JP2017194180A - Refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration cycle device which can effectively utilize an inner heat exchanger.SOLUTION: A refrigeration cycle device comprises: a compressor 20 for sucking and discharging a refrigerant; a high-pressure side heat exchanger 21 for heat-exchanging the refrigerant which is discharged from the compressor; a high-pressure side inner heat exchanger 22 for heat-exchanging the refrigerant and a heat medium which are heat-exchanged by the high-pressure side heat exchanger; a decompression part 23 for decompressing the refrigerant which is heat-exchanged by the high-pressure side inner heat exchanger; a low-pressure side heat exchanger 24 for heat-exchanging the refrigerant which is decompressed by the decompression part; a low-pressure side inner heat exchanger 25 for heat-exchanging the refrigerant which is heat-exchanged by the low-pressure side heat exchanger and the heat medium which is heat-exchanged by the high-pressure side inner heat exchanger; and a flow rate adjustment part 28 for adjusting a flow rate of the heat medium flowing in the high-pressure side inner heat exchanger and the low-pressure side inner heat exchanger.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a refrigeration cycle apparatus including an internal heat exchanger.

  Conventionally, Patent Document 1 describes a refrigeration cycle apparatus including an internal heat exchanger. The internal heat exchanger exchanges heat between the high-pressure refrigerant that has flowed out of the condenser and the low-pressure refrigerant that has flowed out of the evaporator.

  Thereby, since the high-pressure refrigerant is supercooled by the low-pressure refrigerant, the amount of liquid refrigerant supplied to the evaporator side can be increased. In the evaporator, as the amount of liquid refrigerant increases, the refrigerant flow resistance decreases and the cooling capacity improves. On the other hand, since the low-pressure refrigerant is overheated by the high-pressure refrigerant, liquid compression can be prevented from occurring in the compressor.

JP 2007-298196 A

  The internal heat exchanger exchanges heat between the supercooled region liquid refrigerant on the refrigeration cycle high pressure side and the superheated gas gaseous refrigerant on the refrigeration cycle low pressure side. As a result, the supercooled liquid refrigerant is cooled to a lower temperature and the superheated gas gaseous refrigerant is heated to a higher temperature, so that the enthalpy difference in the evaporator is increased and the performance and efficiency of the refrigeration cycle are improved.

  However, in an environment where the heat load is small, the refrigerant flow rate is small on both the refrigeration cycle high pressure side and the refrigeration cycle low pressure side, and the refrigerant temperature difference between the refrigeration cycle high pressure side and the refrigeration cycle low pressure side is small. The heat exchange performance in the exchanger is reduced, and the effect of the internal heat exchanger is hardly obtained. That is, since the internal heat exchange amount is uniquely determined according to the refrigeration cycle load, the internal heat exchanger cannot be effectively used depending on the operating environment.

  An object of this invention is to provide the refrigerating-cycle apparatus which can utilize an internal heat exchanger effectively in view of the said point.

In order to achieve the above object, in the refrigeration cycle apparatus according to claim 1,
A compressor (20) for sucking and discharging refrigerant;
A high pressure side heat exchanger (21) for exchanging heat of the refrigerant discharged from the compressor;
A high-pressure side internal heat exchanger (22) for exchanging heat between the refrigerant and the heat medium heat-exchanged in the high-pressure side heat exchanger;
A decompression section (23) for decompressing the refrigerant heat-exchanged in the high-pressure side internal heat exchanger;
A low pressure side heat exchanger (24) for exchanging heat of the refrigerant decompressed by the decompression unit;
A low pressure side internal heat exchanger (25) for exchanging heat between the refrigerant heat exchanged by the low pressure side heat exchanger and the heat medium heat exchanged by the high pressure side internal heat exchanger;
A flow rate adjusting unit (28, 42, 43, 44, 68, 69, 70) for adjusting the flow rate of the heat medium flowing through the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger.

  According to this, by adjusting the flow rate of the heat medium flowing through the high pressure side internal heat exchanger (22) and the low pressure side internal heat exchanger (24), the amount of heat exchange between the high pressure side refrigerant and the low pressure side refrigerant can be arbitrarily set. Can be adjusted. Therefore, the internal heat exchanger can be used effectively by adjusting the amount of heat exchange between the high-pressure side refrigerant and the low-pressure side refrigerant according to the operating environment.

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

It is a whole lineblock diagram showing the refrigeration cycle device for vehicles in a 1st embodiment. It is a block diagram which shows the electric control part of the refrigeration cycle apparatus for vehicles in 1st Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 2nd Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 3rd Embodiment. It is a typical front view which shows the high voltage | pressure side internal heat exchanger and low voltage | pressure side internal heat exchanger of the refrigeration cycle apparatus for vehicles in 3rd Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 4th Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 5th Embodiment. It is a typical front view which shows the high voltage | pressure side internal heat exchanger and low voltage | pressure side internal heat exchanger in 5th Embodiment. It is a whole lineblock diagram showing the refrigeration cycle device for vehicles in a 6th embodiment. It is a whole block diagram which shows the 1st operation state of the refrigeration cycle apparatus for vehicles in 6th Embodiment. It is a whole block diagram which shows the 2nd operation state of the refrigeration cycle apparatus for vehicles in 6th Embodiment. It is a whole block diagram which shows the 3rd operation state of the refrigeration cycle apparatus for vehicles in 6th Embodiment. It is a whole lineblock diagram showing the refrigeration cycle device for vehicles in a 7th embodiment. It is a whole block diagram which shows the 1st operation state of the refrigeration cycle apparatus for vehicles in 7th Embodiment. It is a whole block diagram which shows the 2nd operation state of the refrigeration cycle apparatus for vehicles in 7th Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 8th Embodiment. It is a whole block diagram which shows the 1st operation state of the refrigeration cycle apparatus for vehicles in 8th Embodiment. It is a whole block diagram which shows the 2nd operation state of the refrigeration cycle apparatus for vehicles in 8th Embodiment. It is a whole block diagram which shows the refrigeration cycle apparatus for vehicles in 9th Embodiment. It is a whole block diagram which shows the 1st operation state of the refrigeration cycle apparatus for vehicles in 9th Embodiment. It is a whole block diagram which shows the 2nd operation state of the refrigeration cycle apparatus for vehicles in 9th Embodiment. It is a whole lineblock diagram showing the 1st operation state of the refrigeration cycle device for vehicles in a 10th embodiment. It is a whole block diagram which shows the 2nd operation state of the refrigeration cycle apparatus for vehicles in 10th Embodiment. It is a whole block diagram which shows the 3rd operation state of the refrigeration cycle apparatus for vehicles in 10th Embodiment. It is a whole block diagram which shows the air_conditioning | cooling mode of the refrigeration cycle apparatus for vehicles in 11th Embodiment. It is a whole block diagram which shows the heating mode of the refrigeration cycle apparatus for vehicles in 11th Embodiment. It is a block diagram which shows the cooling water circuit of the refrigeration cycle apparatus for vehicles in 11th Embodiment. It is a whole block diagram which shows the air_conditioning | cooling mode of the refrigeration cycle apparatus for vehicles in 12th Embodiment. It is a whole lineblock diagram showing the heating mode of the refrigeration cycle device for vehicles in a 12th embodiment.

  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 vehicle refrigeration cycle apparatus 10 shown in FIG. 1 includes a refrigeration cycle 11 and a cooling water circuit 12. The refrigeration cycle 11 is a vapor compression refrigerator. Cooling water circulates in the cooling water circuit 12.

  The cooling water is a fluid as a heat medium. For example, the cooling water is a liquid containing at least ethylene glycol, dimethylpolysiloxane or nanofluid, or an antifreeze liquid. The cooling water circuit 12 is a heat medium circuit in which the heat medium circulates.

  The refrigeration cycle 11 includes a compressor 20, a condenser 21, a high-pressure side internal heat exchanger 22, an expansion valve 23, an evaporator 24, and a low-pressure side internal heat exchanger 25. The refrigerant of the refrigeration cycle 11 is a fluorocarbon refrigerant. The refrigeration cycle 11 is a subcritical refrigeration cycle in which the high-pressure side refrigerant pressure does not exceed the critical pressure of the refrigerant.

  The compressor 20 is an electric compressor driven by electric power supplied from a battery, and sucks, compresses and discharges the refrigerant of the refrigeration cycle 11. The compressor 20 may be a belt-driven compressor that is driven by an engine belt by the driving force of the engine.

  The condenser 21 is a high-pressure side heat exchanger that condenses the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 20 and the outside air. Outside air is blown to the condenser 21 by an outdoor blower (not shown).

  The condenser 21 may condense the high-pressure refrigerant by exchanging heat between the high-pressure refrigerant discharged from the compressor 20 and the cooling water of the cooling water circuit 12.

  The high-pressure side internal heat exchanger 22 is a heat exchanger that exchanges heat between the liquid refrigerant flowing out of the condenser 21 and the cooling water in the cooling water circuit 12.

  The expansion valve 23 is a decompression unit that decompresses and expands the liquid-phase refrigerant that has flowed out of the high-pressure side internal heat exchanger 22. The expansion valve 23 is a temperature type expansion valve having a temperature sensing part 23a for detecting the degree of superheat of the evaporator 24 outlet side refrigerant based on the temperature and pressure of the evaporator 24 outlet side refrigerant. That is, the expansion valve 23 is a temperature type expansion valve that adjusts the throttle passage area by a mechanical mechanism so that the degree of superheat of the refrigerant on the outlet side of the evaporator 24 falls within a predetermined range. The expansion valve 23 may be an electric expansion valve that adjusts the throttle passage area by an electric mechanism.

