WO2017098795A1

WO2017098795A1 - Refrigeration cycle device

Info

Publication number: WO2017098795A1
Application number: PCT/JP2016/079722
Authority: WO
Inventors: 加藤　吉毅; 橋村　信幸; 功嗣三浦; 憲彦榎本; 賢吾杉村; 慧伍佐藤; 竹内　雅之; アリエルマラシガン
Original assignee: 株式会社デンソー
Priority date: 2015-12-10
Filing date: 2016-10-06
Publication date: 2017-06-15

Abstract

This refrigeration cycle device is equipped with: a first expansion valve (13) which decompresses the refrigerant flowing out from a high-pressure-side heat exchanger (12); an outdoor heat exchanger (14) which heat exchanges the refrigerant flowing out from the first expansion valve (13) and outside air; a second expansion valve (15) which decompresses the refrigerant flowing out from the outdoor heat exchanger (14); a low-pressure-side heat exchanger (16) which is disposed in series with the outdoor heat exchanger (14) in the flow of the refrigerant so as to cool a heat carrier by heat exchanging the low-pressure refrigerant decompressed by the first decompression unit (13) and/or the second decompression unit (15) and the heat carrier; a cooler core (26) which cools air by heat exchanging the heat carrier cooled by the low-pressure-side heat exchanger (16) and the air sent to the interior of a vehicle; and a control unit (30) which switches between a heat absorption mode and a heat radiation mode by adjusting the decompression amounts of the first expansion valve (13) and the second expansion valve (15).

Description

Refrigeration cycle equipment

Cross-reference of related applications

This application includes Japanese Patent Application No. 2015-240923 filed on Dec. 10, 2015, and Japanese Patent Application No. 2016 filed on Aug. 10, 2016, the disclosures of which are incorporated herein by reference. Based on -157692.

This disclosure relates to a refrigeration cycle apparatus including a heat exchanger that exchanges heat between refrigerant and outside air.

Conventionally, Patent Document 1 describes a vehicular refrigeration cycle apparatus including a compressor, an indoor condenser, a first expansion valve, a second expansion valve, an outdoor heat exchanger, an indoor evaporator, and an accumulator.

Compressor sucks in refrigerant, compresses it, and discharges it. Refrigerating machine oil for lubricating the compressor is mixed in the refrigerant, and a part of the refrigerating machine oil circulates in the cycle together with the refrigerant.

The indoor condenser is a radiator that dissipates the high-pressure refrigerant discharged from the compressor and heats the air blown into the vehicle interior that has passed through the indoor evaporator.

The first expansion valve exerts a decompression action of the refrigerant in the heating mode and the dehumidifying heating mode. The second expansion valve exerts a refrigerant decompression action in the cooling mode and the dehumidifying heating mode.

The outdoor heat exchanger exchanges heat between the refrigerant and the outside air. The outdoor heat exchanger functions as an evaporator that evaporates the refrigerant and exerts an endothermic effect in the heating mode and the like, and functions as a radiator that radiates the refrigerant in the cooling mode and the like.

The indoor evaporator, in the cooling mode and the dehumidifying and heating mode, evaporates the refrigerant flowing through the interior by exchanging heat with the air blown into the vehicle compartment before passing through the indoor condenser, thereby exhibiting an endothermic effect. This is an evaporator for cooling the air blown into the vehicle interior.

The accumulator is a gas-liquid separator that separates the gas-liquid refrigerant flowing into the accumulator and stores excess refrigerant in the cycle. The suction port side of the compressor is connected to the gas phase refrigerant outlet of the accumulator. Accordingly, the accumulator functions to prevent liquid phase refrigerant from being sucked into the compressor and prevent liquid compression in the compressor.

In this prior art, the accumulator is disposed on the refrigerant outlet side of the indoor evaporator and on the refrigerant suction side of the compressor.

Patent Document 2 describes a refrigeration cycle device for a vehicle including a chiller, a cooler core, and a cooling water pump.

The chiller is a heat exchanger that cools the cooling water by exchanging heat between the low-pressure refrigerant in the refrigeration cycle and the cooling water. The cooler core is a heat exchanger that heat-exchanges the cooling water cooled by the chiller and the air blown into the vehicle interior to cool and dehumidify the air blown into the vehicle interior. The cooling water pump sucks and discharges the cooling water circulating between the chiller and the cooler core.

The vehicle refrigeration cycle apparatus of Patent Literature 2 includes a heater core and a radiator. The heater core is a heat exchanger that heats air that is blown into the vehicle interior that has passed through the cooler core, using the high-pressure side refrigerant of the refrigeration cycle as a heat source. The radiator is a heat exchanger that exchanges heat between the cooling water cooled by the chiller, the cooling water, and the outside air.

Cooling water cooled by the low-pressure side refrigerant of the refrigeration cycle absorbs heat from the outside air by the radiator and absorbs heat from the air blown into the passenger compartment by the cooler core, and the air absorbed by the cooler core is used as the high-pressure side refrigerant of the refrigeration cycle. Dehumidification heating can be performed by heating with a heater core as a heat source.

JP 2012-225637 A Japanese Patent Laid-Open No. 2015-013639

According to the study of the inventors of the present application, in the prior art of Patent Document 1, the refrigerant pressure in the outdoor heat exchanger is lowered in order to ensure sufficient heating performance of the indoor condenser in the heating mode or the like. Therefore, it is necessary to increase the amount of heat absorbed from the outside air of the refrigerant in the outdoor heat exchanger.

However, if the refrigerant pressure in the outdoor heat exchanger falls below a certain level, the condensed water generated on the surface of the indoor evaporator freezes and frost is generated. Therefore, since the air volume passing through the indoor evaporator is reduced, it becomes impossible to obtain the heat exchange capability required for the indoor evaporator.

As a countermeasure against this, the bypass flow path in which the refrigerant flows in parallel to the indoor evaporator, the state in which the refrigerant flows to the indoor evaporator side, and the state in which the refrigerant flows to the bypass flow path are alternately switched to adjust the evaporation pressure. It is conceivable to suppress the frost by suppressing the decrease in the evaporation pressure by providing a pressure regulating valve.

However, according to this measure, when the refrigerant is flowing through the indoor evaporator, if the flow rate of the refrigerant flowing through the indoor evaporator is reduced, the flow rate of the refrigerant flowing through the outdoor heat exchanger is also reduced. Tends to be reduced.

In view of the above points, the present disclosure is directed to lowering the pressure of the refrigerant in the heat exchanger that exchanges heat between the refrigerant and the outside air to increase the amount of heat absorbed from the outside air, and the frost in the heat exchanger that cools the air. A first object is to achieve both suppression of generation.

In the prior art disclosed in Patent Document 1, the accumulator also has a function of returning the refrigeration oil in the refrigerant to the compressor. However, the accumulator is provided on the refrigerant outlet side of the indoor evaporator and on the refrigerant suction side of the compressor. Since it is arranged, the refrigerant and the refrigerating machine oil in the accumulator are likely to be low temperature and low pressure.

Therefore, the viscosity of the refrigerant and refrigerating machine oil in the accumulator increases, and it becomes difficult to return the refrigerating machine oil to the compressor. Therefore, it is necessary to increase the amount of refrigerating machine oil in the refrigerant so that a desired amount of refrigerating machine oil can be returned. Therefore, in the refrigerant mode in which the low-pressure refrigerant pressure becomes high, the return amount of the refrigerating machine oil becomes excessive, and the cooling performance is deteriorated.

Also, since the refrigerant in the accumulator becomes low temperature and low pressure, refrigerant pressure loss in the accumulator increases. In particular, the refrigerant pressure loss increases during the heating mode in which the low-pressure refrigerant pressure is low. As a result, the heating performance is also reduced.

In view of the above points, a second object of the present disclosure is to improve the discharge performance of the refrigeration oil in the refrigerant reservoir and to reduce the pressure loss of the refrigerant in the refrigerant reservoir.

In the prior art of Patent Document 2 described above, when there is a possibility that frost may be generated in the cooler core, generation of frost is prevented by stopping the cooling water pump and stopping heat exchange in the cooler core.

At this time, at the cooling water outlet of the chiller, the temperature of the cooling water is equal to or lower than the outside air temperature, and at the heat exchanger of the cooler core, the temperature of the cooling water is equal to the inside air temperature or the outside air temperature. That is, there is a temperature difference between the cooling water between the chiller and the cooler core. Therefore, even if the cooling water pump is stopped, the low-temperature cooling water of the chiller gradually moves to the cooler core due to convection, so unnecessary heat exchange may occur if the air blowing to the cooler core is continued. The occurrence of frost in the cooler core cannot be sufficiently prevented.

In view of the above points, the present disclosure has a third object of suppressing movement of cooling water between the chiller and the cooler core when circulation of the heat medium between the chiller and the cooler core is stopped. To do.

In the prior art of Patent Document 2, when performing dehumidifying heating, the rotation speed of the compressor is increased to increase the temperature of the air blown from the heater core. However, when the rotation speed of the compressor is increased, frost may occur in the cooler core.

Specifically, when the rotation speed of the compressor is increased, the low pressure of the refrigeration cycle is lowered and the temperature of the cooling water cooled by the chiller is lowered, so that the temperature of the refrigerant flowing into the cooler core is also lowered. As a result, when the surface temperature of the cooler core becomes 0 ° C. or lower, moisture in the air freezes and adheres as ice on the surface of the cooler core, so that air circulation in the cooler core is hindered.

In view of the above points, a fourth object of the present disclosure is to ensure both the temperature of the air blown into the passenger compartment and the suppression of frost generation in the cooler core.

The refrigeration cycle apparatus according to the first aspect of the present disclosure flows out of the compressor that sucks and discharges the refrigerant, the high-pressure side heat exchanger that dissipates the high-pressure refrigerant discharged from the compressor, and the high-pressure side heat exchanger. A first decompression unit for decompressing the refrigerant, a refrigerant outside air heat exchanger for exchanging heat between the refrigerant flowing out from the first decompression unit and the outside air, a second decompression unit for decompressing the refrigerant flowing out from the refrigerant outside air heat exchanger, A low pressure that is arranged in series with the refrigerant outside air heat exchanger in the flow of the refrigerant and cools the heat medium by exchanging heat between the low-pressure refrigerant and the heat medium decompressed at least one of the first decompression unit and the second decompression unit. A side heat exchanger, a cooler core that cools air by exchanging heat between the heat medium cooled by the low-pressure side heat exchanger and the air blown into the vehicle interior, and reduced pressure amounts of the first pressure reducing unit and the second pressure reducing unit Adjust the refrigerant outside air heat exchange And a controller that switches between an endothermic mode in which the refrigerant absorbs heat to the refrigerant and a heat radiation mode in which the refrigerant outside air heat exchanger radiates heat from the refrigerant.

According to this, since the control unit can switch between the heat absorption mode and the heat dissipation mode by adjusting the amount of pressure reduction of the first pressure reduction unit and the second pressure reduction unit, the heat absorption mode and the heat dissipation mode are switched with a simple configuration. Can do.

In addition, since the heat medium is interposed between the low pressure side heat exchanger and the cooler core, the temperature of the heat medium flowing into the cooler core is lower than the temperature of the air cooled by the cooler core, and flows into the cooler core. The temperature of the refrigerant flowing into the low-pressure side heat exchanger becomes lower than the temperature of the heat medium that performs.

Therefore, the refrigerant temperature in the low-pressure side heat exchanger can be lowered, and as a result, the refrigerant pressure in the low-pressure side heat exchanger can be lowered as compared with a configuration in which heat is directly exchanged between the refrigerant and air in the indoor evaporator.

Therefore, the refrigerant pressure in the refrigerant outside air heat exchanger can be lowered to increase the amount of heat absorbed from the outside air of the refrigerant in the refrigerant outside air heat exchanger, and the generation of frost in the cooler core can be suppressed.

The refrigeration cycle apparatus according to the second aspect of the present disclosure flows out of the compressor that sucks and discharges the refrigerant, the high-pressure side heat exchanger that dissipates the high-pressure refrigerant discharged from the compressor, and the high-pressure side heat exchanger. A first decompression unit for decompressing the refrigerant, a refrigerant outside air heat exchanger for exchanging heat between the refrigerant flowing out from the first decompression unit and the outside air, a second decompression unit for decompressing the refrigerant flowing out from the refrigerant outside air heat exchanger, By adjusting the pressure reduction amount of the low pressure side heat exchanger that absorbs heat to the low pressure refrigerant decompressed at least one of the first decompression unit and the second decompression unit, and the decompression amount of the first decompression unit and the second decompression unit, the refrigerant outside air A controller that switches between an endothermic mode in which the heat exchanger absorbs heat into the refrigerant and a heat release mode in which the refrigerant outside air heat exchanger dissipates heat from the refrigerant, and in the endothermic mode, the heat exchanged by the high-pressure heat exchanger is stored and dissipated. Mode, refrigerant And a coolant reservoir for storing a refrigerant heat exchange in a gas heat exchanger.

According to this, the refrigerant reservoir can be provided on the cycle high pressure side in both the heat absorption mode and the heat release mode. In other words, the refrigeration cycle can be converted into a receiver cycle in both the heat absorption mode and the heat dissipation mode.

