as to approach .
9. The control unit
   In the energy saving mode, the first pressure reducing unit is controlled based on the state of the refrigerant flowing out of the first evaporating unit, and the second pressure reducing unit is controlled based on the state of the refrigerant flowing out of the second evaporating unit. to control the
   In the standard mode, the first pressure reducing section is controlled based on the state of the refrigerant flowing out of the first evaporating section, and the second pressure reducing section is controlled based on the state of the refrigerant flowing out of the second evaporating section. The refrigeration cycle apparatus according to any one of claims 1, 4, 7, and 8, which controls
10. The control unit
    In the standard mode, the first pressure reducing section is controlled based on the state of the refrigerant flowing out of the first evaporating section, and the second pressure reducing section is controlled based on the state of the refrigerant flowing out of the second evaporating section. to control the
    The refrigeration cycle apparatus according to any one of claims 2, 5, 7, and 8, wherein in the high cooling mode, the second pressure reducing section is controlled based on the state of the refrigerant flowing out of the second evaporating section.
11. The control unit
    In the standard mode, the first pressure reducing section is controlled based on the state of the refrigerant flowing out of the first evaporating section, and the second pressure reducing section is controlled based on the state of the refrigerant flowing out of the second evaporating section. to control the
    7. The refrigeration cycle apparatus according to claim 3, wherein in said independent mode, said second pressure reducing section is controlled based on the state of said refrigerant flowing out of said second evaporating section.
12. 12. The method according to any one of claims 1 to 11, wherein the first decompression section and the first evaporator, and the second decompression section and the second evaporator are arranged in parallel with each other in the flow of the refrigerant. A refrigeration cycle apparatus as described.

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