  The evaporator 24 is a low-pressure side heat exchanger that evaporates the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant decompressed and expanded by the expansion valve 23 and the air blown into the vehicle interior by an indoor fan (not shown).

  The low-pressure side internal heat exchanger 25 is a heat exchanger that exchanges heat between the gas-phase refrigerant that has flowed out of the evaporator 24 and the cooling water in the cooling water circuit 12. The gas phase refrigerant heat-exchanged by the low-pressure side internal heat exchanger 25 is sucked into the compressor 20 and compressed.

  The evaporator 24 may evaporate the low-pressure refrigerant by exchanging heat between the low-pressure refrigerant decompressed and expanded by the expansion valve 23 and the cooling water.

  The high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 are arranged in the cooling water circuit 12. The cooling water circuit 12 has a pump 28.

  The pump 28 is an electric pump that sucks and discharges cooling water. The pump 28 may be a belt-driven pump that is driven by transmitting the driving force of the engine 21 through a belt.

  The high-pressure side internal heat exchanger 22, the low-pressure side internal heat exchanger 25, and the pump 28 are arranged in series with the cooling water circuit 12.

  The cooling water circuit 12 is configured such that the flow direction of the cooling water in the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 is opposite to the refrigerant flow direction. That is, in the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25, the refrigerant and the cooling water are counterflowed. In the high-pressure-side internal heat exchanger 22 and the low-pressure-side internal heat exchanger 25, the refrigerant and the cooling water exchange heat by a sensible heat change. growing.

  Next, the electric control unit of the vehicle 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.

  Control target devices controlled by the control device 30 are the compressor 20, the pump 28, and the like. Detection signals of sensor groups such as the inside air temperature sensor 31, the outside air temperature sensor 32, the solar radiation sensor 33, the refrigerant temperature sensor 34, the high pressure side temperature sensor 35, and the low pressure side temperature sensor 36 are input to the input side of the control device 30. .

  The room temperature sensor 31 is a room temperature detector that detects the temperature of the room air. The outside temperature sensor 32 is an outside temperature detector that detects the temperature of the outside air. The solar radiation sensor 33 is a solar radiation amount detection unit that detects the amount of solar radiation in the passenger compartment.

  The refrigerant temperature sensor 34 is a refrigerant temperature detection unit that detects the temperature of the refrigerant in the refrigeration cycle 11. Specifically, the refrigerant temperature sensor 34 detects the temperature of the refrigerant discharged from the compressor 20.

  The high pressure side temperature sensor 35 is a high pressure side temperature detector that detects the temperature of the high pressure side internal heat exchanger 22. Specifically, the high pressure side temperature sensor 35 detects the temperature of the cooling water flowing into the high pressure side internal heat exchanger 22.

  The low-pressure side temperature sensor 36 is a low-pressure side temperature detector that detects the temperature of the low-pressure side internal heat exchanger 25. Specifically, the low pressure side temperature sensor 36 detects the temperature of the cooling water flowing into the low pressure side internal heat exchanger 25.

  Operation signals from various air conditioning operation switches provided on the operation panel 37 are input to the input side of the control device 30. For example, the operation panel 37 is arranged near the instrument panel in the front part of the vehicle interior.

  Various air conditioning operation switches provided on the operation panel 37 are a vehicle interior temperature setting switch, an auto switch, an air conditioner switch, an air volume setting switch, an air conditioning stop switch, and the like.

  Each switch may be a push switch in which electrical contacts are made conductive by being mechanically pressed, or may be a touch screen system that reacts by touching a predetermined area on the electrostatic panel.

  The vehicle interior temperature setting switch is target temperature setting means for setting the vehicle interior target temperature Tset by the operation of the passenger. The auto switch is a switch for setting or canceling automatic control of air conditioning. The air conditioner switch is a switch for switching between operation and stop of cooling or dehumidification. The air volume setting switch is a switch for setting the air volume blown from the indoor blower. The air conditioning stop switch is a switch that stops air conditioning.

  The control device 30 determines the air conditioning mode based on the inside air temperature and the target blowing temperature TAO of the vehicle cabin blowing air. The target blowing temperature TAO is a value determined to quickly bring the inside air temperature close to the occupant's desired target temperature Tset, and is calculated by the following formula F1.

TAO = Kset * Tset-Kr * Tr-Kam * Tam-Ks * Ts + C ... F1
In this equation, Tset is the target temperature in the vehicle interior set by the vehicle interior temperature setting switch, Tr is the internal air temperature detected by the internal air temperature sensor 31, and Tam is the external air temperature detected by the external air temperature sensor 32. Ts is the amount of solar radiation detected by the solar radiation sensor 33. Kset, Kr, Kam, Ks are control gains, and C is a correction constant.

  The control device 30 determines that the air-conditioning mode is the cooling mode when the target blowing temperature TAO of the vehicle interior blowing air is lower than the inside air temperature, and the air conditioning mode when the target blowing temperature TAO of the vehicle interior blowing air is higher than the inside air temperature. The mode is determined as the heating mode.

  Next, the operation in the above configuration will be described. When the control device 30 operates the compressor 20 and the like, the air blown into the vehicle compartment is cooled by the evaporator 24. At this time, when the control device 30 operates the pump 28, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12. By increasing the enthalpy difference (that is, the refrigeration capacity) between the side refrigerant and the inlet side refrigerant, the coefficient of performance (so-called COP) of the cycle can be improved.

  In the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25, the flow direction of the refrigerant and the flow direction of the cooling water face each other. That is, in the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25, the refrigerant and the cooling water are counterflowed. Therefore, the heat exchange efficiency between the refrigerant and the cooling water is increased.

  In particular, in the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25, since both the refrigerant and the cooling water exchange heat by sensible heat change, the effect of improving the heat exchange efficiency due to the counterflow is increased.

  In the present embodiment, the pump 28 adjusts the flow rate of the cooling water flowing through the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25. As a result, the amount of heat exchange between the high-pressure side refrigerant and the low-pressure side refrigerant can be arbitrarily adjusted, so that the amount of heat exchange between the high-pressure side refrigerant and the low-pressure side refrigerant can be adjusted according to the operating environment to adjust the internal heat exchangers 22, 25. Can be used effectively.

  For example, when the difference between the high and low pressures of the refrigeration cycle 11 is small, reverse heat exchange is performed in the internal heat exchangers 22 and 25, and the refrigeration cycle efficiency may be significantly deteriorated. That is, in the normal case, the high-pressure side refrigerant is cooled and the low-pressure side refrigerant is heated in the internal heat exchangers 22 and 25, whereas the high-low pressure difference of the refrigeration cycle 11 is small, the internal heat exchangers 22 and 25 In this case, the reverse heat exchange may be performed such that the high-pressure side refrigerant is heated and the low-pressure side refrigerant is cooled.

  In view of this point, in the present embodiment, the control device 30 causes the temperature difference between the refrigerant flowing into the high-pressure side internal heat exchanger 22 and the refrigerant flowing into the low-pressure side internal heat exchanger 25 to be a predetermined value or less. In this case, the high pressure side internal heat exchanger 22 and the low pressure are compared with those before the temperature difference between the refrigerant flowing into the high pressure side internal heat exchanger 22 and the refrigerant flowing into the low pressure side internal heat exchanger 25 becomes a predetermined value or less. The operation of the flow rate adjusting unit is controlled so that the flow rate of the cooling water flowing through the side internal heat exchanger 5 decreases.

  According to this, the amount of internal heat exchange can be reduced by reducing the cooling water flow rate by reducing the number of rotations of the pump 28 or stopping the pump 28, so that reverse heat exchange can be prevented.

  In the present embodiment, when the temperature of the refrigerant discharged from the compressor 20 is equal to or higher than the predetermined temperature, the control device 30 compares the temperature before the temperature of the refrigerant discharged from the compressor 20 becomes equal to or higher than the predetermined temperature. The operation of the pump 28 is controlled so that the flow rate of the cooling water flowing through the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 decreases.

  According to this, when the temperature of the refrigerant discharged from the compressor 20 is high, the degree of superheat of the refrigerant sucked into the compressor 20 can be reduced by reducing the cooling water flow rate and reducing the internal heat exchange amount. Therefore, the refrigerant temperature discharged from the compressor 20 can be lowered without reducing the rotation speed of the compressor 20, that is, the performance of the refrigeration cycle 11.

  At the time of low outside air temperature in winter, the temperature sensing part 23a of the expansion valve 23 is cooled at the time of starting the cycle, and the valve opening does not readily increase. As a result, the desired high pressure is delayed and the cycle start is delayed. .

  In view of this point, in the present embodiment, when the compressor 20 is activated, the control device 30 causes the pump 28 so that the cooling water flows through the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25. Control the operation.

  According to this, since the heat of the high-pressure refrigerant in the refrigeration cycle 11 can be introduced into the temperature sensing portion 23a of the expansion valve 23 by increasing the coolant flow rate at the time of starting the cycle, the temperature sensing portion can be quickly heated. The opening can be quickly enlarged to obtain a desired high pressure quickly, and thus cycle activation can be accelerated.

  In the present embodiment, the control device 30, when a predetermined time has elapsed since the start of the compressor 20, compared to before the predetermined time has elapsed since the start of the compressor 20, the high pressure side internal heat exchanger. The operation of the pump 28 is controlled so that the flow rate of the cooling water flowing through the low-pressure side internal heat exchanger 25 is reduced.