Therefore, since the viscosity of the refrigerant and the refrigeration oil in the refrigerant storage section is smaller than that of the accumulator cycle having the refrigerant storage section on the cycle low pressure side, the pressure loss of the refrigerant can be reduced and the discharge performance of the refrigeration oil can be improved.

The refrigeration cycle apparatus according to the third aspect of the present disclosure flows out of the compressor that sucks and discharges the refrigerant, the high-pressure side heat exchanger that dissipates the high-pressure refrigerant discharged from the compressor, and the high-pressure side heat exchanger. A decompression unit that decompresses the refrigerant, a low-pressure side heat exchanger that cools the heat medium by exchanging heat between the low-pressure refrigerant decompressed by the decompression unit and the heat medium, and a heat medium that is cooled by the low-pressure side heat exchanger A cooler core having a heat exchanging section for exchanging heat with air to cool the air, a heat medium pump for sucking and discharging the heat medium, and circulating the heat medium between the low pressure side heat exchanger and the cooler core, and the cooler core The low pressure side heat exchanger has an inlet and an outlet for the heat medium, and the heat exchanger is disposed at a position higher in the gravitational direction than at least one of the inlet and the outlet. Has been.

According to this, when the circulation of the heat medium between the low pressure side heat exchanger and the cooler core is stopped, the low temperature heat medium in the low pressure side heat exchanger and the high temperature heat medium in the cooler core are It is possible to suppress switching by convection due to a temperature difference.

The refrigeration cycle apparatus according to the fourth aspect of the present disclosure flows out of the compressor that sucks and discharges the refrigerant, the high-pressure side heat exchanger that dissipates the high-pressure refrigerant discharged from the compressor, and the high-pressure side heat exchanger. A decompression unit that decompresses the refrigerant, a low-pressure side heat exchanger that cools the heat medium by exchanging heat between the low-pressure refrigerant decompressed by the decompression unit and the heat medium, and a heat medium that is cooled by the low-pressure side heat exchanger A cooler core having a heat exchanging section for exchanging heat with air to cool the air, a heat medium pump for sucking and discharging the heat medium, and circulating the heat medium between the low pressure side heat exchanger and the cooler core, and the cooler core And a heat medium flow path section that forms a flow path of the heat medium between the low pressure side heat exchanger and the cooler core. Moreover, the low-pressure side heat exchanger has an inlet and an outlet for the heat medium, and at least a part of the heat medium flow path is disposed at a position lower in the direction of gravity than the heat exchanger.

According to this, the same effect as the refrigeration cycle apparatus according to the third aspect can be obtained.

A refrigeration cycle apparatus according to a fifth aspect of the present disclosure heats air by exchanging heat between a compressor that sucks and discharges refrigerant, and high-pressure refrigerant discharged from the compressor and air blown into the passenger compartment. A high-pressure heat exchanger, a high-pressure heat exchanger that dissipates the high-pressure refrigerant discharged from the compressor, a decompression unit that decompresses the refrigerant flowing out of the high-pressure heat exchanger, and a refrigerant decompressed by the decompression unit; Cooling with a refrigerant outdoor air heat exchanger that exchanges heat with the outside air, a low pressure side heat exchanger that cools the heat medium by exchanging heat between the refrigerant and the heat medium that has flowed out of the refrigerant outside air heat exchanger, and a low pressure side heat exchanger A cooler core that cools the air by exchanging heat between the generated heat medium and the air blown into the vehicle interior, and an in-vehicle device that generates heat during operation and is absorbed by the heat medium cooled by the low-pressure side heat exchanger; , The flow rate of the heat medium flowing in the cooler core and on-vehicle equipment The flow rate adjusting unit for adjusting the flow rate of the flowing heat medium and the frost suppression control for suppressing the frost of the cooler core by controlling the flow rate adjusting unit so as to suppress the flow rate of the heat medium flowing through the cooler core are performed. When performing, it has a control part which controls a flow control part so that a heat carrier may flow into in-vehicle equipment.

According to this, the occurrence of frost in the cooler core can be suppressed by performing the frost suppression control. When the frost suppression control is performed, the heat medium flows through the in-vehicle device, so that the heat can be absorbed from the in-vehicle device. Therefore, even if the amount of heat absorbed from the cooler core is reduced by performing the frost suppression control, the amount of heat absorbed from the in-vehicle device can be compensated, so that the temperature of air blown into the vehicle interior can be secured.

Therefore, it is possible to ensure both the temperature of the air blown into the passenger compartment and the suppression of frost generation in the cooler core.

It is a whole lineblock diagram of the refrigerating cycle device in a 1st embodiment. It is a schematic diagram which shows the outdoor heat exchanger in 1st Embodiment. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus in 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the heating mode of the refrigeration cycle apparatus in 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the air_conditioning | cooling mode of the refrigerating-cycle apparatus in 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 1st dehumidification heating mode of the refrigeration cycle apparatus in 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant at the time of the 2nd dehumidification heating mode of the refrigeration cycle apparatus in 1st Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in the 1st Example of 2nd Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 2nd Example of 2nd Embodiment. It is a schematic diagram which shows the outdoor heat exchanger and shutter in 2nd Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 2nd Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 3rd Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 4th Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 1st Example of 5th Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 2nd Example of 5th Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 3rd Example of 5th Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 1st Example of 6th Embodiment. It is a block diagram which shows a part of refrigeration cycle apparatus in 2nd Example of 6th Embodiment. It is a whole block diagram of the refrigerating-cycle apparatus in 7th Embodiment. It is a graph which illustrates the relationship between the outside air temperature in 7th Embodiment, the target blowing temperature of a heater core, and the target blowing temperature of a cooler core. It is a whole block diagram of the refrigerating-cycle apparatus in 8th Embodiment. It is a flowchart which shows the control processing which the control apparatus of 8th Embodiment performs.

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

(First embodiment)
A refrigeration cycle apparatus 10 shown in FIG. 1 is a vehicular refrigeration cycle apparatus used for adjusting a vehicle interior space to an appropriate temperature. In the present embodiment, the refrigeration cycle apparatus 10 is applied to a hybrid vehicle that obtains driving force for vehicle travel from an engine (in other words, an internal combustion engine) and a travel electric motor.

The hybrid vehicle of the present embodiment is configured as a plug-in hybrid vehicle capable of charging power supplied from an external power source (in other words, commercial power source) when the vehicle is stopped to a battery (in other words, an in-vehicle battery) mounted on the vehicle. Has been. As the battery, for example, a lithium ion battery can be used.

The driving force output from the engine is used not only for driving the vehicle but also for operating the generator. And the electric power generated by the generator and the electric power supplied from the external power source can be stored in the battery, and the electric power stored in the battery constitutes the refrigeration cycle apparatus 10 as well as the electric motor for traveling. It is supplied to various in-vehicle devices such as electric components.

The refrigeration cycle apparatus 10 is a vapor compression refrigerator that includes a compressor 11, a high-pressure side heat exchanger 12, a first expansion valve 13, an outdoor heat exchanger 14, a second expansion valve 15, and a low-pressure side heat exchanger 16. . In the refrigeration cycle apparatus 10 of the present embodiment, a chlorofluorocarbon refrigerant is used as the refrigerant, and a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the refrigerant critical pressure is configured.

The compressor 11 is an electric compressor driven by electric power supplied from a battery or a variable capacity compressor driven by a belt, and sucks, compresses and discharges the refrigerant of the refrigeration cycle apparatus 10.

The high-pressure side heat exchanger 12 is a condenser 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 21.

The cooling water of the high-temperature cooling water circuit 21 is a fluid as a heat medium. The cooling water of the high temperature cooling water circuit 21 is a high temperature heat medium. In the present embodiment, at least ethylene glycol, dimethylpolysiloxane, a liquid containing nanofluid, or an antifreeze liquid is used as the cooling water of the high-temperature cooling water circuit 21.

1st expansion valve 13 is the 1st decompression part which decompresses and expands the liquid phase refrigerant which flowed out from high pressure side heat exchanger 12. The first expansion valve 13 is an electric variable throttle mechanism, and includes a valve body and an electric actuator. The valve body is configured to be able to change the passage opening (in other words, the throttle opening) of the refrigerant passage. 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 open function that fully opens the refrigerant passage when the throttle opening is fully opened. That is, the first expansion valve 13 can prevent the refrigerant from depressurizing by fully opening the refrigerant passage. The operation of the first expansion valve 13 is controlled by a control signal output from the control device 30.

The outdoor heat exchanger 14 is a refrigerant outdoor air heat exchanger that exchanges heat between the refrigerant flowing out of the first expansion valve 13 and the outside air. Outside air is blown to the outdoor heat exchanger 14 by an outdoor blower 17.

The outdoor blower 17 is a blower that blows outside air toward the outdoor heat exchanger 14. The outdoor blower 17 is an electric blower that drives a fan with an electric motor. The outdoor heat exchanger 14 and the outdoor blower 17 are disposed in the foremost part of the vehicle. Accordingly, the traveling wind can be applied to the outdoor heat exchanger 14 when the vehicle is traveling.

When the temperature of the refrigerant flowing through the outdoor heat exchanger 14 is lower than the temperature of the outside air, the outdoor heat exchanger 14 functions as a heat absorber that causes the refrigerant to absorb the heat of the outside air. When the temperature of the refrigerant flowing through the outdoor heat exchanger 14 is higher than the temperature of the outside air, the outdoor heat exchanger 14 functions as a radiator that radiates the heat of the refrigerant to the outside air.

The second expansion valve 15 is a second decompression unit that decompresses and expands the liquid-phase refrigerant that has flowed out of the outdoor heat exchanger 14. The second expansion valve 15 is an electric variable throttle mechanism, and includes a valve body and an electric actuator. The valve body is configured to be able to change the passage opening (in other words, the throttle opening) of the refrigerant passage. The electric actuator has a stepping motor that changes the throttle opening of the valve body.

The second expansion valve 15 is composed of a variable throttle mechanism with a fully open function that fully opens the refrigerant passage when the throttle opening is fully opened. That is, the second expansion valve 15 can prevent the refrigerant from depressurizing by fully opening the refrigerant passage. The operation of the second expansion valve 15 is controlled by a control signal output from the control device 30.

The heat absorption mode and the heat radiation mode are switched by changing the throttle opening of the first expansion valve 13 and the second expansion valve 15. The endothermic mode is an operation mode in which the outdoor heat exchanger 14 causes the refrigerant to absorb heat. The heat release mode is an operation mode in which the outdoor heat exchanger 14 releases heat from the refrigerant.

The low-pressure side heat exchanger 16 is an evaporator that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant flowing out of the second expansion valve 15 and the cooling water of the low-temperature cooling water circuit 22. The gas-phase refrigerant evaporated in the low-pressure side heat exchanger 16 is sucked into the compressor 11 and compressed.

The cooling water in the low-temperature cooling water circuit 22 is a fluid as a heat medium. The cooling water in the low-temperature cooling water circuit 22 is a low-temperature heat medium. In the present embodiment, a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid is used as the cooling water of the low-temperature cooling water circuit 22.

The high-pressure side heat exchanger 12 has a heat exchange part 12a. The heat exchanging unit 12 a of the high-pressure side heat exchanger 12 exchanges heat between the refrigerant discharged from the compressor 11 and the cooling water of the high-temperature cooling water circuit 21. A modulator 12b and a supercooling unit 12c are integrated with the high pressure side heat exchanger 12. The modulator 12b of the high-pressure side heat exchanger 12 is a first refrigerant storage unit that separates the gas-liquid refrigerant flowing out of the heat exchange unit 12a of the high-pressure side heat exchanger 12 and stores excess liquid-phase refrigerant. The supercooling section 12c of the high-pressure side heat exchanger 12 exchanges heat between the liquid-phase refrigerant that has flowed out of the modulator 12b of the high-pressure-side heat exchanger 12 and the cooling water of the high-temperature cooling water circuit 21 in the endothermic mode. It is the supercooling part for the endothermic mode to supercool.

The outdoor heat exchanger 14 has a heat exchange part 14a. The outdoor heat exchanger 14 is integrated with a modulator 14b and a supercooling unit 14c. The heat exchanging unit 14a of the outdoor heat exchanger 14 exchanges heat between the refrigerant flowing out of the first expansion valve 13 and the outside air. The modulator 14b of the outdoor heat exchanger 14 is a second refrigerant storage unit that separates the gas-liquid refrigerant flowing out of the heat exchange unit 14a of the outdoor heat exchanger 14 and stores excess liquid-phase refrigerant. The subcooling section 14c of the outdoor heat exchanger 14 performs heat exchange between the liquid refrigerant flowing out of the modulator 14b of the outdoor heat exchanger 14 and the outside air in the heat dissipation mode, and supercools the liquid refrigerant so that the liquid phase refrigerant is supercooled. It is.

A supercooling bypass flow path 18 is connected to the modulator 14b of the outdoor heat exchanger 14. The supercooling bypass flow path 18 is a bypass part in which the refrigerant that has flowed through the modulator 14b of the outdoor heat exchanger 14 bypasses the supercooling part 14c and flows.

A supercooling bypass opening / closing valve 19 is disposed in the supercooling bypass flow path 18. The supercooling bypass opening / closing valve 19 is a bypass opening degree adjusting unit that adjusts the opening degree of the supercooling bypass passage 18. The supercooling bypass opening / closing valve 19 is an electromagnetic valve and is controlled by the control device 30.

In the high-temperature cooling water circuit 21, a high-pressure side heat exchanger 12, a high-temperature side pump 23, and a heater core 24 are arranged. In the low temperature cooling water circuit 22, a low pressure side heat exchanger 16, a low temperature side pump 25 and a cooler core 26 are arranged.

The high temperature side pump 23 and the low temperature side pump 25 are heat medium pumps that suck and discharge the cooling water. The high temperature side pump 23 and the low temperature side pump 25 are electric pumps. The high temperature side pump 23 is a high temperature side flow rate adjusting unit that adjusts the flow rate of the cooling water circulating in the high temperature cooling water circuit 21. The low temperature side pump 25 is a low temperature side flow rate adjusting unit that adjusts the flow rate of the cooling water circulating in the low temperature cooling water circuit 22.

The heater core 24 is a high-temperature side heat medium heat exchanger that heats the air blown into the vehicle interior by exchanging heat between the cooling water of the high-temperature coolant circuit 21 and the air blown into the vehicle interior. In the heater core 24, the cooling water radiates heat to the air blown into the vehicle interior due to the change in sensible heat. That is, in the heater core 24, even if the cooling water radiates heat to the air blown into the vehicle interior, the cooling water remains in a liquid phase and does not change phase.

The high-pressure side heat exchanger 12 and the heater core 24 heat the air blown into the vehicle interior by exchanging heat between the high-pressure refrigerant discharged from the compressor 11 and the air blown into the vehicle compartment via the cooling water. It is a high-pressure side heat exchange part. The high-pressure side heat exchanging unit heat-exchanges the high-pressure refrigerant discharged from the compressor 11 and the air blown into the passenger compartment without passing through the cooling water to heat the air blown into the passenger compartment. It may be.

The cooler core 26 is a low-temperature heat medium heat exchanger that cools the air blown into the vehicle interior by exchanging heat between the cooling water of the low-temperature coolant circuit 22 and the air blown into the vehicle interior. In the cooler core 26, the cooling water absorbs heat from the air blown into the vehicle interior due to the change in sensible heat. That is, in the cooler core 26, even if the cooling water absorbs heat from the air blown into the passenger compartment, the cooling water remains in a liquid phase and does not change phase.

The cooler core 26 and the heater core 24 are accommodated in an air conditioning casing (not shown). The air conditioning casing is an air passage forming member that forms an air passage.

The heater core 24 is disposed on the air flow downstream side of the cooler core 26 in the air passage in the air conditioning casing. The air conditioning casing is disposed in the vehicle interior space.

In the air conditioning casing, an inside / outside air switching box (not shown) and an indoor fan 27 are arranged. The inside / outside air switching box is an inside / outside air switching unit that switches between introduction of inside air and outside air into an air passage in the air conditioning casing. The indoor blower 27 sucks and blows the inside air and the outside air introduced into the air passage in the air conditioning casing through the inside / outside air switching box.

An air mix door (not shown) is arranged between the cooler core 26 and the heater core 24 in the air passage in the air conditioning casing. The air mix door adjusts the air volume ratio between the cool air that flows into the heater core 24 out of the cool air that has passed through the cooler core 26 and the cool air that bypasses the heater core 24 and flows.

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

¡The rotary shaft of the air mix door is driven by a servo motor. The operation of the servo motor is controlled by the control device 30.

The cooler core 26 has a cooling water inlet 26a, a distribution tank 26b, a heat exchange part 26c, a collecting tank 26d, and a cooling water outlet 26e.

The cooling water inlet 26a allows the cooling water flowing out from the low pressure side heat exchanger 16 to flow into the distribution tank 26b. The distribution tank 26b distributes the cooling water to the plurality of cooling water tubes of the heat exchange unit 26c. The heat exchanging part 26c has a plurality of cooling water tubes, and exchanges heat between the cooling water and the air blown into the vehicle interior. The collecting tank 26d collects the cooling water that has flowed through the plurality of cooling water tubes of the heat exchange unit 26c. The cooling water outlet 26e allows the cooling water to flow from the collecting tank 26d to the cooling water suction side of the low temperature side pump 25.

The low-pressure side heat exchanger 16 has a cooling water inlet 16a and a cooling water outlet 16b. The cooling water discharged from the low temperature side pump 25 flows into the low pressure side heat exchanger 16 through the cooling water inlet 16a. The cooling water heat-exchanged by the low-pressure side heat exchanger 16 flows out to the cooling water inlet 26a side of the cooler core 26 through the cooling water outlet 16b.

The heat exchange part 26c of the cooler core 26 is disposed at a position higher in the gravitational direction than at least one of the cooling water inlet 16a and the cooling water outlet 16b of the low-pressure side heat exchanger 16.

At least a part of the low-temperature cooling water passage 22a through which the cooling water of the low-temperature cooling water circuit 22 flows is disposed at a position lower in the gravitational direction than the heat exchange part 26c of the cooler core 26. The low-temperature cooling water flow path 22 a is a heat medium flow path portion through which cooling water flows between the low-pressure side heat exchanger 16 and the cooler core 26.

As shown in FIG. 2, the outdoor heat exchanger 14 includes a refrigerant inlet 14d, a heat exchange part distribution tank 14e, a heat exchange part collection tank 14f, a bypass outlet 14g, a supercooling part distribution tank 14h, and a supercooling part collection tank 14i. And a refrigerant outlet 14k.

The refrigerant inlet 14d is provided in the heat exchange part distribution tank 14e. The heat exchange unit distribution tank 14e distributes the refrigerant to the plurality of refrigerant tubes of the heat exchange unit 14a. The heat exchange unit collecting tank 14f collects the refrigerant that has flowed through the plurality of refrigerant tubes of the heat exchange unit 14a.

The piping which forms the supercooling bypass flow path 18 is connected to the bypass outlet 14g. The bypass outlet 14g is provided in the supercooling part distribution tank 14h. The supercooling part distribution tank 14h distributes the refrigerant to the plurality of refrigerant tubes of the supercooling part 14c. The supercooling part collection tank 14i collects the refrigerant that has flowed through the plurality of refrigerant tubes of the supercooling part 14c. The refrigerant outlet 14k is provided in the supercooling unit collecting tank 14i. A filter 14m is accommodated in the modulator 14b.

As shown by the arrows in FIG. 2, the refrigerant flowing from the refrigerant inlet 14d is the heat exchange part distribution tank 14e, the heat exchange part 14a, the heat exchange part collect tank 14f, the modulator 14b, the supercooling part distribution tank 14h, and the supercooling part 14c. After flowing in the order of the supercooling section collecting tank 14i, it flows out from the refrigerant outlet 14k.

When the supercooling bypass opening / closing valve 19 opens the supercooling bypass passage 18, the refrigerant flowing into the supercooling portion distribution tank 14h flows out from the bypass outlet 14g to the supercooling bypass passage 18.

Next, the electric control unit of the refrigeration cycle apparatus 10 will be described with reference to FIG. The control device 30 includes a known microcomputer including a CPU, a ROM, a RAM, and the like and peripheral circuits thereof. The control device 30 performs various calculations and processes based on a control program stored in the ROM. Various devices to be controlled are connected to the output side of the control device 30. The control device 30 is a control unit that controls the operation of various devices to be controlled.

The control target devices controlled by the control device 30 include the compressor 11, the first expansion valve 13, the second expansion valve 15, the outdoor blower 17, the supercooling bypass opening / closing valve 19, the high temperature side pump 23, the low temperature side pump 25, and the like. is there.

Software and hardware for controlling the electric motor of the compressor 11 in the control device 30 is a refrigerant discharge capacity control unit. Software and hardware for controlling the first expansion valve 13 in the control device 30 is a first throttle control unit. Software and hardware for controlling the second expansion valve 15 in the control device 30 is a second throttle control unit.

Software and hardware for controlling the outdoor blower 17 in the control device 30 is an outside air blowing capacity control unit. Software and hardware for controlling the supercooling bypass opening / closing valve 19 in the control device 30 is a bypass opening degree control unit.

Software and hardware for controlling the high temperature side pump 23 in the control device 30 is a high temperature side heat medium flow control unit. Software and hardware for controlling the low temperature side pump 25 in the control device 30 is a low temperature side heat medium flow control unit.

On the input side of the control device 30, various air conditioners such as an inside air temperature sensor 31, an outside air temperature sensor 32, a solar radiation amount sensor 33, an outdoor heat exchanger temperature sensor 34, a low pressure side heat exchanger temperature sensor 35, and a cooler core temperature sensor 36. A sensor group for control is connected.

The inside air temperature sensor 31 detects the passenger compartment temperature Tr. The outside air temperature sensor 32 detects the outside air temperature Tam. The solar radiation amount sensor 33 detects the solar radiation amount Ts in the passenger compartment. The outdoor heat exchanger temperature sensor 34 detects the temperature of the outdoor heat exchanger 14. For example, the outdoor heat exchanger temperature sensor 34 detects the temperature of the refrigerant flowing into the outdoor heat exchanger 14. The low-pressure side heat exchanger temperature sensor 35 detects the temperature of the cooling water flowing out from the low-pressure side heat exchanger 16.

The cooler core temperature sensor 36 detects the temperature of the cooler core 26. For example, the low-pressure side heat exchanger temperature sensor 35 detects the temperature of the cooling water flowing out from the low-pressure side heat exchanger 16. For example, the cooler core temperature sensor 36 is a fin thermistor that detects the heat exchange fin temperature of the cooler core 26. The cooler core temperature sensor 36 may be a temperature sensor that detects the temperature of the cooling water flowing into the cooler core 26.

An operation panel 39 is connected to the input side of the control device 30. The operation panel 39 is disposed in the vicinity of the instrument panel in the front part of the vehicle interior and is operated by a passenger. Various operation switches are provided on the operation panel 39. Operation signals from various operation switches are input to the control device 30.

The various operation switches on the operation panel 39 are an air conditioner switch, a temperature setting switch, and the like. The air conditioner switch sets whether or not to cool the air blown into the vehicle interior by the indoor air conditioning unit. The temperature setting switch sets a set temperature in the passenger compartment.

Next, the operation in the above configuration will be described. The control device 30 switches the air conditioning mode to any one of the heating mode, the cooling mode, the first dehumidifying heating mode, and the second dehumidifying heating mode based on the target blowing temperature TAO or the like.

The target air temperature TAO is the target temperature of the air that is blown out into the passenger compartment. The control device 30 calculates the target blowing temperature TAO based on the following mathematical formula.

TAO = Kset × Tset−Kr × Tr−Kam × Tam−Ks × Ts + C
In this equation, Tset is the vehicle interior set temperature set by the temperature setting switch of the operation panel 39, Tr is the inside air temperature detected by the inside air temperature sensor 31, Tam is the outside air temperature detected by the outside air temperature sensor 32, and Ts is This is the amount of solar radiation detected by the solar radiation amount sensor 33. Kset, Kr, Kam, Ks are control gains, and C is a correction constant.

Next, operations in the heating mode, the cooling mode, the first dehumidifying heating mode, and the second dehumidifying heating mode will be described. The heating mode and the second dehumidifying heating mode are endothermic modes in which the outdoor heat exchanger 14 absorbs heat from the refrigerant. The cooling mode and the first dehumidifying and heating mode are heat dissipation modes in which the outdoor heat exchanger 14 dissipates the refrigerant.

(Heating mode)
In the heating mode, the control device 30 brings the first expansion valve 13 into a throttled state and the second expansion valve 15 into a fully opened state. In the heating mode, the control device 30 drives the high temperature side pump 23 and stops the low temperature side pump 25.

The control device 30 determines the operating states of the various control devices connected to the control device 30 (control signals output to the various control devices) based on the target blowing temperature TAO, the detection signal of the sensor group, and the like.

The control signal output to the first expansion valve 13 is determined so that the supercooling degree of the refrigerant flowing into the first expansion valve 13 approaches a predetermined target supercooling degree. The target degree of supercooling is determined so that the coefficient of performance of the cycle (so-called COP) approaches the maximum value.

Regarding the control signal output to the servo motor of the air mix door (not shown), the air mix door fully opens the air passage of the heater core 24 so that the total flow rate of the blown air that has passed through the cooler core 26 passes through the air passage of the heater core 24. To be determined.

In the heating mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

That is, as indicated by points a1 and a2 in FIG. 4, the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 and exchanges heat with the cooling water in the high-temperature cooling water circuit 21. Dissipate heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.

As shown at points a2 and a3 in FIG. 4, the refrigerant that has flowed out of the high-pressure heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes a low-pressure refrigerant. And as shown to the point a3 and the point a4 of FIG. 4, the low pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and absorbs heat from the outside air blown from the blower fan. Evaporate.

The refrigerant that has flowed out of the outdoor heat exchanger 14 flows into the second expansion valve 15. At this time, since the second expansion valve 15 is fully opened, the refrigerant flowing out of the outdoor heat exchanger 14 flows into the low-pressure side heat exchanger 16 without being depressurized by the second expansion valve 15.

Since the low temperature side pump 25 is stopped, the cooling water of the low temperature cooling water circuit 22 does not circulate in the low pressure side heat exchanger 16. Therefore, as indicated by a point a4 in FIG. 4, the low-pressure refrigerant flowing into the low-pressure side heat exchanger 16 hardly absorbs heat from the cooling water in the low-temperature cooling water circuit 22. Then, as indicated by points a4 and a1 in FIG. 4, the refrigerant that has flowed out of the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

In the high-pressure side heat exchanger 12, the refrigerant condensed in the heat exchanging portion 12a is gas-liquid separated by the modulator 12b and the excess refrigerant is stored. The liquid-phase refrigerant that has flowed out of the modulator 12b flows through the supercooling section 12c and is supercooled.