  According to this, by increasing the cooling water flow rate at the time of starting the cycle, the heat of the high-pressure refrigerant in the refrigeration cycle 11 is introduced into the temperature sensing part of the expansion valve 23 to quickly warm the temperature sensing part. When the temperature sensing unit 23 is warmed, the cooling water flow rate can be reduced to adjust to the normal internal heat exchange amount.

  In the present embodiment, the high-pressure side heat exchanger 22 and the low-pressure side heat exchanger 25 are arranged in series with each other in the flow of the cooling water. Thereby, the heat exchanger efficiency of the high-pressure side heat exchanger 22 and the low-pressure side heat exchanger 25 can be improved.

(Second Embodiment)
In the present embodiment, as shown in FIG. 3, the heat generating device 40 is arranged in the cooling water circuit 12. The heat generating device 40 is a temperature adjusting device that generates heat during operation and requires temperature maintenance.

  The high-pressure side internal heat exchanger 22, the low-pressure side internal heat exchanger 25, the pump 28, and the heat generating device 40 are arranged in series in the cooling water circuit 12. In FIG. 3, the refrigeration cycle 11 is not shown.

  A detection signal from a device temperature sensor (not shown) is input to the input side of the control device 30. The device temperature sensor is a device temperature detection unit that detects the temperature of the heat generating device 40.

  In the present embodiment, since the heat generating device 40 is disposed in the cooling water circuit 12, cooling water having a temperature between the temperature of the high-pressure side refrigerant and the temperature of the low-pressure side refrigerant in the refrigeration cycle 11 flows through the heat generating device 40. Therefore, the temperature of the heat generating device 40 can be adjusted within an appropriate temperature range.

  For example, since the heat generating device 40 is cooled at a high outdoor temperature in summer and the heat generating device 40 is heated at a low outdoor temperature in winter, the heat generating device 40 can be automatically adjusted to an appropriate temperature.

For example, the heat generating device 40 is a battery. The battery has an appropriate temperature of about 0 to 25 ° C., cooling is required in the summer, and heating is required in the winter. On the other hand, the battery has a characteristic of hating extreme temperature changes.
.

  By arranging the battery in the cooling water circuit 12, the temperature of the cooling water flowing into the battery becomes an intermediate temperature between the temperature of the high-pressure side refrigerant and the temperature of the low-pressure side refrigerant in the refrigeration cycle 11. Therefore, the battery can be cooled in summer and the battery can be heated in winter. Moreover, since the degree of supercooling of the refrigerant heat-exchanged in the high-pressure side internal heat exchanger 22 is further increased by heating the battery, the enthalpy difference in the evaporator 24 is further increased, and the performance and efficiency of the refrigeration cycle are increased. Further improvement.

(Third embodiment)
In the present embodiment, as shown in FIG. 4, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 are arranged in parallel with each other in the cooling water circuit 12, and the pump 28 and the heating device 40 are provided with cooling water. In the circuit 12, the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25 are arranged in series.

  A heat generating device 40 is disposed in the cooling water circuit 12. In FIG. 4, the refrigeration cycle 11 is not shown.

  As shown in FIG. 5, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 are integrated as a heat exchanger 41. The heat exchanger 41 includes a plurality of high-pressure side refrigerant circulation portions 41a, a plurality of low-pressure side refrigerant circulation portions 41b, a plurality of cooling water circulation portions 41c, a cooling water distribution tank 41d, and a cooling water collecting tank 41e.

  The plurality of high-pressure side refrigerant circulation portions 41 a form a refrigerant flow path through which the liquid-phase refrigerant that has flowed out of the condenser 21 flows. The plurality of low-pressure side refrigerant circulation portions 41b form a refrigerant flow path through which the gas-phase refrigerant that has flowed out of the evaporator 24 flows.

  The plurality of cooling water circulation portions 41c form a cooling water flow path through which the cooling water distributed from the cooling water distribution tank 41d flows. The cooling water circulation part 41c is arranged adjacent to the high-pressure side refrigerant circulation part 41a and the low-pressure side refrigerant circulation part 41b.

  The high-pressure side internal heat exchanger 22 is configured by the high-pressure side refrigerant circulation part 41a and the cooling water circulation part 41c adjacent to the high-pressure side refrigerant circulation part 41a. The low-pressure side internal heat exchanger 25 is configured by the low-pressure side refrigerant circulation part 41b and the cooling water circulation part 41c adjacent to the low-pressure side refrigerant circulation part 41b.

  The cooling water distribution tank 41d and the cooling water collection tank 41e are a common tank unit that distributes and collects the cooling water to the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25.

  The cooling water distribution tank 41d forms a space for distributing the cooling water discharged from the pump 28 to the plurality of cooling water circulation portions 41c. A cooling water inlet 41f into which the cooling water discharged from the pump 28 flows is formed in the cooling water distribution tank 41d. The cooling water inlet 41f is a common heat medium inlet through which the heat medium flows into the high-pressure side internal heat exchanger 22 and the low-pressure side heat exchanger 25.

  The cooling water collecting tank 41e forms a space in which cooling water that has flowed through the plurality of cooling water circulation portions 41c is collected and flows out to the suction side of the pump 28. The cooling water collecting tank 41e is formed with a cooling water outlet 41g through which the cooling water flows out to the suction side of the pump 28. The cooling water outlet 41g is a common heat medium outlet through which the heat medium flows out from the high-pressure side internal heat exchanger 22 and the low-pressure side heat exchanger 25.

  The heat exchanger 41 includes a high-pressure side refrigerant distribution tank (not shown), a high-pressure side refrigerant collection tank (not shown), a low-pressure side refrigerant distribution tank (not shown), and a low-pressure side refrigerant collection tank (not shown).

  The high-pressure side refrigerant distribution tank forms a space for distributing the liquid-phase refrigerant flowing out of the condenser 21 to the plurality of high-pressure side refrigerant circulation portions 41a. The high-pressure side refrigerant assembly tank forms a space in which the liquid-phase refrigerant that has flowed through the plurality of high-pressure side refrigerant circulation portions 41 a is collected and flows out to the inlet side of the expansion valve 23.

  The low-pressure side refrigerant distribution tank forms a space for distributing the gas-phase refrigerant flowing out of the evaporator 24 to the plurality of low-pressure side refrigerant circulation portions 41b. The low-pressure side refrigerant collection tank forms a space for collecting the gas-phase refrigerant that has flowed through the plurality of low-pressure side refrigerant circulation portions 41 b and flowing out to the suction side of the compressor 20.

  In the cooling water circulation part 41c adjacent to the high pressure side refrigerant circulation part 41a, the cooling water exchanges heat with the liquid phase refrigerant of the high pressure side refrigerant circulation part 41a, so that the liquid phase refrigerant in the high pressure side refrigerant circulation part 41a is cooled and cooled. Water is heated.

  In the cooling water circulation part 41c adjacent to the low pressure side refrigerant circulation part 41b, the cooling water exchanges heat with the gas phase refrigerant in the low pressure side refrigerant circulation part 41b, so that the gas phase refrigerant in the low pressure side refrigerant circulation part 41b is cooled and cooled. Is cooled.

  The cooling water heated by the cooling water circulation part 41c adjacent to the high-pressure side refrigerant circulation part 41a and the cooling water cooled by the cooling water circulation part 41c adjacent to the low-pressure side refrigerant circulation part 41b are mixed in the cooling water collecting tank 41e. As a result, the temperature reaches an intermediate temperature and flows out to the suction side of the pump 28.

  The temperature of the cooling water mixed in the cooling water collecting tank 41e can be optimized by setting the number ratio between the high-pressure side refrigerant circulation part 41a and the low-pressure side refrigerant circulation part 41b.

  In the present embodiment, the high-pressure side internal heat exchanger 22 and the low-pressure side heat exchanger 25 are integrated by having a common cooling water distribution tank 41d and a cooling water collection tank 41e that distribute and collect the cooling water. Yes. The pump 28 adjusts the flow rate of the cooling water flowing through the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25. According to this, the structure of the high-pressure side internal heat exchanger 22 and the low-pressure side heat exchanger 25 can be simplified.

(Fourth embodiment)
In this embodiment, as shown in FIG. 6, compared to the third embodiment, a three-way valve 42 is provided at the cooling water flow branch between the high pressure side internal heat exchanger 22 side and the low pressure side internal heat exchanger 25 side. Is arranged.

  The three-way valve 42 adjusts the opening ratio between the cooling water flow path on the high pressure side internal heat exchanger 22 side and the cooling water flow path on the low pressure side internal heat exchanger 25 side, so that the high pressure side internal heat exchanger 22 side The cooling water flow ratio between the cooling water channel and the cooling water channel on the low-pressure side internal heat exchanger 25 side is adjusted. The operation of the three-way valve 42 is controlled by the control device 30.

  The control device 30 can control the operation of the three-way valve 42 to adjust the temperature of the cooling water flowing into the heat generating device 40.

  In the present embodiment, the three-way valve 42 can independently control the flow rate of the cooling water flowing through the high pressure side internal heat exchanger 22 and the flow rate of the cooling water flowing through the low pressure side internal heat exchanger 25. And when the control apparatus 30 needs to heat the heat generating apparatus 40, the flow volume of the cooling water which flows through the high voltage | pressure side internal heat exchanger 22 increases, or the flow volume of the cooling water which flows through the low voltage | pressure side internal heat exchanger 25 increases. The operation of the three-way valve 42 is controlled so as to decrease.