In the heating mode, the control device 30 opens the supercooling bypass opening / closing valve 19. Thereby, the refrigerant that has flowed out of the modulator 14b of the outdoor heat exchanger 14 flows through the supercooling portion 14c and the supercooling bypass channel 18 of the outdoor heat exchanger 14, so that the refrigerant in the supercooling portion 14c of the outdoor heat exchanger 14 is reduced. Pressure loss can be reduced.

As described above, in the heating mode, the heat of the high-pressure refrigerant discharged from the compressor 11 by the high-pressure side heat exchanger 12 is radiated to the cooling water of the high-temperature cooling water circuit 21, and the high-temperature cooling water circuit 21 is heated by the heater core 24. The heat of the cooling water can be dissipated to the air blown into the vehicle interior, and the heated air blown into the vehicle interior can be blown out. Thereby, heating of a vehicle interior is realizable.

(Cooling mode)
In the cooling mode, the control device 30 sets the first expansion valve 13 to a fully open state and sets the second expansion valve 15 to a throttle state. In the cooling mode, the control device 30 stops the high temperature side pump 23 and drives the low temperature side pump 25.

The control signal output to the second expansion valve 15 is determined such that the degree of supercooling of the refrigerant flowing into the second expansion valve 15 approaches a predetermined target degree of supercooling so that the COP approaches the maximum value. Is done.

Regarding the control signal output to the servo motor of the air mix door (not shown), the air mix door closes the air passage of the heater core 24 so that the entire flow rate of the blown air that has passed through the cooler core 26 flows bypassing the heater core 24. It is determined.

In the refrigeration cycle apparatus 10 in the cooling mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

That is, the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 as indicated by a point b1 in FIG. At this time, since the high temperature side pump 23 is stopped, the cooling water of the high temperature cooling water circuit 21 does not circulate in the high pressure side heat exchanger 12. Therefore, the refrigerant that has flowed into the high-pressure side heat exchanger 12 flows out of the high-pressure side heat exchanger 12 with little heat exchange with the cooling water in the high-temperature cooling water circuit 21.

The refrigerant that has flowed out of the high-pressure side heat exchanger 12 flows into the first expansion valve 13. At this time, since the first expansion valve 13 fully opens the refrigerant passage, the refrigerant flowing out from the high pressure side heat exchanger 12 flows into the outdoor heat exchanger 14 without being depressurized by the first expansion valve 13. To do.

5, the refrigerant flowing into the outdoor heat exchanger 14 dissipates heat to the outside air blown from the blower fan in the outdoor heat exchanger 14.

As shown at points b2 and b3 in FIG. 5, the refrigerant flowing out of the outdoor heat exchanger 14 flows into the second expansion valve 15 and is decompressed and expanded at the second expansion valve 15 until it becomes a low-pressure refrigerant. . As shown at points b3 and b4 in FIG. 5, the low-pressure refrigerant decompressed by the second expansion valve 15 flows into the low-pressure side heat exchanger 16, absorbs heat from the cooling water in the low-temperature cooling water circuit 22, and evaporates. To do. Thereby, since the cooling water of the low-temperature cooling water circuit 22 is cooled, the vehicle interior blown air is cooled by the cooler core 26.

Then, as indicated by points b4 and b1 in FIG. 5, the refrigerant flowing out from the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

In the outdoor heat exchanger 14, the refrigerant condensed in the heat exchange part 14a is separated into gas and liquid by the modulator 14b and the excess refrigerant is stored. In the cooling mode, the control device 30 closes the supercooling bypass opening / closing valve 19. As a result, the liquid-phase refrigerant that has flowed out of the modulator 14b flows through the supercooling portion 14c and is supercooled.

As described above, in the cooling mode, the vehicle interior air cooled by the cooler core 26 can be blown into the vehicle interior. Thereby, cooling of a vehicle interior is realizable.

(First dehumidifying heating mode)
In the first dehumidifying and heating mode, the control device 30 places the first expansion valve 13 and the second expansion valve 15 in the throttle state. In the first dehumidifying and heating mode, the control device 30 drives both the high temperature side pump 23 and the low temperature side pump 25.

As for the control signal output to the servo motor of the air mix door (not shown), the air mix door fully opens the air passage of the heater core 24 so that the total flow rate of the air passing through the cooler core 26 passes through the air passage of the heater core 24. It is determined.

In the first dehumidifying and heating mode, the first expansion valve 13 and the second expansion valve 15 are in the throttle state. Therefore, in the first dehumidifying and heating mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

That is, as indicated by points c1 and c2 in FIG. 6, the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 and exchanges heat with the cooling water in the high-temperature cooling water circuit 21. Dissipate heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.

As shown at points c2 and c3 in FIG. 6, the refrigerant flowing out from the high pressure side heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes an intermediate pressure refrigerant. Then, as shown at points c3 and c4 in FIG. 6, the intermediate pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and dissipates heat to the outside air blown from the outdoor blower. .

As shown at points c4 and c5 in FIG. 6, the refrigerant flowing out of the outdoor heat exchanger 14 flows into the second expansion valve 15 and is decompressed and expanded until it becomes a low-pressure refrigerant at the second expansion valve 15. . As shown at points c5 and c6 in FIG. 6, the low-pressure refrigerant decompressed by the second expansion valve 15 flows into the low-pressure side heat exchanger 16, absorbs heat from the cooling water in the low-temperature cooling water circuit 22, and evaporates. To do. Thereby, the cooling water of the low-temperature cooling water circuit 22 is cooled. Then, as indicated by points c6 and c1 in FIG. 6, the refrigerant flowing out from the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

As described above, in the first dehumidifying and heating mode, the vehicle interior blown air cooled and dehumidified by the cooler core 26 can be heated by the heater core 24 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

At this time, in the first dehumidifying and heating mode, since the first expansion valve 13 is in the throttle state, the temperature of the refrigerant flowing into the outdoor heat exchanger 14 can be lowered compared to the cooling mode. Therefore, the temperature difference between the refrigerant temperature and the outside air temperature in the outdoor heat exchanger 14 can be reduced, and the heat radiation amount of the refrigerant in the outdoor heat exchanger 14 can be reduced.

As a result, the heat release amount of the refrigerant in the high-pressure side heat exchanger 12 can be increased without increasing the refrigerant circulation flow rate that circulates the cycle in the cooling mode, and the blowout blown from the heater core 24 in the cooling mode. The temperature of the air can be raised.

In the outdoor heat exchanger 14, the refrigerant condensed in the heat exchange part 14a is separated into gas and liquid by the modulator 14b and the excess refrigerant is stored. In the heating mode, the control device 30 closes the supercooling bypass opening / closing valve 19. Thereby, the liquid-phase refrigerant | coolant which flowed out from the modulator 14b of the outdoor heat exchanger 14 flows through the supercooling part 14c, and is supercooled.

(Second dehumidifying heating mode)
In the second dehumidifying and heating mode, the control device 30 places the first expansion valve 13 and the second expansion valve 15 in the throttle state. In the second dehumidifying and heating mode, the control device 30 drives both the high temperature side pump 23 and the low temperature side pump 25.

In the second dehumidifying and heating mode, the throttle opening of the first expansion valve 13 is set to a throttled state that is smaller than that in the first dehumidifying and heating mode, and the throttle opening of the second expansion valve 15 is set to be smaller than that in the first dehumidifying and heating mode. Set to an increased aperture state. Accordingly, in the second dehumidifying heating mode, the state of the refrigerant circulating in the cycle changes as shown in the Mollier diagram of FIG.

That is, as indicated by points d1 and d2 in FIG. 7, the high-pressure refrigerant discharged from the compressor 11 flows into the high-pressure side heat exchanger 12 and exchanges heat with the cooling water in the high-temperature cooling water circuit 21. Dissipate heat. Thereby, the cooling water of the high temperature cooling water circuit 21 is heated.

As shown at points d2 and d3 in FIG. 7, the refrigerant that has flowed out of the high-pressure side heat exchanger 12 flows into the first expansion valve 13 and is depressurized until it becomes an intermediate-pressure refrigerant having a temperature lower than the outside air temperature. . As shown at points d3 and d4 in FIG. 7, the intermediate-pressure refrigerant decompressed by the first expansion valve 13 flows into the outdoor heat exchanger 14 and absorbs heat from the outside air blown from the outdoor blower. .

As indicated by points d4 and d5 in FIG. 7, the refrigerant that has flowed out of the outdoor heat exchanger 14 flows into the second expansion valve 15 via the third refrigerant passage 18, and then enters the second expansion valve 15. It is expanded under reduced pressure until it becomes a low-pressure refrigerant. As shown at points d5 and d6 in FIG. 7, the low-pressure refrigerant decompressed by the second expansion valve 15 flows into the low-pressure side heat exchanger 16 and absorbs heat from the vehicle interior blown air blown from the blower 32. Evaporate. As a result, the air blown into the passenger compartment is cooled by the cooler core 26. Then, as indicated by points d6 and d1 in FIG. 7, the refrigerant flowing out from the low-pressure side heat exchanger 16 flows to the suction side of the compressor 11 and is compressed again by the compressor 11.

As described above, in the second dehumidifying and heating mode, similarly to the first dehumidifying and heating mode, the vehicle interior air cooled and dehumidified by the cooler core 26 can be heated by the heater core 24 and blown out into the vehicle interior. Thereby, dehumidification heating of a vehicle interior is realizable.

At this time, in the second dehumidifying heating mode, the outdoor heat exchanger 14 functions as a heat absorber (in other words, an evaporator) by reducing the throttle opening of the first expansion valve 13, so the first dehumidifying temperature The temperature blown out from the heater core 24 can be increased as compared with the heating mode.

As a result, the suction refrigerant density of the compressor 11 can be increased with respect to the first dehumidifying heating mode, and the high pressure side heat exchange can be performed without increasing the rotation speed (in other words, refrigerant discharge capacity) of the compressor 11. The amount of heat released from the refrigerant in the vessel 12 can be increased, and the temperature of the blown air blown from the heater core 24 can be increased as compared with the first dehumidifying and heating mode.

In the heating mode, the control device 30 opens the supercooling bypass opening / closing valve 19. Thereby, since the refrigerant | coolant which flowed out from the modulator 14b of the outdoor heat exchanger 14 flows through the supercooling part 14c and the supercooling bypass flow path 18, the pressure loss of the refrigerant | coolant in the supercooling part 14c can be reduced.

In the vehicle air conditioner 1 of the present embodiment described above, appropriate cooling, heating, and dehumidifying heating in the passenger compartment are achieved by changing the throttle opening of the first expansion valve 13 and the second expansion valve 15 as described above. Thus, comfortable air conditioning in the passenger compartment can be realized.

In the present embodiment, the low-pressure side heat exchanger 16 is arranged in series with the outdoor heat exchanger 14 in the refrigerant flow, and the low-pressure refrigerant is decompressed by at least one of the first expansion valve 13 and the second expansion valve 15. The heat medium is cooled by exchanging heat with the cooling water. The cooler core 26 cools the air by exchanging heat between the cooling water cooled by the low-pressure side heat exchanger 16 and the air blown into the vehicle interior.

According to this, since the outdoor heat exchanger 14 and the low pressure side heat exchanger 16 are arranged in series with each other in the refrigerant flow, the refrigerant pressure and the refrigerant temperature in the low pressure side heat exchanger 16 are low. However, the heat exchange performance of the cooler core 26 can be controlled by adjusting the flow rate of the cooling water flowing through the cooler core 26, and as a result, the occurrence of frost in the cooler core 26 can be suppressed.

As a result, since the refrigerant pressure in the outdoor heat exchanger 14 can be lowered, the heat absorption amount can be kept large, and a desired blowing temperature can be obtained.

Further, since the cooling water is interposed between the low-pressure side heat exchanger 16 and the cooler core 26, the temperature of the cooling water flowing into the cooler core 26 is lower than the temperature of the air cooled by the cooler core 26. The temperature of the refrigerant flowing into the low pressure side heat exchanger 16 is lower than the temperature of the cooling water flowing into the cooler core 26.

Therefore, compared with the configuration in which the refrigerant and air are directly heat-exchanged by the indoor evaporator as in the conventional technique of Patent Document 1, the temperature of the refrigerant in the low-pressure side heat exchanger 16 can be lowered, and as a result, the low-pressure side heat The refrigerant pressure in the exchanger 16 can also be lowered.

Further, in the present embodiment, the heat absorption mode and the heat radiation mode are switched by the control unit 30 adjusting the pressure reduction amount of the first expansion valve 13 and the second expansion valve 15. The heat absorption mode is an operation mode in which the outdoor heat exchanger 14 absorbs heat from the refrigerant (that is, the heating mode and the second dehumidifying heating mode). The heat release mode is an operation mode in which the outdoor heat exchanger 14 releases heat from the refrigerant (that is, the cooling mode and the first dehumidifying heating mode). Thereby, the refrigerating-cycle apparatus which can switch heat absorption mode and heat radiation mode is realizable by simple structure.

In this embodiment, the modulator 12b on the high-pressure side heat exchanger 12 side separates the gas-liquid of the refrigerant heat-exchanged by the high-pressure side heat exchanger 12 in the endothermic mode and stores the refrigerant. The modulator 14b on the outdoor heat exchanger 14 side separates the gas-liquid of the refrigerant heat-exchanged by the outdoor heat exchanger 14 in the heat dissipation mode and stores the refrigerant.

Specifically, the modulator 12b on the high pressure side heat exchanger 12 side is disposed on the refrigerant flow downstream side of the high pressure side heat exchanger 12 and on the refrigerant flow upstream side of the first expansion valve 13. The refrigerant is stored by separating the gas-liquid of the heat-exchanged refrigerant. The modulator 14b on the outdoor heat exchanger 14 side is disposed on the downstream side of the refrigerant flow of the outdoor heat exchanger 14 and on the upstream side of the refrigerant flow of the second expansion valve 15, and is a gas-liquid refrigerant that has undergone heat exchange in the outdoor heat exchanger 14. To store refrigerant.

According to this, it is possible to have a refrigerant reservoir on the cycle high pressure side in both the endothermic mode and the heat release mode. In other words, the refrigeration cycle can be converted into a receiver cycle in both the heat absorption mode and the heat dissipation mode.

Therefore, compared with an accumulator cycle having a refrigerant reservoir on the low pressure side of the cycle, the viscosity of the refrigerant and the refrigeration oil in the refrigerant reservoir is reduced, so that the pressure loss of the refrigerant can be reduced and the refrigeration oil can be easily discharged. Cycle performance can be improved. Further, since the refrigerating machine oil can be easily discharged, the amount of refrigerating machine oil enclosed can be reduced, and the refrigerant storage section can be downsized.

In addition, the refrigerant reservoir can be moved automatically in the endothermic mode and the heat release mode, and in both the endothermic mode and the heat release mode, the high pressure side enthalpy can be reduced to the liquid saturation line, so optimal control is possible. It becomes possible.

In the present embodiment, the control unit 30 controls the operation of the low temperature side pump 25 to control the low pressure side heat exchanger when the temperature of the cooling water flowing out from the low pressure side heat exchanger 16 is 0 ° C. or less in the endothermic mode. The flow rate of the cooling water in at least one of 16 and the cooler core 26 is adjusted.

For example, the control unit 30 controls the operation of the low temperature side pump 25 to control the low pressure side heat exchanger 16 and the cooler core when the temperature of the cooling water flowing out from the low pressure side heat exchanger 16 is 0 ° C. or less in the endothermic mode. The flow rate of the cooling water in both of them is adjusted.

Specifically, the control unit 30 causes the low-temperature side pump 25 to decrease the flow rate of the cooling water in at least one of the low-pressure side heat exchanger 16 and the cooler core 26 as the refrigerant pressure in the outdoor heat exchanger 14 decreases. Control the operation of

According to this, even if the refrigerant pressure / refrigerant temperature in the low pressure side heat exchanger 16 is low, the heat exchange performance of the cooler core 26 can be controlled by adjusting the flow rate of the cooling water flowing through the cooler core 26, As a result, generation | occurrence | production of frost with the cooler core 26 can be suppressed.

Furthermore, by adjusting the flow rate of the cooling water flowing through the low pressure side heat exchanger 16, the temperature difference between the refrigerant and the cooling water can be increased. By adjusting the flow rate of the cooling water flowing through the cooler core 26, the temperature difference between the air and the cooling water can be increased.

As a result, since the temperature difference between the air and the cooling water can be increased, the refrigerant temperature (in other words, the refrigerant pressure) in the outdoor heat exchanger 14 is lowered in order to increase the heat absorption amount in the outdoor heat exchanger 14. Even so, it is possible to suppress the temperature of the cooling water flowing into the cooler core 26 from becoming 0 ° C. or lower, and thus it is possible to suppress the occurrence of frost in the cooler core 26.

The control unit 30 may adjust the flow rate of the cooling water by controlling the rotational speed of the low temperature side pump 25. The control part 30 may adjust the flow volume (namely, time average flow volume) of cooling water by driving the low temperature side pump 25 intermittently.

A flow rate adjustment valve may be arranged in the low-temperature cooling water circuit 22. Thereby, the control part 30 can adjust the flow volume of a cooling water by adjusting the opening degree of a flow regulating valve.

In the present embodiment, the supercooling bypass opening / closing valve 19 reduces the opening degree of the supercooling bypass passage 18 in the heat dissipation mode compared to that in the heat absorption mode.

According to this, in the heat dissipation mode, the cooling water flowing through the supercooling bypass channel 18 is less than in the heat absorption mode, and the cooling water flowing through the supercooling portion 14c on the outdoor heat exchanger 14 side is increased. Therefore, the refrigerant can be reliably supercooled by the supercooling bypass channel 18 in the heat dissipation mode in which the refrigerant needs to be supercooled by the supercooling bypass channel 18.

In the heat absorption mode, the amount of cooling water flowing through the supercooling bypass channel 18 increases, and the amount of cooling water flowing through the subcooling portion 14c on the outdoor heat exchanger 14 side decreases. Therefore, it is possible to suppress an increase in pressure loss in the supercooling portion 14c on the outdoor heat exchanger 14 side in the heat absorption mode in which it is not necessary to supercool the refrigerant in the supercooling bypass channel 18.

In the present embodiment, the supercooling bypass channel 18 extends from the supercooling part distribution tank part 14h of the outdoor heat exchanger 14 to the downstream side of the refrigerant flow of the supercooling part 14c on the outdoor heat exchanger 14 side.

According to this, the refrigerant that has passed through the modulator 14b on the outdoor heat exchanger 14 side flows into the supercooling bypass channel 18 in both the heat absorption mode and the heat dissipation mode. Therefore, a conventional modulator can be used as the modulator 14b on the outdoor heat exchanger 14 side without changing the design. For example, it is not necessary to change the position of the filter 14m inside the modulator 14b with respect to the conventional modulator.

As described above, since the high temperature side pump 23 is stopped in the cooling mode, the cooling water does not flow through the high pressure side heat exchanger 12. At this time, if the temperature of the refrigerant flowing through the high-pressure side heat exchanger 12 becomes high and the cooling water temperature in the high-pressure side heat exchanger 12 becomes high, the cooling water may boil inside the high-pressure side heat exchanger 12. .

Therefore, in the present embodiment, the control unit 30 stops the high temperature side pump 23 during the cooling mode, and when the temperature of the high temperature side cooling water in the high pressure side heat exchanger 12 becomes equal to or higher than the predetermined temperature during the cooling mode, The operation of the high temperature side pump 23 is controlled so that the flow rate of the high temperature side cooling water flowing through the heat exchanger 12 increases. Thereby, it can suppress that a cooling water boils inside the high voltage | pressure side heat exchanger 12 at the time of air_conditioning | cooling mode.

In the present embodiment, the control unit 30 controls the operation of the low temperature side pump 25 and adjusts the flow rate of the cooling water in the low pressure side heat exchanger 16, whereby the refrigerant heat exchanged by the low pressure side heat exchanger 16 is adjusted. Control the degree of superheat. According to this, it is very easy to control the degree of superheat.

When the cooling water pump 25 is stopped and the cooling water is not circulated between the low pressure side heat exchanger 16 and the cooler core 26, when the blower 27 is activated and air is blown to the cooler core 26, The temperature of the cooling water becomes higher than the temperature of the cooling water in the low-pressure side heat exchanger 16. When the cooling water moves by convection due to the temperature difference of the cooling water and the low-temperature cooling water in the low-pressure side heat exchanger 16 and the high-temperature cooling water in the cooler core 26 are interchanged, frost is generated in the cooler core 26 or the low-pressure side heat exchanger. The amount of heat absorbed by the refrigerant at 16 will decrease.

Therefore, in the present embodiment, the heat exchanging portion 26c of the cooler core 26 is disposed at a position higher in the gravitational direction than the cooling water inlet 16a and the cooling water outlet 16b of the low pressure side heat exchanger 16, so that the low pressure side heat exchange is performed. The low-temperature cooling water in the cooler 16 and the high-temperature cooling water in the cooler core 26 can be suppressed from being exchanged by convection, and as a result, frost formation occurs in the cooler core 26 or the heat absorption amount of the refrigerant in the low-pressure side heat exchanger 16 is reduced. Can be suppressed.

For the same reason, even if at least a part of the low-temperature cooling water flow path 22a forming the low-temperature cooling water circuit 22 is disposed at a position lower in the gravitational direction than the heat exchanging portion 26c of the cooler core 26, frost occurs in the cooler core 26. Or the amount of heat absorbed by the refrigerant in the low pressure side heat exchanger 16 can be reduced.

(Second Embodiment)
As shown in FIGS. 8 and 9, the refrigeration cycle apparatus 10 of the present embodiment includes a heat supply device 40. The heat supply device 40 is a device that supplies heat to the cooling water. Cooling water flows through the heat supply device 40. The heat supply device 40 is a heat generating device, a ventilation heat recovery heat exchanger, or the like.

Heat generating devices are engines, electric motors for traveling, batteries, inverters, DC-DC converters, turbochargers, intercoolers, EGR coolers, CVT coolers, and the like.

換気 Ventilation heat recovery heat exchanger is a heat exchanger that recovers the heat discarded during ventilation. The ventilation heat recovery heat exchanger is a heat exchanger that exchanges heat between air discharged from the passenger compartment to the outside of the passenger compartment for cooling and cooling water.

In the first embodiment shown in FIG. 8, the heat supply device 40 is disposed in the low-temperature cooling water circuit 22. In the second embodiment shown in FIG. 9, the heat supply device 40 is arranged in the high temperature cooling water circuit 21.

As shown in FIG. 10, a shutter 41 is disposed in the vicinity of the outdoor heat exchanger 14. The shutter 41 is driven to open and close by an electric actuator (not shown). The operation of the electric actuator is controlled by the control device 30.

The shutter 41 adjusts the opening degree of the passage of the outside air flowing through the outdoor heat exchanger 14. That is, the shutter 41 is a heat exchanger flow rate adjusting unit that adjusts the flow rate of the outside air flowing through the outdoor heat exchanger 14. For example, by reducing the opening degree of the shutter 41, the flow rate of the outside air flowing through the outdoor heat exchanger 14 can be reduced.

As shown in FIG. 11, the refrigeration cycle apparatus 10 of the present embodiment includes a heat exchanger bypass channel 42 and a heat exchanger bypass opening / closing valve 43. The heat exchanger bypass channel 42 is a heat exchanger bypass portion in which the refrigerant flows by bypassing the first expansion valve 13 and the outdoor heat exchanger 14. In the example of FIG. 11, the heat exchanger bypass passage 42 joins the supercooling bypass passage 18.

The heat exchanger bypass opening / closing valve 43 is a heat exchanger bypass opening degree adjusting unit that adjusts the opening degree of the heat exchanger bypass passage 42. That is, the heat exchanger bypass opening / closing valve 43 is a heat exchanger flow rate adjusting unit that adjusts the flow rate of the outside air flowing through the outdoor heat exchanger 14. The heat exchanger bypass opening / closing valve 43 is an electromagnetic valve and is controlled by the control device 30. For example, the flow rate of the refrigerant flowing into the outdoor heat exchanger 14 can be reduced by increasing the opening degree of the heat exchanger bypass opening / closing valve 43.

In this embodiment, the cycle performance can be improved by the heat supply device 40 supplying heat to the cooling water. In particular, the frost of the outdoor heat exchanger 14 can be suppressed or the heating performance can be improved by introducing the heat supplied from the heat supply device 40 into the low-pressure side heat exchanger 16 in the heating mode. .

If the amount of heat introduced from the heat supply device 40 to the low pressure side heat exchanger 16 is too large in the heating mode, if the temperature of the refrigerant flowing into the outdoor heat exchanger 14 becomes too high, the low pressure of the refrigeration cycle increases, There is a possibility that the temperature of the refrigerant flowing into the outdoor heat exchanger 14 becomes equal to or higher than the outside air temperature, and the refrigerant radiates heat in the outdoor heat exchanger 14 to waste heat.

Therefore, in the present embodiment, when the temperature difference between the temperature of the refrigerant flowing into the outdoor heat exchanger 14 and the outside air becomes equal to or less than a predetermined value, the control unit 30 controls the outside air and the refrigerant flowing into the outdoor heat exchanger 14. The operation of at least one of the outdoor blower 17, the shutter 41, and the heat exchanger bypass opening / closing valve 43 is controlled so that at least one of the flow rates decreases. Thereby, it can suppress that a refrigerant | coolant thermally radiates with the outdoor heat exchanger 14. FIG.

For example, when the temperature difference between the refrigerant flowing into the outdoor heat exchanger 14 and the outside air becomes a predetermined value or less, the control unit 30 reduces the rotation speed of the outdoor heat exchanger 14 to reduce the outdoor heat exchange. What is necessary is just to reduce the flow volume of the external air which flows into the vessel 14.

For example, when the temperature difference between the refrigerant flowing into the outdoor heat exchanger 14 and the outside air becomes a predetermined value or less, the control unit 30 causes the outside air blowing direction to the outdoor heat exchanger 14 to be reversed. The operation of the outside air blower 17 may be controlled.