  Thereby, when it is necessary to heat the heat generating apparatus 40, the temperature of the cooling water flowing into the heat generating apparatus 40 can be raised to heat the heat generating apparatus 40 reliably.

  When it is necessary for the control device 30 to cool the heat generating device 40, the flow rate of the cooling water flowing through the high-pressure side internal heat exchanger 22 decreases or the flow rate of the cooling water flowing through the low-pressure side internal heat exchanger 25 increases. Thus, the operation of the three-way valve 42 is controlled.

  Thereby, when it is necessary to cool the heat generating apparatus 40, the temperature of the cooling water flowing into the heat generating apparatus 40 can be lowered to reliably cool the heat generating apparatus 40.

(Fifth embodiment)
In the third embodiment, the cooling water circuit 12 includes the common pump 28, but in this embodiment, the cooling water circuit 12 includes the high-pressure side pump 43 and the low-pressure side pump 44 as illustrated in FIG. 7. The high pressure side pump 43 is disposed in the cooling water flow path on the low pressure side internal heat exchanger 25 side. The low-pressure side pump 44 is disposed in the cooling water flow path on the high-pressure side internal heat exchanger 22 side.

  The operation of the high-pressure side pump 43 and the low-pressure side pump 44 is controlled by the control device 30. The control device 30 controls the output ratio of the high-pressure side pump 43 and the low-pressure side pump 44 to cool the cooling water flow path on the high pressure side internal heat exchanger 22 side and the cooling water flow path on the low pressure side internal heat exchanger 25 side. Since the water flow ratio can be adjusted, the temperature of the cooling water flowing into the heat generating device 40 can be adjusted.

  The control device 30 intermittently drives the high-pressure side pump 43 and the low-pressure side pump 44 to control the time ratio of the intermittent operation, whereby the cooling water flow path and the low-pressure side internal heat exchanger on the high-pressure side internal heat exchanger 22 side are controlled. Since the cooling water flow ratio with the cooling water flow path on the 25th side can be adjusted, the temperature of the cooling water flowing into the heating device 40 can be adjusted.

  In the present embodiment, as shown in FIG. 8, in the heat exchanger 41 in which the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25 are integrated, the cooling water distribution tank 41 d is discharged from the high pressure side pump 43. The distributed cooling water is distributed to the cooling water circulation part 41c adjacent to the high pressure side refrigerant circulation part 41a, and the cooling water discharged from the low pressure side pump 44 is supplied to the cooling water circulation part adjacent to the low pressure side refrigerant circulation part 41b. To 41c. The cooling water collecting tank 41e includes cooling water that has flowed through a plurality of cooling water circulation portions 41c adjacent to the high-pressure side refrigerant circulation portion 41a, and cooling water that has flowed through the cooling water circulation portion 41c adjacent to the low-pressure side refrigerant circulation portion 41b. Spill separately.

(Sixth embodiment)
In this embodiment, as shown in FIGS. 9 to 12, the state in which the cooling water circulates between the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25, the high pressure side internal heat exchanger 22, and the low pressure The state in which the cooling water circulates between at least one of the side internal heat exchangers 25 and the heat generating device 40 can be switched. 9-12, illustration of the refrigerating cycle 11 is abbreviate | omitted.

  The cooling water circuit 12 includes a high pressure side channel 45, a low pressure side channel 46, and an equipment channel 47. The high pressure side flow path 45 is provided with the high pressure side internal heat exchanger 22 and the high pressure side pump 43. The low pressure side flow path 46 is provided with a low pressure side internal heat exchanger 25 and a low pressure side pump 44. A heat generating device 40 is disposed in the device flow path 47.

  One end of the device channel 47 is connected to the downstream end of the high-pressure channel 45 and the upstream end of the low-pressure channel 46. The other end of the device flow path 47 is connected to the cooling water flow upstream end of the high pressure side flow path 45 and the cooling water flow downstream end of the low pressure side flow path 46.

  A three-way valve 48 is disposed at a connection portion between the device flow path 47, the high pressure side flow path 45 and the low pressure side flow path 46.

  The three-way valve 48 switches the flow of cooling water as shown in FIGS. FIG. 10 shows a state where the low-pressure side internal heat exchanger 25 and the heat generating device 40 are connected. In this state, the waste heat of the heat generating device 40 can be absorbed by the low pressure side refrigerant of the low pressure side internal heat exchanger 25. That is, the waste heat of the heat generating device 40 can be used in the refrigeration cycle 11.

  FIG. 11 shows a state where the low-pressure side internal heat exchanger 25 and the high-pressure side internal heat exchanger 22 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity).

  FIG. 12 shows a state where the high-pressure side internal heat exchanger 22 and the heat generating device 40 are connected. In this state, the heat of the high-pressure side refrigerant in the high-pressure side internal heat exchanger 22 can be supplied to the heat generating device 40. That is, the heat generating device 40 can be heated using the waste heat of the refrigeration cycle 11.

  In the present embodiment, the three-way valve 48 includes a state in which cooling water circulates between the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25, and the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25. The state in which the cooling water circulates between at least one internal heat exchanger and the heat generating device 40 among the units 25 is switched.

  According to this, for example, when the heat load of the refrigeration cycle 11 is high, the effect of improving the refrigeration cycle performance / efficiency due to the internal heat exchange is great, so the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 When the heat load of the refrigeration cycle 11 is low, the effect of improving the refrigeration cycle performance / efficiency by the internal heat exchange is small, so the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 generate heat. It can be used for adjusting the temperature of the device 40 or recovering waste heat of the heat generating device 40.

  That is, the high-pressure-side internal heat exchanger 22 and the low-pressure-side internal heat exchanger 25 not only serve as internal heat exchangers but also serve to adjust the temperature of the heat generating device 40 and recover waste heat from the heat generating device 40. Therefore, the configuration can be simplified and the size of the apparatus can be reduced as compared with the case where devices that fulfill these roles are provided separately.

(Seventh embodiment)
In this embodiment, as shown in FIG. 13, the arrangement of the high-pressure pump 43 is different from that of the sixth embodiment.

  One end of the device flow path 47 is connected to the cooling water flow upstream end of the high pressure side flow path 45 and the cooling water flow upstream end of the low pressure flow path 46. The other end of the device channel 47 is connected to the cooling water flow downstream end of the high pressure channel 45 and the cooling water flow downstream end of the low pressure channel 46.

  The three-way valve 48 switches the flow of cooling water as shown in FIGS. FIG. 14 shows a state where the low-pressure side internal heat exchanger 25, the high-pressure side internal heat exchanger 22 and the heat generating device 40 are connected. In this state, the temperature of the heat generating device 40 can be adjusted with intermediate-temperature cooling water.

  By controlling the opening ratio of the three-way valve 48, the output ratio of the high-pressure side pump 43 and the low-pressure side pump 44, and the time ratio of intermittent operation, the cooling water on the high-pressure side internal heat exchanger 22 side and the low-pressure side internal heat exchange are controlled. Since the flow ratio with the cooling water on the side of the heater 25 can be adjusted, the temperature of the cooling water flowing into the heat generating device 40 can be adjusted.

  FIG. 15 shows a state where the low-pressure side internal heat exchanger 25 and the high-pressure side internal heat exchanger 22 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity).

  In the state shown in FIG. 15, the cooling water flows back through the high-pressure side pump 43, so that a pump that can rotate forward and reverse is used as the high-pressure side pump 43, or a bypass circuit that bypasses the high-pressure side pump 43 is provided. preferable.

(Eighth embodiment)
In the present embodiment, as shown in FIGS. 16 to 18, a first heat generating device 51, a second heat generating device 52, a first three-way valve 53 and a second three-way valve 54 are arranged in the cooling water circuit 12.

  The cooling water circuit 12 includes a first connection channel 55, a second connection channel 56, a first device channel 57, and a second device channel 58. The first heat generating device 51 is disposed in the first device channel 57. A second heat generating device 52 is disposed in the second device channel 58. The first heat generating device 51 and the second heat generating device 52 are devices that generate heat when operated.

  The first connection channel 55 connects the cooling water flow downstream end of the high pressure channel 45 and the cooling water upstream end of the low pressure channel 46. The second connection flow path 56 connects the cooling water flow upstream end of the high pressure side flow path 45 and the cooling water flow downstream end of the low pressure flow path 46.

  One end of the first device channel 57 is connected to a connection portion between the high-pressure side channel 45 and the first connection channel 55. The other end of the first device channel 57 is connected to a connection portion between the high-pressure side channel 45 and the second connection channel 56.

  One end of the second device flow path 58 is connected to a connection portion between the low pressure side flow path 46 and the first connection flow path 55. The other end of the second device flow path 58 is connected to a connection portion between the low pressure side flow path 46 and the second connection flow path 56.

  The first three-way valve 53 is disposed at the connection portion between the high-pressure channel 45 and the first device channel 57. The second three-way valve 54 is disposed at the connection portion between the low pressure side flow path 46 and the second device flow path 58.

  The first three-way valve 53 and the second three-way valve 54 switch the flow of cooling water as shown in FIGS.

  FIG. 17 shows a state where the high-pressure side internal heat exchanger 22 and the first heat generating device 51 are connected, and the low-pressure side internal heat exchanger 25 and the second heat generating device 52 are connected. In this state, the heat of the high-pressure side refrigerant of the high-pressure side internal heat exchanger 22 can be supplied to the first heat generating device 51, and the waste heat of the second heat-generating device 52 is absorbed by the low-pressure side refrigerant of the low-pressure side internal heat exchanger 25. it can. That is, the waste heat of the refrigeration cycle 11 can be used to heat the first heat generating device 51, and the waste heat of the second heat generation device 52 can be used in the refrigeration cycle 11.

  FIG. 18 shows a state where the low-pressure side internal heat exchanger 25 and the high-pressure side internal heat exchanger 22 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity).

(Ninth embodiment)
In the present embodiment, as shown in FIGS. 19 to 21, a two-way valve 59 is arranged instead of the first three-way valve 53 and the second three-way valve 54 of the eighth embodiment. The two-way valve 59 is disposed in the first connection channel 55.

  The two-way valve 59 switches the flow of cooling water as shown in FIGS. FIG. 20 shows a state where the high-pressure side internal heat exchanger 22 and the first heat generating device 51 are connected, and the low-pressure side internal heat exchanger 25 and the second heat generating device 52 are connected. In this state, the heat of the high-pressure side refrigerant of the high-pressure side internal heat exchanger 22 can be supplied to the first heat generating device 51, and the waste heat of the second heat-generating device 52 is absorbed by the low-pressure side refrigerant of the low-pressure side internal heat exchanger 25. it can. That is, the waste heat of the refrigeration cycle 11 can be used to heat the first heat generating device 51, and the waste heat of the second heat generation device 52 can be used in the refrigeration cycle 11.

  FIG. 21 shows a state where the low-pressure side internal heat exchanger 25, the high-pressure side internal heat exchanger 22, the first heat generating device 51, and the second heat generating device 52 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity). In this state, since the heat of the high-pressure side refrigerant of the high-pressure side internal heat exchanger 22 can be supplied to the first heat generating device 51 and the second heat generating device 52, the first heat generating device is utilized using the waste heat of the refrigeration cycle 11. 51 and the second heat generating device 52 can be heated.

(10th Embodiment)
In this embodiment, as shown to FIGS. 22-24, the air radiator 60 is arrange | positioned at the cooling water circuit 12 of the said 8th Embodiment. The air radiator 60 is a heat medium air heat exchanger that radiates heat of the cooling water to the air by exchanging heat between the cooling water and the air. The air blower 61 blows air to the air radiator 60.

  A connection flow path pump 62 is disposed in the first connection flow path 55. The operation of the connection flow path pump 62 is controlled by the control device 30.

  FIG. 22 shows a state where the high-pressure side internal heat exchanger 22, the low-pressure side internal heat exchanger 25, the first heat generating device 51, the second heat generating device 52, and the air radiator 60 are connected.

  In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity). In this state, since the heat of the high-pressure side refrigerant of the high-pressure side internal heat exchanger 22 can be supplied to the first heat generating device 51 and the second heat generating device 52, the first heat generating device is utilized using the waste heat of the refrigeration cycle 11. 51 and the second heat generating device 52 can be heated. In this state, the heat of the cooling water is radiated to the air in the air radiator 60.

  FIG. 23 shows a state where the high-pressure side internal heat exchanger 22, the low-pressure side internal heat exchanger 25, the first heat generating device 51, and the air radiator 60 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity). In this state, since the heat of the high-pressure side refrigerant of the high-pressure side internal heat exchanger 22 can be supplied to the first heat generating device 51, the first heat generating device 51 can be heated using the waste heat of the refrigeration cycle 11. In this state, the heat of the cooling water is radiated to the air in the air radiator 60.

  FIG. 24 shows a state where the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 are connected. In this state, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger 25 exchange heat through the cooling water of the cooling water circuit 12, so the enthalpy difference between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24. The cycle coefficient of performance (so-called COP) can be improved by expanding (that is, refrigerating capacity).

  In the present embodiment, the first three-way valve 53 and the second three-way valve 54 have a high-pressure side internal heat exchanger 22, a low-pressure side heat exchanger 25, a first heat generating device 51, and a second heat generation with respect to the air radiator 60. Cooling water is selectively circulated with at least one of the devices 52.

  Thereby, it can switch to various operation modes. For example, when the outside air temperature is low, the coolant can be absorbed from the outside air by circulating the cooling water between the air radiator 60 and the low-pressure heat exchanger 25.

  For example, when the first heat generating device 51 and the second heat generating device 52 generate a large amount of heat, the cooling water is circulated between the air radiator 60 and the first heat generating device 51 and the second heat generating device 52 to thereby generate the first heat generating device 51 and the second heat generating device 52. The efficiency of the refrigeration cycle 11 can be prevented from deteriorating by dissipating heat from the heat generating device 51 and the second heat generating device 52 to the outside air.

  For example, the cooling water is circulated between the air radiator 60 and the high-pressure side internal heat exchanger 22 during the maximum cooling, so that the heat of the high-pressure side refrigerant is dissipated to the outside air, thereby improving the efficiency of the refrigeration cycle 11. it can.

(Eleventh embodiment)
In the present embodiment, as shown in FIG. 25, the refrigeration cycle 11 has a refrigerant flow switching valve 65 and a cooling water refrigerant heat exchanger 66. The refrigerant flow switching valve 65 is a refrigerant flow switching unit that switches the refrigerant flow state in accordance with the air conditioning mode.

  The cooling water refrigerant heat exchanger 66 is a heat medium refrigerant heat exchanger that exchanges heat between the cooling water of the cooling water circuit 12 and the refrigerant. The cooling water refrigerant heat exchanger 66 is arranged on the refrigerant discharge side of the compressor 20 and the refrigerant inlet side of the condenser 21.

  The cooling water refrigerant heat exchanger 66 is formed with a first refrigerant inlet 66a, a second refrigerant outlet 66b, a first cooling water inlet 66c, and a second cooling water outlet 66d.

  Outside air is blown to the condenser 21 by the outdoor blower 67. The traveling wind can be applied to the condenser 21 during traveling of the vehicle. The outdoor blower 67 is a blower that blows outside air toward the condenser 21. The outdoor blower 67 is an electric blower that drives a fan with an electric motor.

  The condenser 21 includes a first air refrigerant heat exchange unit 211, a gas-liquid separation unit 212, and a second air refrigerant heat exchange unit 213. The first air refrigerant heat exchange unit 211 and the second air refrigerant heat exchange unit 213 are heat exchange core units that exchange heat between the refrigerant and the air, and include a refrigerant flow path through which the refrigerant flows and an air flow path through which the air flows. Have.

  The gas-liquid separation unit 212 has a gas-liquid separation space for separating the gas-liquid of the refrigerant. The gas-liquid separation unit 212 has a first refrigerant flow port 212a through which the refrigerant flows between the first air refrigerant heat exchange unit 211 and the first liquid refrigerant heat exchange unit 211. The gas-liquid separation unit 212 has a second refrigerant circulation port 212b through which refrigerant flows between the second air refrigerant heat exchange unit 213. The 1st refrigerant | coolant circulation port 212a is arrange | positioned rather than the 2nd refrigerant | coolant circulation port 212b at the gravity direction upper side.

  The first air refrigerant heat exchanger 211 is connected to the second refrigerant outlet 66 b of the cooling water refrigerant heat exchanger 66. Thereby, the condenser 21 and the cooling water refrigerant | coolant heat exchanger 66 are arrange | positioned in series with respect to a refrigerant | coolant flow. The second air refrigerant heat exchange unit 213 is connected to the expansion valve 23.

  The expansion valve 23 is a bidirectional expansion valve. The bidirectional expansion valve is an expansion valve that can expand the refrigerant under reduced pressure even when the refrigerant flows backward.

  The evaporator 24 includes a first coolant coolant heat exchanger 241, a gas-liquid separator 242, and a second coolant coolant heat exchanger 243. The 1st cooling water refrigerant | coolant heat exchange part 241 and the 2nd cooling water refrigerant | coolant heat exchange part 243 are heat exchange core parts which heat-exchange a cooling water and a refrigerant | coolant, the cooling medium flow through which a refrigerant | coolant flows, and a cooling water flow And a water flow path.

  The gas-liquid separation unit 242 has a gas-liquid separation space for separating the gas-liquid of the refrigerant. The gas-liquid separation unit 242 has a first refrigerant flow port 242a through which the refrigerant flows between the first cooling water refrigerant heat exchange unit 241. The gas-liquid separation unit 242 has a second refrigerant circulation port 242b through which the refrigerant flows between the second cooling water refrigerant heat exchange unit 243. The first refrigerant circulation port 242a is disposed on the lower side in the gravity direction than the second refrigerant circulation port 242b. The first coolant coolant heat exchange unit 241 is connected to the expansion valve 23.

  The refrigerant flow switching valve 65 has a refrigerant inlet 65a into which refrigerant flows, a refrigerant outlet 65b from which refrigerant flows out, a first inlet 65c and a second inlet 65d through which refrigerant flows.

  The refrigerant inlet 65 a is connected to the refrigerant discharge side of the compressor 20. The refrigerant outlet 65 b is connected to the refrigerant suction side of the compressor 20. The first inlet / outlet port 65c is connected to the first refrigerant inlet port 66a of the cooling water / refrigerant heat exchanger 66. The second inflow / outflow port 65d is connected to the second coolant coolant heat exchange unit 243 of the evaporator 24.