The air blowing direction of the outside air to the outdoor heat exchanger 14 is reversed, so that high temperature outside air (that is, outside air warmed by the engine) in the engine room of the vehicle can flow into the outdoor heat exchanger 14. Therefore, it is possible to reliably prevent the refrigerant from radiating heat in the outdoor heat exchanger 14 and wasting heat.

For example, when the temperature difference between the refrigerant flowing into the outdoor heat exchanger 14 and the outside air becomes equal to or less than a predetermined value, the control unit 30 reduces the opening of the passage of the outside air flowing through the outdoor heat exchanger 14. By controlling the operation of the shutter 41, the flow rate of the outside air flowing into the outdoor heat exchanger 14 may be reduced.

For example, when the temperature difference between the refrigerant flowing into the outdoor heat exchanger 14 and the outside air becomes equal to or less than a predetermined value, the control unit 30 increases the opening of the heat exchanger bypass on / off valve 43 to increase the outdoor temperature. The flow rate of the refrigerant flowing into the heat exchanger 14 may be reduced.

(Third embodiment)
As shown in FIG. 12, the refrigeration cycle apparatus 10 may include an internal heat exchanger 45. The internal heat exchanger 45 has a high-pressure side refrigerant passage 45a and a low-pressure side refrigerant passage 45b.

The internal heat exchanger 45 is a heat exchanger that exchanges heat between the high-pressure refrigerant that flows through the high-pressure refrigerant passage 45a and the low-pressure refrigerant that flows through the low-pressure refrigerant passage 45b.

The high-pressure side refrigerant passage 45 a is arranged on the downstream side of the refrigerant flow of the outdoor heat exchanger 14 and on the upstream side of the refrigerant flow of the second expansion valve 15. The low-pressure side refrigerant passage 45 b is disposed on the refrigerant flow downstream side of the low-pressure side heat exchanger 16 and on the refrigerant suction side of the compressor 11.

(Fourth embodiment)
In the present embodiment, as shown in FIG. 13, an ejector 46 is disposed instead of the second expansion valve 15.

The ejector 46 is a decompression unit that decompresses the refrigerant, and also a refrigerant circulation unit for fluid transportation (in other words, a momentum transportation type) that circulates the refrigerant by suction action (in other words, entrainment action) of the refrigerant flow ejected at high speed. It is also a pump).

The ejector 46 includes a nozzle portion 46a and a refrigerant suction port 46b. The nozzle part 46 a expands the refrigerant under reduced pressure by reducing the passage area of the refrigerant that has passed through the outdoor heat exchanger 14. The refrigerant suction port 46b is disposed in the same space as the refrigerant outlet of the nozzle portion 46a, and sucks the gas phase refrigerant from the low-pressure side heat exchanger 16.

The diffuser part 46d is arrange | positioned in the refrigerant | coolant flow downstream site | part of the nozzle part 46a and the refrigerant | coolant suction port 46b among the ejectors 46. FIG. The diffuser portion 46d is a pressure increasing portion that increases the pressure by mixing the high-speed refrigerant flow from the nozzle portion 46a and the suction refrigerant in the refrigerant suction port 46b.

The diffuser portion 46d is formed in a shape that gradually increases the refrigerant passage area, and acts to decelerate the refrigerant flow to increase the refrigerant pressure, that is, to convert the velocity energy of the refrigerant into pressure energy.

The low pressure side heat exchanger 16 is connected to the outlet portion (the tip portion of the diffuser portion 46d) of the ejector 46.

One end of an ejector bypass passage 47 is connected to the refrigerant inlet side of the nozzle portion 46a via a three-way valve 48. The ejector bypass channel 47 is a channel through which the refrigerant bypasses the ejector 46. The other end of the ejector bypass channel 47 is connected to the refrigerant inlet side of the low pressure side heat exchanger 16. The three-way valve 48 switches between a state in which the refrigerant flows out to the ejector 46 side and a state in which the refrigerant flows out to the ejector bypass channel 47 side. The operation of the three-way valve 48 is controlled by the control device 30.

(Fifth embodiment)
In the above embodiment, the high-pressure side heat exchanger 12 exchanges heat between the high-pressure side refrigerant discharged from the compressor 11 and the cooling water of the high-temperature cooling water circuit 21, but the first embodiment of this embodiment shown in FIG. As in the example and the second example of this embodiment shown in FIG. 15, the high pressure side heat exchanger 12 exchanges heat between the high pressure side refrigerant discharged from the compressor 11 and the air blown into the vehicle interior. May be. 14 and 15 is housed in an air conditioning casing (not shown) instead of the heater core 24 of the above embodiment.

In the above embodiment, the low-pressure heat exchanger 16 exchanges heat between the low-pressure refrigerant that has flowed out of the second expansion valve 15 and the cooling water of the low-temperature cooling water circuit 22, but the second embodiment of the present embodiment shown in FIG. As in the example and the third example of the present embodiment shown in FIG. 16, the low-pressure side heat exchanger 16 exchanges heat between the low-pressure refrigerant that has flowed out of the second expansion valve 15 and the air that is blown into the vehicle interior. May be. The low pressure side heat exchanger 16 shown in FIGS. 15 and 16 is accommodated in an air conditioning casing (not shown) instead of the cooler core 26 of the above embodiment.

(Sixth embodiment)
In the refrigeration cycle apparatus 10 of the above-described embodiment, a receiver

cycle including modulators

12b and 14b on the high-pressure side is configured, but the first example of this embodiment shown in FIG. 17 and the present embodiment shown in FIG. As in the second embodiment, an accumulator cycle including the accumulator 50 on the low pressure side may be configured.

The accumulator 50 separates the gas-liquid refrigerant flowing out from the low-pressure side heat exchanger 16, stores the separated liquid-phase refrigerant therein, and causes the separated gas-phase refrigerant to flow out to the suction port side of the compressor 11. It is a refrigerant | coolant storage part.

The high-pressure side heat exchanger 12 shown in FIG. 17 exchanges heat between the high-pressure side refrigerant discharged from the compressor 11 and the cooling water of the high-temperature cooling water circuit 21. The high-pressure side heat exchanger 12 shown in FIG. 18 exchanges heat between the high-pressure side refrigerant discharged from the compressor 11 and the air blown into the vehicle interior.

(Seventh embodiment)
In the present embodiment, as shown in FIG. 19, an in-vehicle device 55 is disposed in the low temperature cooling water circuit 22. The in-vehicle device 55 is arranged in parallel with the cooler core 26 in the flow of the cooling water in the low-temperature cooling water circuit 22.

The in-vehicle device 55 is a device that is mounted on a vehicle and that generates heat when activated. For example, the in-vehicle device 55 is a battery heat exchanger, an inverter, a transaxle, a motor generator, or the like.

¡Batteries and transaxles deteriorate in performance when they are overcooled, so some temperature adjustment is required.

A vehicle-mounted device temperature sensor (not shown) is connected to the input side of the control device 30. The in-vehicle device temperature sensor is an in-vehicle temperature detection unit that detects the temperature of the in-vehicle device 55. The in-vehicle device temperature sensor may be a sensor that detects the temperature of the cooling water flowing into the in-vehicle device 55.

The low-temperature cooling water circuit 22 has a branch portion 22b and a junction portion 22c. In the branch part 22b, the flow of the cooling water flowing out from the low pressure side heat exchanger 16 is branched into the cooler core 26 side and the in-vehicle device 55 side. In the junction part 22c, the flow of the cooling water that has flowed out of the cooler core 26 and the flow of the cooling water that has flowed out of the in-vehicle device 55 merge.

In the low-temperature cooling water circuit 22, a first flow control valve 56 is disposed between the branch portion 22 b and the cooler core 26. In the low-temperature cooling water circuit 22, a second flow regulating valve 57 is disposed between the branch portion 22 b and the in-vehicle device 55.

The first flow control valve 56 and the second flow control valve 57 are valves that adjust the flow rate of the cooling water by changing the opening degree of the cooling water flow path. The first flow regulating valve 56 and the second flow regulating valve 57 are valves that can fully open and fully close the cooling water flow path. The first flow adjustment valve 56 and the second flow adjustment valve 57 are electromagnetic valves controlled by the control device 30.

The first flow control valve 56 and the second flow control valve 57 are flow rate adjusting units that adjust the flow rate of the cooling water flowing through the cooler core 26 and the flow rate of the cooling water flowing through the in-vehicle device 55.

In the present embodiment, the control device 30 controls the first flow regulating valve 56 and the second flow regulating valve 57 so that the temperature adjustment of the cooler core 26 is prioritized over the temperature adjustment of the in-vehicle device 55.

As described in the above embodiment, in the first dehumidifying and heating mode and the second dehumidifying and heating mode, the cooling water cooled by the low pressure side heat exchanger 16 flows into the cooler core 26 and the air blown into the vehicle interior is The dehumidification is performed by being cooled by the cooler core 26, the cooling water heated by the high pressure side heat exchanger 12 flows into the heater core 24, and the air cooled by the cooler core 26 is heated by the heater core 24. Air-conditioned air having a target blowing temperature is generated.

At this time, the target blowing temperature of the heater core 24 (that is, the target blowing temperature TAO) varies depending on the inside air temperature and the outside air temperature.

FIG. 20 is a graph illustrating the relationship between the outside air temperature, the target outlet temperature of the heater core 24, and the target outlet temperature of the cooler core 26.

When the outdoor temperature is low (for example, 0 ° C. to 10 ° C.), by switching to the above-described second dehumidifying heating mode, the outdoor heat exchanger 14, the cooler core 26, and the vehicle-mounted device 55 absorb heat to generate a desired heater core blowing temperature. .

At this time, the control device 30 performs cooler core frost prevention control (in other words, frost suppression control). The cooler core frost prevention control is a control in which the flow rate of the cooling water flowing through the cooler core 26 is adjusted by the first flow control valve 56 so that frost is not generated in the cooler core 26.

Specifically, the control device 30 determines that the surface temperature of the cooler core 26 or the temperature of the cooling water flowing into the cooler core 26 is equal to or lower than the frost limit temperature (for example, 0 ° C.), the surface temperature of the cooler core 26, When the temperature of the cooling water flowing into the cooler core 26 is predicted to be equal to or lower than the frost limit temperature (for example, 0 ° C.), the flow rate of the cooling water flowing into the cooler core 26 with the opening of the first flow regulating valve 56 reduced or fully closed. Is reduced or reduced to zero. Thereby, since the surface temperature of the cooler core 26 rises, generation | occurrence | production of frost in the cooler core 26 can be suppressed.

At this time, although the heat absorption amount of the cooler core 26 is reduced, the heat amount for heating can be obtained by absorbing heat from the in-vehicle device 55. Therefore, the amount of heat necessary for heating can be ensured without increasing the rotational speed of the compressor 11 as much as possible.

Further, the control device 30 adjusts the flow rate of the cooling water flowing through the in-vehicle device 55 by the second flow control valve 57 so that the in-vehicle device 55 is not overcooled.

Specifically, the control device 30 determines that the temperature of the in-vehicle device 55 or the temperature of the cooling water flowing into the in-vehicle device 55 has become lower than the lower limit temperature, or the temperature of the in-vehicle device 55 or the in-vehicle device 55 When it is predicted that the temperature of the cooling water to be reduced will be lower than the lower limit temperature, the opening degree of the second flow control valve 57 is reduced or fully closed to reduce or reduce the flow rate of the cooling water flowing to the in-vehicle device 55. Thereby, since the temperature of the vehicle equipment 55 rises, it can suppress that the vehicle equipment 55 becomes overcooling.

When the opening degree of both the first flow regulating valve 56 and the second flow regulating valve 57 is reduced or fully closed, the control device 30 reduces or reduces the flow rate of the cooling water discharged from the low temperature side pump 25. To.

The low temperature side pump 25 is a flow rate adjusting unit that adjusts the flow rate of the cooling water flowing through the cooler core 26 and the flow rate of the cooling water flowing through the in-vehicle device 55.

In the present embodiment, the control device 30 performs the frost suppression control on the first flow control valve 56, and when performing the frost suppression control, the second flow control valve 57 so that the cooling water flows to the in-vehicle device 55. To control. The frost suppression control is a control for suppressing the frost of the cooler core 26 by controlling the first flow regulating valve 56 and the low temperature side pump 25 so that the flow rate of the cooling water flowing through the cooler core 26 is suppressed.

According to this, the occurrence of frost in the cooler core 26 can be suppressed by performing the frost suppression control. When the frost suppression control is performed, the cooling water flows through the in-vehicle device 55, so that heat can be absorbed from the in-vehicle device 55. Therefore, even if the heat absorption amount from the cooler core 26 is reduced by performing the frost suppression control, the heat absorption amount from the in-vehicle device 55 can be compensated, so that the temperature of the air blown into the vehicle interior can be secured.

Moreover, compared with the case where heat is not absorbed from the in-vehicle device 55, the power of the compressor 11 consumed to secure the temperature of the air blown into the vehicle interior can be reduced.

In the present embodiment, when the frost suppression control is performed, the control device 30 controls the flow rate of the cooling water flowing through the in-vehicle device 55 so that the temperature of the in-vehicle device 55 does not fall below the lower limit temperature. Adjustment is performed by the side pump 25. Thereby, it can suppress that the vehicle equipment 55 is overcooled.