  As shown in FIG. 26, the refrigerant flow switching valve 65 has a state in which the refrigerant inlet 65a is connected to the first inlet 65c and the refrigerant outlet 65b is connected to the second inlet 65d, as shown in FIG. The state in which the refrigerant inlet 65a is connected to the second inlet / outlet 65d and the refrigerant outlet 65b is connected to the first inlet / outlet 65c is switched.

  When the air conditioning mode is the cooling mode, the refrigerant flow switching valve 65 switches to the refrigerant flow state shown in FIG. In other words, when the air conditioning mode is the cooling mode, the refrigerant flow switching valve 65 connects the refrigerant discharge port 20b of the compressor 20 and the cooling water refrigerant heat exchanger 66, and the refrigerant inlet port 20a of the compressor 20 The evaporator 24 is connected.

  The refrigerant flow switching valve 65 switches to the refrigerant flow state shown in FIG. 26 when the air conditioning mode is the heating mode. In other words, when the air-conditioning mode is the heating mode, the refrigerant flow switching valve 65 connects the refrigerant outlet 20b of the compressor 20 and the evaporator 24, and the refrigerant inlet 20a of the compressor 20 and the cooling water refrigerant heat. The switch 66 is connected.

  The high-pressure side internal heat exchanger 22 is disposed between the condenser 21 and the expansion valve 23. The low-pressure side internal heat exchanger 25 is disposed between the refrigerant outlet 65 b of the refrigerant flow switching valve 65 and the refrigerant inlet 20 a of the compressor 20.

  As shown in FIG. 27, the cooling water circuit 12 includes a first cooling water pump 68, a second cooling water pump 69, and a third cooling water pump 70.

  The first cooling water pump 68, the second cooling water pump 69, and the third cooling water pump 70 are electric pumps that suck and discharge the cooling water. The first cooling water pump 68, the second cooling water pump 69, and the third cooling water pump 70 may be belt-driven pumps that are driven by transmitting the driving force of the engine 21 through the belt.

  The coolant discharge sides of the first coolant pump 68, the second coolant pump 69, and the third coolant pump 70 are connected to the coolant inlet side of the upstream coolant flow switching valve 71. The cooling water suction side of the first cooling water pump 68, the second cooling water pump 69 and the third cooling water pump 70 is connected to the cooling water outlet side of the downstream cooling water flow switching valve 72.

  The cooling water circuit 12 includes a cooling water refrigerant heat exchanger 66, a high pressure side internal heat exchanger 22, an evaporator 24, a low pressure side internal heat exchanger 25, a cooler core 73, a heater core 74, a temperature control device 75, and waste heat recovery heat. An exchanger 76, an upstream side cooling water flow switching valve 71, and a downstream side cooling water flow switching valve 72 are arranged.

  The cooler core 73, the heater core 74, the temperature control device 75, and the waste heat recovery heat exchanger 76 are cooling water distribution devices (in other words, heat medium distribution devices) through which cooling water flows.

  The cooler core 73 is an air cooling heat exchanger (in other words, a heat medium air heat exchanger) that exchanges heat between cooling water and air blown into the vehicle interior space to cool the air blown into the vehicle interior space. is there. The cooler core 73 is a cold energy utilization device that utilizes the cold heat of the cooling water.

  In the cooler core 73, the cooling water absorbs heat from the air by sensible heat change. That is, in the cooler core 73, even if the cooling water absorbs heat from the air, the cooling water remains in a liquid phase and does not change phase.

  The heater core 74 is an air heating heat exchanger (in other words, a heat medium air heat exchanger) that heat-exchanges cooling air and air blown into the vehicle interior space to heat the air blown into the vehicle interior space. is there. The heater core 74 is a heat utilization device that utilizes the heat of the cooling water.

  In the heater core 74, the cooling water dissipates heat to the air by sensible heat change. That is, in the heater core 74, even if the cooling water radiates heat to the air, the cooling water remains in a liquid phase and does not change phase.

  The cooler core 73 and the heater core 74 are accommodated in a casing of an indoor air conditioning unit (not shown). An air passage through which air flows toward the vehicle interior is formed in the casing of the indoor air conditioning unit.

  The temperature control device 75 is an in-vehicle device whose temperature is adjusted by cooling water. The waste heat recovery heat exchanger 76 is a heat exchanger that recovers waste heat of various in-vehicle devices into cooling water.

  Cooling water refrigerant heat exchanger 66, evaporator 24, high pressure side internal heat exchanger 22, low pressure side internal heat exchanger 25, cooler core 73, heater core 74, temperature control device 75, and cooling water inlet of waste heat recovery heat exchanger 76 The side is connected to the coolant outlet side of the upstream coolant flow switching valve 71.

  Cooling water refrigerant heat exchanger 66, evaporator 24, high pressure side internal heat exchanger 22, low pressure side internal heat exchanger 25, cooler core 73, heater core 74, temperature control device 75, and cooling water outlet of waste heat recovery heat exchanger 76 The side is connected to the coolant inlet side of the downstream coolant flow switching valve 72.

  The upstream side cooling water flow switching valve 71 and the downstream side cooling water flow switching valve 72 are cooling water flow switching units that switch the cooling water flow state according to the air conditioning mode.

  The upstream side cooling water flow switching valve 71 and the downstream side cooling water flow switching valve 72 include a cooling water refrigerant heat exchanger 66, an evaporator 24, a high pressure side internal heat exchanger 22, a low pressure side internal heat exchanger 25, a cooler core 73, One of the first cooling water pump 68, the second cooling water pump 69, and the third cooling water pump 70 is selectively applied to each of the heater core 74, the temperature control device 75, and the waste heat recovery heat exchanger 76. Connect.

  That is, the upstream side cooling water flow switching valve 71 and the downstream side cooling water flow switching valve 72 include the cooling water refrigerant heat exchanger 66, the evaporator 24, the high pressure side internal heat exchanger 22, the low pressure side internal heat exchanger 25, the cooler core. 73, between the first cooling water pump 68 and the second cooling water pump 69, between the heater core 74, the temperature control device 75, and the waste heat recovery heat exchanger 76, and between the second cooling water pump 69. The state in which the cooling water circulates and the state in which the cooling water circulates between the third cooling water pump 70 are switched.

  The control device 30 includes a refrigerant flow switching valve 65, an upstream cooling water flow switching valve 71, a downstream cooling water flow switching valve 72, a first cooling water pump 68, a second cooling water pump 69, a third cooling water pump 70, and the like. Also controls the operation.

  Next, the operation in the above configuration will be described. When the air conditioning mode is the cooling mode, the control device 30 switches the refrigerant flow switching valve 65 as shown in FIG. As a result, the refrigerant flows in the order of the compressor 20, the cooling water refrigerant heat exchanger 66, the condenser 21, the high-pressure side internal heat exchanger 22, the expansion valve 23, the evaporator 24, the low-pressure side internal heat exchanger 25, and the compressor 20. Circulate.

  When the air conditioning mode is the cooling mode, the control device 30 circulates the cooling water between the first cooling water pump 68 and the evaporator 24, the cooler core 73, the temperature control device 75, and the waste heat recovery heat exchanger 76. Then, the cooling water circulates between the second cooling water pump 69, the cooling water refrigerant heat exchanger 66, and the heater core 74, and the third cooling water pump 70, the high pressure side internal heat exchanger 22, and the low pressure side internal heat exchanger. The upstream-side cooling water flow switching valve 71 and the downstream-side cooling water flow switching valve 72 are switched so that the cooling water circulates between the cooling water and the cooling water.

  Thus, in the cooling mode, the coolant coolant heat exchanger 66 and the condenser 21 function as a high-pressure side heat exchanger of the refrigeration cycle, and the evaporator 24 functions as a low-pressure side heat exchanger of the refrigeration cycle. That is, in the cooling water refrigerant heat exchanger 66 and the condenser 21, the high-pressure side refrigerant of the refrigeration cycle dissipates heat, and in the evaporator 24, the low-pressure side refrigerant of the refrigeration cycle absorbs heat. Therefore, the cooling water is heated by the cooling water refrigerant heat exchanger 66, and the cooling water is cooled by the evaporator 24.

  The cooling water cooled by the evaporator 24 cools the air blown into the vehicle interior by the cooler core 73. Thereby, the vehicle interior can be cooled. The cooling water cooled by the evaporator 24 absorbs heat from the temperature control device 75 and the waste heat recovery heat exchanger 76. Thereby, the temperature control device 75 can be cooled and the waste heat can be recovered by the waste heat recovery heat exchanger 76.

  The cooling water heated by the cooling water refrigerant heat exchanger 66 heats the air blown into the vehicle interior by the heater core 74. Thereby, the cold air cooled by the cooler core 73 can be reheated and can be cooled at a desired temperature.

  Since the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25 exchange heat via the cooling water, the enthalpy difference (that is, refrigeration capacity) between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24 is increased. Thus, the coefficient of performance of the cycle (so-called COP) can be improved.

  In the cooling mode, in the condenser 21, the refrigerant flows in the order of the first air refrigerant heat exchange unit 211, the gas-liquid separation unit 212, and the second air refrigerant heat exchange unit 213. The gas-liquid two-phase refrigerant heat-exchanged by the first air refrigerant heat exchange unit 211 flows into the gas-liquid separation unit 212 from the first refrigerant circulation port 212a. The refrigerant in the gas-liquid separation unit 212 flows out from the second refrigerant circulation port 212b to the second air refrigerant heat exchange unit 213.