Specifically, when the control device 30 performs the frost suppression control, the temperature of the in-vehicle device 55 is lower than the lower limit temperature, and the temperature of the in-vehicle device 55 is higher than the lower limit temperature. Thus, the second flow control valve 57 and the low temperature side pump 25 are controlled so that the flow rate of the cooling water flowing to the in-vehicle device 55 is reduced. Thereby, it can suppress that the vehicle equipment 55 is overcooled.

(Eighth embodiment)
In the seventh embodiment, the temperatures of the cooler core 26 and the in-vehicle device 55 are adjusted by the first flow regulating valve 56 and the second flow regulating valve 57. In the present embodiment, as shown in FIG. The temperature of the cooler core 26 and the vehicle equipment 55 is adjusted.

The switching valve 58 is arranged in a branch portion of the low-temperature cooling water circuit 22 where the flow of the cooling water flowing out from the low-pressure side heat exchanger 16 is branched into the cooler core 26 side and the in-vehicle device 55 side.

The switching valve 58 can open and close the cooling water passage on the cooler core 26 side and the cooling water passage on the in-vehicle device 55 side independently. The switching valve 58 can adjust independently the opening degree of the cooling water flow path on the cooler core 26 side and the opening degree of the cooling water flow path on the in-vehicle device 55 side. The switching valve 58 is an electromagnetic valve controlled by the control device 30.

The switching valve 58 is a flow rate adjusting unit that adjusts the flow rate of the cooling water flowing through the cooler core 26 and the flow rate of the cooling water flowing through the in-vehicle device 55.

In the present embodiment, the control device 30 controls the switching valve 58 so that the temperature adjustment of the cooler core 26 is prioritized over the temperature adjustment of the in-vehicle device 55.

Similarly to the seventh embodiment, in the first dehumidifying and heating mode and the second dehumidifying and heating mode, the cooling water cooled by the low-pressure side heat exchanger 16 flows into the cooler core 26 and the air blown into the vehicle interior is The dehumidification is performed by being cooled by the cooler core 26, the cooling water heated by the high pressure side heat exchanger 12 flows into the heater core 24, and the air cooled by the cooler core 26 is heated by the heater core 24. Air-conditioned air having a target blowing temperature is generated.

At this time, similarly to the seventh embodiment, the target air temperature of the heater core 24 (that is, the target air temperature TAO) varies depending on the inside air temperature and the outside air temperature.

At a low outside air temperature (for example, 0 ° C. to 10 ° C.), by switching to the above-described second dehumidifying heating mode, the outdoor heat exchanger 14, the cooler core 26, and the in-vehicle device 55 perform heat absorption to obtain a desired heater core blowing temperature. Generate.

At this time, the control device 30 performs cooler core frost prevention control (in other words, frost suppression control). Specifically, the control device 30 determines that the surface temperature of the cooler core 26 or the temperature of the cooling water flowing into the cooler core 26 is equal to or lower than the frost limit temperature (for example, 0 ° C.), the surface temperature of the cooler core 26, When the temperature of the cooling water flowing into the cooler core 26 is predicted to be equal to or lower than the frost limit temperature (for example, 0 ° C.), the switching valve 58 reduces or completely closes the opening of the cooling water flow path on the cooler core 26 side to the cooler core 26. Decrease or reduce the flow rate of the flowing cooling water. Thereby, since the surface temperature of the cooler core 26 rises, generation | occurrence | production of frost in the cooler core 26 can be suppressed.

The control device 30 executes the control process shown in the flowchart of FIG. 22 during the cooler core frost prevention control.

First, in step S100, it is determined whether or not the temperature Td of the in-vehicle device 55 is lower than the lower limit temperature Ti. When it determines with the temperature Td of the vehicle equipment 55 not being lower than the minimum temperature Ti, it progresses to step S110 and switches the switching valve 58 so that the vehicle equipment 55 may be connected to the low voltage | pressure side heat exchanger 16. FIG. Thereby, it can absorb heat from the vehicle equipment 55 and can be used as a heating heat source.

On the other hand, if it is determined in step S100 that the temperature Td of the in-vehicle device 55 is lower than the lower limit temperature Ti, the process proceeds to step S120, and the switching valve 58 is switched so that the in-vehicle device 55 is not connected to the low-pressure side heat exchanger 16. At the same time, the flow rate of the cooling water discharged from the low temperature side pump 25 is reduced or made zero.

Thereby, it is possible to suppress the occurrence of frost in the cooler core 26 and to suppress the temperature Td of the in-vehicle device 55 from being lower than the lower limit temperature Ti and being supercooled.

In the present embodiment, the control device 30 performs the frost suppression control on the switching valve 58 and the low temperature side pump 25, and when performing the frost suppression control, the switching valve 58 and The low temperature side pump 25 is controlled. The frost suppression control is a control for suppressing the frost of the cooler core 26 by controlling the switching valve 58 and the low temperature side pump 25 so that the flow rate of the cooling water flowing through the cooler core 26 is suppressed.

Thus, as in the seventh embodiment, it is possible to achieve both ensuring the temperature of the air blown into the passenger compartment and suppressing the occurrence of frost in the cooler core. Moreover, compared with the case where it does not absorb heat from the vehicle equipment 55, the motive power of the compressor 11 consumed in order to ensure the blowing air temperature to a vehicle interior can be reduced.

In the present embodiment, when the frost suppression control is performed, the control device 30 controls the flow rate of the cooling water flowing to the in-vehicle device 55 so that the temperature of the in-vehicle device 55 does not fall below the lower limit temperature. Adjust by. Thereby, similarly to the said 7th Embodiment, it can suppress that the vehicle equipment 55 is overcooled.

Specifically, when the control device 30 performs the frost suppression control, the temperature of the in-vehicle device 55 is lower than the lower limit temperature, and the temperature of the in-vehicle device 55 is higher than the lower limit temperature. Thus, the switching valve 58 and the low temperature side pump 25 are controlled so that the flow rate of the cooling water flowing through the in-vehicle device 55 is reduced. Thereby, similarly to the said 7th Embodiment, it can suppress that the vehicle equipment 55 is overcooled.

(Other embodiments)
The above embodiments can be combined as appropriate. The above embodiment can be variously modified as follows, for example.

(1) In the above embodiment, the modulator 12b and the supercooling unit 12c on the high-pressure side heat exchanger 12 side may be configured by the heat exchange unit 12a of the high-pressure side heat exchanger 12. That is, the liquid refrigerant may be stored inside the heat exchange part 12a of the high-pressure side heat exchanger 12.

When the high-pressure side heat exchanger 12 is a refrigerant cooling water heat exchanger that exchanges heat between the refrigerant and the cooling water, the temperature difference between the refrigerant and the cooling water becomes very small in the high-pressure side heat exchanger 12. Therefore, compared with the case where the high-pressure side heat exchanger 12 is a refrigerant air heat exchanger that exchanges heat between the refrigerant and air, the volume of liquid refrigerant in the high-pressure side heat exchanger 12 with respect to the amount of subcooling acquired. The percentage increase is very large. As a result, the liquid refrigerant storage amount can be increased.

That is, when the amount of liquid refrigerant in the high-pressure side heat exchanger 12 increases, the refrigerant condensing area decreases, the refrigeration cycle high pressure increases, and the degree of supercooling slightly increases, the liquid refrigerant storage in the high-pressure side heat exchanger 12 increases. Therefore, the amount of liquid refrigerant stored and the high pressure of the refrigeration cycle can be maintained in a good state.

In this embodiment, the modulator 12b on the high-pressure side heat exchanger 12 side is integrated with the high-pressure side heat exchanger 12, so that the configuration can be simplified.

In this embodiment, the modulator 12b and the supercooling unit 12c on the high-pressure side heat exchanger 12 side exchange heat between the refrigerant and the high-temperature side cooling water in the heat absorption mode. Can be cooled.

(2) In the above embodiment, during the heating mode, the refrigerant flowing out from the heat exchange part 12a of the high-pressure side heat exchanger 12 is stored in the modulator 12b of the high-pressure side heat exchanger 12, and the refrigerant is stored in the high-pressure side heat exchanger. You may make it store in the inside of the refrigerant | coolant piping between 12 and the 1st expansion valve 13. FIG.

In other words, the refrigerant outlet side of the high-pressure side heat exchanger 12 and the refrigerant inlet of the first expansion valve 13 can be stored so that the refrigerant flowing out from the heat exchange unit 12a of the high-pressure side heat exchanger 12 can be stored in the heating mode. A large volume of the refrigerant piping on the side may be ensured.

That is, in the said embodiment, although the 1st refrigerant | coolant storage part which stores the refrigerant | coolant which flowed out from the heat exchange part 12a of the high voltage | pressure side heat exchanger 12 is the modulator 12b of the high voltage | pressure side heat exchanger 12, the 1st refrigerant | coolant storage part is The refrigerant piping on the refrigerant outlet side of the high-pressure side heat exchanger 12 and on the refrigerant inlet side of the first expansion valve 13 may be used.

According to this, since the modulator 12b and the supercooling part 12c of the high-pressure side heat exchanger 12 are not necessary, the configuration can be simplified.

(3) In each of the above embodiments, cooling water is used as a heat medium for adjusting the temperature of the temperature adjustment target device, but various media such as oil may be used as the heat medium.

Nanofluid may be used as the heat medium. A nanofluid is a fluid in which nanoparticles having a particle size of the order of nanometers are mixed. By mixing the nanoparticles with the heat medium, the following effects can be obtained in addition to the effect of lowering the freezing point and making the antifreeze liquid like cooling water using ethylene glycol.

That is, the effect of improving the thermal conductivity in a specific temperature range, the effect of increasing the heat capacity of the heat medium, the effect of preventing the corrosion of metal pipes and the deterioration of rubber pipes, and the heat medium at an extremely low temperature The effect which improves the fluidity | liquidity of can be acquired.

Such an effect varies depending on the particle configuration, particle shape, blending ratio, and additional substance of the nanoparticles.

According to this, since the thermal conductivity can be improved, it is possible to obtain the same cooling efficiency even with a small amount of heat medium as compared with the cooling water using ethylene glycol.

Also, since the heat capacity of the heat medium can be increased, the amount of cold storage heat due to the sensible heat of the heat medium itself can be increased.

Even if the compressor 11 is not operated by increasing the amount of cold storage heat, it is possible to control the temperature and cooling of the equipment using the cold storage heat for a certain amount of time. Can be realized.

The aspect ratio of the nanoparticles is preferably 50 or more. This is because sufficient thermal conductivity can be obtained. The aspect ratio is a shape index that represents the ratio of the vertical and horizontal dimensions of the nanoparticles.

Nanoparticles containing any of Au, Ag, Cu and C can be used. Specifically, Au nanoparticle, Ag nanowire, CNT, graphene, graphite core-shell nanoparticle, Au nanoparticle-containing CNT, and the like can be used as the constituent atoms of the nanoparticle.

CNT is a carbon nanotube. The graphite core-shell nanoparticle is a particle body having a structure such as a carbon nanotube surrounding the atom.

(4) In the refrigeration cycle apparatus 10 of each of the above embodiments, a chlorofluorocarbon refrigerant is used as the refrigerant. However, the type of the refrigerant is not limited to this, and natural refrigerants such as carbon dioxide, hydrocarbon refrigerants, etc. May be used.

The refrigeration cycle apparatus 10 of each of the above embodiments constitutes a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant, but the supercritical refrigeration in which the high-pressure side refrigerant pressure exceeds the critical pressure of the refrigerant. You may comprise the cycle.

Claims

A compressor (11) for sucking and discharging refrigerant;
A high-pressure side heat exchanger (12) for radiating heat from the high-pressure refrigerant discharged from the compressor (11);
A first decompression section (13) for decompressing the refrigerant that has flowed out of the high-pressure side heat exchanger (12);
A refrigerant outdoor air heat exchanger (14) for exchanging heat between the refrigerant flowing out of the first decompression section (13) and the outside air;
A second decompression section (15) for decompressing the refrigerant that has flowed out of the refrigerant outside air heat exchanger (14);
The low-pressure refrigerant disposed in series with the refrigerant outside air heat exchanger (14) in the refrigerant flow and depressurized at least one of the first decompression unit (13) and the second decompression unit (15); A low pressure side heat exchanger (16) for exchanging heat with the heat medium to cool the heat medium;
A cooler core (26) that cools the air by exchanging heat between the heat medium cooled by the low-pressure side heat exchanger (16) and air blown into the vehicle interior;
An endothermic mode in which the refrigerant outside heat exchanger (14) absorbs heat by the refrigerant by adjusting the amount of decompression of the first decompression section (13) and the second decompression section (15), and the refrigerant outside air heat exchange A refrigerating cycle device provided with a control part (30) which changes a heat dissipation mode in which a vessel (14) radiates the refrigerant.
A refrigerant storage unit (12b) that stores the refrigerant heat-exchanged by the high-pressure side heat exchanger (12) in the heat absorption mode and stores the refrigerant heat-exchanged by the refrigerant outside air heat exchanger (14) in the heat dissipation mode. 14b). The refrigeration cycle apparatus according to claim 1, further comprising:
A compressor (11) for sucking and discharging refrigerant;
A high-pressure side heat exchanger (12) for radiating heat from the high-pressure refrigerant discharged from the compressor (11);
A first decompression section (13) for decompressing the refrigerant that has flowed out of the high-pressure side heat exchanger (12);
A refrigerant outdoor air heat exchanger (14) for exchanging heat between the refrigerant flowing out of the first decompression section (13) and the outside air;
A second decompression section (15) for decompressing the refrigerant that has flowed out of the refrigerant outside air heat exchanger (14);
A low-pressure side heat exchanger (16) for absorbing heat to the low-pressure refrigerant decompressed at least one of the first decompression unit (13) and the second decompression unit (15);
An endothermic mode in which the refrigerant outside heat exchanger (14) absorbs heat by the refrigerant by adjusting the amount of decompression of the first decompression section (13) and the second decompression section (15), and the refrigerant outside air heat exchange A controller (30) for switching between a heat release mode in which the vessel (14) dissipates the refrigerant;
In the endothermic mode, the refrigerant that has been heat-exchanged by the high-pressure side heat exchanger (12) is stored, and in the heat dissipation mode, a refrigerant storage unit that stores the refrigerant that has been heat-exchanged by the refrigerant outside air heat exchanger (14). (12b, 14b).
A flow rate adjustment unit (25) for adjusting the flow rate of the heat medium in at least one of the low-pressure side heat exchanger (16) and the cooler core (26);
The control unit (30) controls the operation of the flow rate adjustment unit (25) when the temperature of the heat medium flowing out from the low-pressure side heat exchanger (16) is 0 ° C. or less in the endothermic mode. The refrigeration cycle apparatus according to claim 1 or 2.
The control unit (30) reduces the pressure of the heat medium in at least one of the low pressure side heat exchanger (16) and the cooler core (26) as the pressure of the refrigerant in the refrigerant outside air heat exchanger (14) is lower. The refrigeration cycle apparatus according to claim 4, wherein the operation of the flow rate adjusting unit (25) is controlled so that the flow rate is reduced.
The refrigeration cycle apparatus according to claim 5, wherein the flow rate adjusting unit (25) adjusts the flow rate of the heat medium in both the low pressure side heat exchanger (16) and the cooler core (26).
In the endothermic mode, the high-pressure side heat exchanger (12) and the refrigerant outside air heat exchanger (14) are arranged in series with each other in the refrigerant flow,
In the heat dissipation mode, the refrigerant outside air heat exchanger (14) and the low pressure side heat exchanger (16) are arranged in series with each other in the refrigerant flow,
The refrigerant reservoir is disposed downstream of the refrigerant flow of the high-pressure side heat exchanger (12) and upstream of the refrigerant flow of the first decompression unit (13), and performs heat exchange with the high-pressure side heat exchanger (12). A first refrigerant storage section (12b) for storing the generated refrigerant, a refrigerant flow downstream side of the refrigerant outside air heat exchanger (14) and a refrigerant flow upstream side of the second decompression section (15), 4. The refrigeration cycle apparatus according to claim 2, wherein the refrigeration cycle apparatus is a second refrigerant storage section (14 b) that stores the refrigerant heat-exchanged by the outdoor air heat exchanger (14).
The first refrigerant reservoir (12b) is integrated with the high-pressure side heat exchanger (12),
The high pressure side heat exchanger (12) heats the high temperature side heat medium by exchanging heat between the refrigerant and the high temperature side heat medium,
Furthermore, the refrigerating-cycle apparatus of Claim 7 provided with the heater core (24) which heat-exchanges the said high temperature side heat medium heated with the said high voltage | pressure side heat exchanger (12) and the said air.
A heat absorption mode subcooling section (12c) for supercooling the refrigerant flowing out of the first refrigerant storage section (12b) during the heat absorption mode;
The said 1st refrigerant | coolant storage part (12b) and the said heat absorption mode subcooling part (12c) are heat-exchanged between the said refrigerant | coolant and the said high temperature side heat medium at the time of the said heat absorption mode. The refrigeration cycle apparatus described.
A subcooling section for heat dissipation mode (14c) that supercools the refrigerant that has flowed out of the second refrigerant storage section (14b) during the heat dissipation mode;
A bypass unit (18) in which the refrigerant flowing out of the refrigerant outside air heat exchanger (14) flows bypassing the heat dissipation mode subcooling unit (14c);
10. The apparatus according to claim 7, further comprising: a bypass opening adjustment unit (19) that reduces a flow path opening of the bypass unit (18) in the heat dissipation mode compared to the heat absorption mode. The refrigeration cycle apparatus described.
The heat dissipation mode subcooling section (14c) has a plurality of refrigerant tubes through which the refrigerant flows,
A distribution tank section (14h) for distributing the refrigerant flowing out of the second refrigerant storage section (14b) to the plurality of refrigerant tubes;
The said bypass part (18) is a refrigerating-cycle apparatus of Claim 10 extended from the said distribution tank part (14h) to the refrigerant | coolant flow downstream of the said supercooling part for heat dissipation modes (14c).
The high pressure side heat exchanger (12) heats the high temperature side heat medium by exchanging heat between the refrigerant and the high temperature side heat medium,
Furthermore, a high temperature side heat medium heat exchanger (24) for exchanging heat of the high temperature side heat medium heated by the high pressure side heat exchanger (12),
A high temperature side flow rate adjustment unit (23) for adjusting the flow rate of the high temperature side heat medium flowing through the high pressure side heat exchanger (12),
The control unit (30) stops the high temperature side flow rate adjustment unit (23) during the heat dissipation mode, and the temperature of the high temperature side heat medium in the high pressure side heat exchanger (12) is equal to or higher than a predetermined temperature during the heat dissipation mode. 8. The operation of the high temperature side flow rate adjusting unit (23) is controlled so that the flow rate of the high temperature side heat medium flowing through the high pressure side heat exchanger (12) increases. The refrigeration cycle apparatus according to one.
A heat supply device (40) through which the heat medium flows and supplies heat to the heat medium;
A heat exchanger flow rate adjustment unit (17, 41, 43) for adjusting the flow rate of at least one of the outside air and the refrigerant flowing into the refrigerant outside air heat exchanger (14),
When the temperature difference between the refrigerant flowing into the refrigerant outside air heat exchanger (14) and the outside air becomes a predetermined value or less, the control unit (30) causes the refrigerant outside air heat exchanger (14) to 13. The operation of the heat exchanger flow rate adjustment unit (17, 41, 43) is controlled so that a flow rate of at least one of the outside air and the refrigerant flowing in is reduced. Refrigeration cycle equipment.
The heat exchanger flow rate adjustment unit is an outside air blower (17) for blowing the outside air to the refrigerant outside air heat exchanger (14),
When the temperature difference between the refrigerant flowing into the refrigerant outside air heat exchanger (14) and the outside air becomes a predetermined value or less, the control unit (30) moves to the refrigerant outside air heat exchanger (14). The refrigeration cycle apparatus according to claim 13, wherein the operation of the outside air blower (17) is controlled so that the blowing direction of the outside air is reversed.
The heat exchanger flow rate adjustment unit is a shutter (41) that adjusts the opening degree of the outside air passage that flows through the refrigerant outside air heat exchanger (14).
When the temperature difference between the refrigerant flowing into the refrigerant outside air heat exchanger (14) and the outside air becomes equal to or less than a predetermined value, the control unit (30) is configured to reduce the opening degree. The refrigeration cycle apparatus according to claim 13, which controls the operation of (41).
A flow rate adjusting unit (25) for adjusting the flow rate of the heat medium in the low pressure side heat exchanger (16);
The said control part (30) controls the superheat degree of the said refrigerant | coolant heat-exchanged by the said low voltage | pressure side heat exchanger (16) by controlling the action | operation of the said flow volume adjustment part (25). The refrigeration cycle apparatus described in 1.
A fan (27) for blowing the air to the cooler core (26);
The low-pressure side heat exchanger (16) has an inlet (16a) and an outlet (16b) for the heat medium,
The cooler core (26) includes a heat exchanging part (26c) that cools the air by exchanging heat between the heat medium cooled by the low-pressure side heat exchanger (16) and air,
The refrigeration cycle apparatus according to any one of claims 1 to 16, wherein the heat exchange part (26c) is disposed at a position higher in a gravitational direction than the inlet (16a) and the outlet (16b).
A blower (27) for blowing the air to the cooler core (26);
A heat medium flow path section (22a) through which the heat medium flows between the low pressure side heat exchanger (16) and the cooler core (26);
The low-pressure side heat exchanger (16) has an inlet (16a) and an outlet (16b) for the heat medium,
The refrigeration cycle apparatus according to any one of claims 1 to 16, wherein at least a part of the heat medium flow path part (22a) is arranged at a position lower in a gravitational direction than the heat exchange part (26c). .
A compressor (11) for sucking and discharging refrigerant;
A high-pressure side heat exchanger (12) for radiating heat from the high-pressure refrigerant discharged from the compressor (11);
A decompression section (13, 15) for decompressing the refrigerant flowing out of the high pressure side heat exchanger (12);
A low-pressure side heat exchanger (16) that cools the heat medium by exchanging heat between the low-pressure refrigerant decompressed by the decompression unit (13, 15) and the heat medium;
A cooler core (26) having a heat exchanging portion (26c) for exchanging heat between the heat medium cooled by the low-pressure side heat exchanger (16) and air and cooling the air;
A heat medium pump (25) that sucks and discharges the heat medium, and circulates the heat medium between the low pressure side heat exchanger (16) and the cooler core (26);
A blower (27) for blowing the air to the cooler core (26),
The low-pressure side heat exchanger (16) has an inlet (16a) and an outlet (16b) for the heat medium,
The said heat exchange part (26c) is a refrigerating-cycle apparatus arrange | positioned in the position of a gravity direction higher than at least one among the said inlet (16a) and the said outlet (16b).
A compressor (11) for sucking and discharging refrigerant;
A high-pressure side heat exchanger (12) for radiating heat from the high-pressure refrigerant discharged from the compressor (11);
A decompression section (13, 15) for decompressing the refrigerant flowing out of the high pressure side heat exchanger (12);
A low-pressure side heat exchanger (16) that cools the heat medium by exchanging heat between the low-pressure refrigerant decompressed by the decompression unit (13, 15) and the heat medium;
A cooler core (26) having a heat exchanging portion (26c) for exchanging heat between the heat medium cooled by the low-pressure side heat exchanger (16) and air and cooling the air;
A heat medium pump (25) that sucks and discharges the heat medium, and circulates the heat medium between the low pressure side heat exchanger (16) and the cooler core (26);
A blower (27) for blowing the air to the cooler core (26);
A heat medium flow path section (22a) that forms a flow path of the heat medium between the low pressure side heat exchanger (16) and the cooler core (26),
The low-pressure side heat exchanger (16) has an inlet (16a) and an outlet (16b) for the heat medium,
At least a part of the heat medium flow path part (22a) is a refrigeration cycle apparatus arranged at a position lower in the direction of gravity than the heat exchange part (26c).
21. The refrigeration cycle apparatus according to claim 19 or 20, wherein the refrigerant outside air heat exchanger (14) and the low pressure side heat exchanger (16) are arranged in series with each other in the flow of the refrigerant.
A compressor (11) for sucking and discharging refrigerant;
A high-pressure side heat exchanging section (12, 24) for heating the air by exchanging heat between the high-pressure refrigerant discharged from the compressor (11) and the air blown into the vehicle interior;
A high-pressure side heat exchanger (12) for radiating heat from the high-pressure refrigerant discharged from the compressor (11);
A decompression section (13) for decompressing the refrigerant flowing out of the high pressure side heat exchanger (12);
A refrigerant outside air heat exchanger (14) for exchanging heat between the refrigerant decompressed by the decompression unit (13) and the outside air;
A low pressure side heat exchanger (16) for cooling the heat medium by exchanging heat between the refrigerant and the heat medium flowing out from the refrigerant outside air heat exchanger (14);
A cooler core (26) that cools the air by exchanging heat between the heat medium cooled by the low-pressure side heat exchanger (16) and the air blown into the vehicle interior;
On-vehicle equipment (55) that generates heat during operation and is absorbed by the heat medium cooled by the low-pressure side heat exchanger (16),
A flow rate adjusting unit (56, 57, 58) for adjusting the flow rate of the heat medium flowing through the cooler core (26) and the flow rate of the heat medium flowing through the in-vehicle device (55);
Frost suppression control is performed to suppress the frost of the cooler core (26) by controlling the flow rate adjusting unit (56, 57, 58) so that the flow rate of the heat medium flowing through the cooler core (26) is suppressed. A refrigeration cycle comprising a control unit (30) for controlling the flow rate adjusting unit (56, 57, 58, 25) so that the heat medium flows to the in-vehicle device (55) when the frost suppression control is performed. apparatus.
When the control unit (30) performs the frost suppression control, the flow rate of the heat medium flowing through the in-vehicle device (55) is set so that the temperature of the in-vehicle device (55) does not fall below a lower limit temperature. The refrigeration cycle apparatus according to claim 22, wherein the refrigeration cycle apparatus is adjusted by an adjustment unit (56, 57, 58, 25).
When the control unit (30) performs the frost suppression control and the temperature of the in-vehicle device (55) is lower than the lower limit temperature, the temperature of the in-vehicle device (55) exceeds the lower limit temperature. 24. The refrigeration cycle apparatus according to claim 23, wherein the flow rate adjusting unit (56, 57, 58, 25) is controlled so that a flow rate of the heat medium flowing through the in-vehicle device (55) is reduced as compared with a case where the vehicle is installed. .