  Since the first refrigerant circulation port 212a is disposed above the second refrigerant circulation port 212b in the gravitational direction, the gas-liquid separation of the refrigerant is performed by the gas-liquid separation unit 212, and the liquid-phase refrigerant becomes the gas-liquid separation unit 212. Accumulate at the bottom inside. Then, the liquid-phase refrigerant accumulated at the bottom in the gas-liquid separation unit 212 flows to the second air refrigerant heat exchange unit 213.

  Therefore, the 1st air refrigerant heat exchange part 211 functions as a condenser which condenses a refrigerant, and the 2nd air refrigerant heat exchange part 213 functions as a supercooler which raises the subcooling degree of a refrigerant.

  In the cooling mode, in the evaporator 24, the refrigerant flows in the order of the first cooling water refrigerant heat exchange unit 241, the gas-liquid separation unit 242, and the second cooling water refrigerant heat exchange unit 243. The mist-like gas-liquid two-phase refrigerant heat-exchanged by the first cooling water refrigerant heat exchange unit 241 flows into the gas-liquid separation unit 242 from the first refrigerant circulation port 242a. The refrigerant in the gas-liquid separation unit 242 flows out from the second refrigerant circulation port 242b to the second cooling water refrigerant heat exchange unit 243.

  Since the first refrigerant circulation port 242a is arranged below the second refrigerant circulation port 242b in the gravity direction, the gas-liquid separation unit 242 does not separate the gas-liquid of the mist-like refrigerant and is in a gas-liquid two-phase state. As it is, it flows to the second cooling water refrigerant heat exchanger 243.

  Therefore, the 1st cooling water refrigerant | coolant heat exchange part 241 and the 2nd cooling water refrigerant | coolant heat exchange part 243 function as an evaporator which evaporates a refrigerant | coolant.

  When the air conditioning mode is the heating mode, the control device 30 switches the refrigerant flow switching valve 65 as shown in FIG. As a result, the refrigerant flows in the order of the compressor 20, the evaporator 24, the expansion valve 23, the high-pressure side internal heat exchanger 22, the condenser 21, the cooling water refrigerant heat exchanger 66, the low-pressure side internal heat exchanger 25, and the compressor 20. Circulate.

  When the air conditioning mode is the heating mode, the control device 30 causes the cooling water to circulate between the first cooling water pump 68, the evaporator 24, and the heater core 74, and the second cooling water pump 69 and the high-pressure side internal heat. The upstream side cooling is performed so that the cooling water circulates between the exchanger 22, the cooling water refrigerant heat exchanger 66, the low pressure side internal heat exchanger 25, the cooler core 73, the temperature control device 75, and the waste heat recovery heat exchanger 76. The water flow switching valve 71 and the downstream cooling water flow switching valve 72 are switched.

  In the heating mode, the evaporator 24 functions as a high-pressure side heat exchanger of the refrigeration cycle, and the high-pressure side internal heat exchanger 22, the condenser 21, the coolant coolant heat exchanger 66, and the low-pressure side internal heat exchanger 25 are Functions as a low-pressure heat exchanger for the refrigeration cycle. That is, in the evaporator 24, the high-pressure side refrigerant of the refrigeration cycle dissipates heat, and in the high-pressure side internal heat exchanger 22, the condenser 21, the cooling water refrigerant heat exchanger 66, and the low-pressure side internal heat exchanger 25, the low-pressure side refrigerant of the refrigeration cycle. Absorbs heat.

  Accordingly, the cooling water is heated by the evaporator 24, and the cooling water is cooled by the high-pressure side internal heat exchanger 22, the condenser 21, the cooling water refrigerant heat exchanger 66, and the low-pressure side internal heat exchanger 25.

  The cooling water cooled by the high-pressure side internal heat exchanger 22, the cooling water refrigerant heat exchanger 66 and the low-pressure side internal heat exchanger 25 cools and dehumidifies the air blown into the vehicle interior by the cooler core 73. The cooling water heated by the evaporator 24 heats the air blown into the vehicle interior by the heater core 74. Thereby, the cold air cooled and dehumidified by the cooler core 73 can be heated by the heater core 74 and dehumidified and heated.

  The cooling water cooled by the high-pressure side internal heat exchanger 22, the cooling water refrigerant heat exchanger 66 and the low-pressure side internal heat exchanger 25 is absorbed by the temperature control device 75 and the waste heat recovery heat exchanger 76. Thereby, the temperature control device 75 can be cooled and the waste heat can be recovered by the waste heat recovery heat exchanger 76.

  In the heating mode, in the evaporator 24, the refrigerant flows in the order of the second cooling water refrigerant heat exchange unit 243, the gas-liquid separation unit 242, and the first cooling water refrigerant heat exchange unit 241. The gas-liquid two-phase refrigerant heat-exchanged in the second cooling water refrigerant heat exchange unit 243 flows into the gas-liquid separation unit 242 from the second refrigerant circulation port 242b. The refrigerant in the gas-liquid separation unit 242 flows out from the first refrigerant circulation port 242a to the first cooling water refrigerant heat exchange unit 241.

  Since the first refrigerant circulation port 242a is disposed below the second refrigerant circulation port 242b in the gravity direction, the gas-liquid separation of the refrigerant is performed by the gas-liquid separation unit 242, and the liquid-phase refrigerant is converted into the gas-liquid separation unit 242. Accumulate at the bottom inside. Then, the liquid-phase refrigerant accumulated at the bottom in the gas-liquid separation unit 242 flows to the first cooling water refrigerant heat exchange unit 241.

  Therefore, the 2nd cooling water refrigerant | coolant heat exchange part 243 functions as a condenser which condenses a refrigerant | coolant, and the 1st cooling water refrigerant | coolant heat exchange part 241 functions as a supercooler which raises the supercooling degree of a refrigerant | coolant.

  In the heating mode, in the condenser 21, the refrigerant flows in the order of the second air refrigerant heat exchange unit 213, the gas-liquid separation unit 212, and the first air refrigerant heat exchange unit 211. The mist-like gas-liquid two-phase refrigerant heat-exchanged by the second air refrigerant heat exchange unit 213 flows into the gas-liquid separation unit 212 from the second refrigerant circulation port 212b. The refrigerant in the gas-liquid separation unit 212 flows out from the first refrigerant circulation port 121a to the first air refrigerant heat exchange unit 211.

  Since the first refrigerant circulation port 212a is disposed above the second refrigerant circulation port 212b in the gravity direction, the gas-liquid separation unit 212 does not separate the gas-liquid of the mist-like refrigerant and is in a gas-liquid two-phase state. It flows into the 1st air refrigerant | coolant heat exchange part 211 as it is.

  Therefore, the 2nd air refrigerant heat exchange part 213 and the 1st air refrigerant heat exchange part 211 function as an evaporator which evaporates a refrigerant.

  When frosting occurs in the condenser 21 in the heating mode, the condenser 21 can be defrosted by switching to the cooling mode. That is, by switching to the cooling mode, the condenser 21 can be defrosted using the heat of the high-pressure side refrigerant in the refrigeration cycle.

  In the present embodiment, the refrigerant flow switching valve 65 is in a state where the condenser 21 is located upstream of the expansion valve 23 in the refrigerant flow and the evaporator 24 is located downstream of the expansion valve 23 in the refrigerant flow. And the state in which the condenser 21 is positioned downstream of the expansion valve 23 in the refrigerant flow and the evaporator 24 is positioned upstream of the expansion valve 23 in the refrigerant flow.

  The upstream side cooling water flow switching valve 71 and the downstream side cooling water flow switching valve 72 are connected to the high pressure side internal heat exchanger 22, the low pressure side internal heat exchanger 25, and the cooling water refrigerant heat exchanger 66. Switch the flow.

  Thereby, according to switching of the operation mode (namely, cooling mode and heating mode) of refrigerating cycle 11, high-pressure side internal heat exchanger 22, low-pressure side internal heat exchanger 25, refrigerant cooling water heat exchanger 66, cooling water, It is possible to appropriately control the heat exchange.

  In this embodiment, the cooling water circuit 12 includes the high-pressure side internal heat exchanger 22, the low-pressure side heat exchanger 25, the cooling water refrigerant heat exchanger 66, the temperature adjustment device 75, the waste heat recovery heat exchanger 76, and the cooler core 73. The cooling water is circulated between at least one of the heater cores 74.

  According to this, at least one of the high pressure side internal heat exchanger 22, the low pressure side heat exchanger 25 and the cooling water refrigerant heat exchanger 66, the temperature control device 75, the waste heat recovery heat exchanger 76, the cooler core 73 and the heater core 74. It is possible to perform heat management appropriately by exchanging heat between the two.

(Twelfth embodiment)
In the eleventh embodiment, the expansion valve 23 is a bidirectional expansion valve. However, in the present embodiment, the expansion valve 23 is a one-way expansion valve. The one-way expansion valve is an expansion valve that cannot expand the refrigerant under reduced pressure when the refrigerant is flowing backward.

  As illustrated in FIGS. 28 and 29, the refrigeration cycle apparatus 10 includes an expansion valve switching valve 77. Regardless of the air conditioning mode, the expansion valve switching valve 77 always sets the refrigerant flow direction to the expansion valve 23 in the same direction. That is, the expansion valve switching valve 77 makes the refrigerant flow directions in the expansion valve 23 the same in the cooling mode and the heating mode. The operation of the expansion valve switching valve 77 is controlled by the control device 30.

  The expansion valve switching valve 77 has a refrigerant inlet 77a into which refrigerant flows, a refrigerant outlet 77b from which refrigerant flows out, a first inlet 77c and a second inlet 77d through which refrigerant flows. .

  The refrigerant inlet 77a is connected to the refrigerant outlet 23a side of the expansion valve 23. The refrigerant outlet 77b is connected to the refrigerant inlet 23b side of the expansion valve 23. The first inflow / outflow port 77 c is connected to the condenser 21. The second inflow / outflow port 77d is connected to the first coolant coolant heat exchange unit 241 of the evaporator 24.

  As shown in FIG. 29, the expansion valve switching valve 77 has a state in which the refrigerant inlet 77a is connected to the second inlet / outlet 77d and the refrigerant outlet 77b is connected to the first inlet / outlet 77c, as shown in FIG. The refrigerant inlet 77a is connected to the first inlet 77c and the refrigerant outlet 77b is connected to the second inlet 77d.

  The high-pressure side internal heat exchanger 22 is disposed between the refrigerant outlet 77 b of the expansion valve switching valve 77 and the refrigerant inlet 23 b of the expansion valve 23.

  The expansion valve switching valve 77 switches the refrigerant flow as shown in FIG. 28 when the air conditioning mode is the cooling mode, and switches the refrigerant flow as shown in FIG. 29 when the air conditioning mode is the heating mode.

  Thereby, since the flow direction of the refrigerant in the expansion valve 23 is the same in the cooling mode and in the heating mode, even if the expansion valve 23 is a one-way expansion valve, the expansion valve 23 is in both the cooling mode and the heating mode. The refrigerant can be expanded under reduced pressure.

  When the air conditioning mode is the cooling mode, as shown in FIG. 28, the compressor 20, the cooling water refrigerant heat exchanger 66, the condenser 21, the high-pressure side internal heat exchanger 22, the expansion, as in the eleventh embodiment. The refrigerant circulates in the order of the valve 23, the evaporator 24, the low-pressure side internal heat exchanger 25, and the compressor 20.

  When the air conditioning mode is the cooling mode, the control device 30 controls the first cooling water pump 68, the evaporator 24, the cooler core 73, the temperature control device 75, and the waste heat recovery heat exchanger as in the eleventh embodiment. The cooling water circulates between the second cooling water pump 69, the cooling water refrigerant heat exchanger 66 and the heater core 74, and the other cooling water of the third cooling water pump 70. The upstream side cooling water flow switching valve 71 and the downstream side cooling water flow switching valve 72 are switched so that the cooling water circulates between the pump and the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25. Thereby, in the air_conditioning | cooling mode of this embodiment, it operate | moves similarly to the air_conditioning | cooling mode of the said 11th Embodiment.

  When the air-conditioning mode is the heating mode, as shown in FIG. 29, the compressor 20, the evaporator 24, the high-pressure side internal heat exchanger 22, the expansion valve 23, the condenser 21, the cooling water refrigerant heat exchanger 66, the low-pressure side The refrigerant circulates in the order of the internal heat exchanger 25 and the compressor 20.

  When the air conditioning mode is the heating mode, the control device 30 causes the cooling water to circulate between the first cooling water pump 68, the evaporator 24, and the heater core 74, and the second cooling water pump 69 and the cooling water refrigerant heat. The cooling water circulates between the exchanger 66, the cooler core 73, the temperature control device 75, and the waste heat recovery heat exchanger 76, and the third cooling water pump 70, the high-pressure side internal heat exchanger 22 and the low-pressure side internal heat exchanger are circulated. The upstream-side cooling water flow switching valve 71 and the downstream-side cooling water flow switching valve 72 are switched so that the cooling water circulates between the cooling water and the cooling water.

  In the heating mode, the evaporator 24 functions as a high-pressure side heat exchanger for the refrigeration cycle, and the cooling water refrigerant heat exchanger 66 and the condenser 21 function as a low-pressure side heat exchanger for the refrigeration cycle. That is, in the evaporator 24, the high-pressure side refrigerant of the refrigeration cycle dissipates heat, and in the cooling water refrigerant heat exchanger 66 and the condenser 21, the low-pressure side refrigerant of the refrigeration cycle absorbs heat. Therefore, the cooling water is heated by the evaporator 24, and the cooling water is cooled by the cooling water refrigerant heat exchanger 66.

  The cooling water cooled by the cooling water refrigerant heat exchanger 66 cools and dehumidifies the air blown into the vehicle interior by the cooler core 73. The cooling water heated by the evaporator 24 heats the air blown into the vehicle interior by the heater core 74. Thereby, the cold air cooled and dehumidified by the cooler core 73 can be heated and dehumidified and heated at a desired temperature.

  The cooling water cooled by the cooling water / refrigerant heat exchanger 66 absorbs heat from the temperature control device 75 and the waste heat recovery heat exchanger 76. Thereby, the temperature control device 75 can be cooled and the waste heat can be recovered by the waste heat recovery heat exchanger 76.

  Since the high pressure side internal heat exchanger 22 and the low pressure side internal heat exchanger 25 exchange heat through the cooling water, the enthalpy difference (that is, the refrigeration capacity) between the outlet side refrigerant and the inlet side refrigerant of the evaporator 24 is increased. , The coefficient of performance of the cycle (so-called COP) can be improved.

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

  (1) In each of the above embodiments, the cooling water is used as the cooling water circulating in the cooling water circuit 12, but various media such as oil may be used as the cooling water.

  Nanofluid may be used as the cooling water. 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 cooling water, the following working effects can be obtained in addition to the cooling effect using ethylene glycol (the effect of lowering the freezing point as in the so-called antifreeze solution).

  That is, the effect of improving the thermal conductivity in a specific temperature range, the effect of increasing the heat capacity of the cooling water, the effect of preventing the corrosion of the metal pipe and the deterioration of the rubber pipe, and the cooling water at a cryogenic temperature The effect which improves the fluidity | liquidity of can be acquired.

  Such effects vary 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.

  Moreover, since the heat capacity of the heat medium can be increased, the amount of heat stored in the heat medium itself can be increased. The amount of cold storage heat of the heat medium itself is the amount of cold storage heat by sensible heat.

  Even if the compressor 20 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. Motorization becomes possible.

  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, carbon nanotube (so-called CNT), graphene, graphite core-shell nanoparticle, Au nanoparticle-containing CNT, and the like can be used as the constituent atoms of the nanoparticle. The graphite core-shell type nanoparticle is a particle body having a structure such as a carbon nanotube surrounding the atom.

  (2) In the refrigeration cycle 11 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, and the like are used. It may be used.

  (3) The refrigeration cycle 11 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.

12 Cooling water circuit (heat medium circuit)
20 Compressor 21 Condenser (High pressure side heat exchanger)
22 High-pressure side internal heat exchanger 23 Expansion valve (decompression unit)
24 Evaporator (Low pressure side heat exchanger)
25 Low-pressure side internal heat exchanger 28 Pump (flow control unit)
30 Control device (control unit)

Claims (14)

A compressor (20) for sucking and discharging refrigerant;
A high pressure side heat exchanger (21) for exchanging heat of the refrigerant discharged from the compressor;
A high pressure side internal heat exchanger (22) for exchanging heat between the refrigerant heat exchanged by the high pressure side heat exchanger and the heat medium;
A decompression section (23) for decompressing the refrigerant heat-exchanged by the high-pressure side internal heat exchanger;
A low pressure side heat exchanger (24) for exchanging heat of the refrigerant decompressed by the decompression unit;
A low-pressure side internal heat exchanger (25) for exchanging heat between the refrigerant heat-exchanged by the low-pressure side heat exchanger and the heat medium heat-exchanged by the high-pressure side internal heat exchanger;
A refrigeration cycle apparatus comprising: a flow rate adjusting unit (28, 42, 43, 44, 68, 69, 70) for adjusting a flow rate of the heat medium flowing through the high pressure side internal heat exchanger and the low pressure side internal heat exchanger. A heat medium circuit (12) for circulating the heat medium in the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger;
In the heat medium circuit, a temperature control device (40, which is temperature-controlled by the heat medium heat-exchanged by the high-pressure side internal heat exchanger and the heat medium heat-exchanged by the low-pressure side internal heat exchanger The refrigeration cycle apparatus according to claim 1, wherein 51, 52, and 75) are disposed.   A state in which the heat medium circulates between the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger; and at least one internal heat of the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger The refrigeration cycle apparatus according to claim 2, further comprising a switching unit (48, 53, 54, 59, 71, 72) that switches between a state in which the heat medium circulates between the exchanger and the temperature control device.   The refrigerant that flows into the high-pressure side internal heat exchanger when the temperature difference between the refrigerant that flows into the high-pressure side internal heat exchanger and the refrigerant that flows into the low-pressure side internal heat exchanger becomes a predetermined value or less. Of the heat medium flowing through the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger as compared to before the temperature difference between the refrigerant flowing into the low-pressure side internal heat exchanger becomes equal to or less than a predetermined value. The refrigeration cycle apparatus according to any one of claims 1 to 3, further comprising a control unit (30) for controlling the operation of the flow rate adjusting unit so that the flow rate decreases.   When the temperature of the refrigerant discharged from the compressor is equal to or higher than a predetermined temperature, the high-pressure side internal heat exchanger is compared with the case before the temperature of the refrigerant discharged from the compressor is equal to or higher than a predetermined temperature. The refrigeration according to any one of claims 1 to 3, further comprising a control unit (30) for controlling the operation of the flow rate adjusting unit so that the flow rate of the heat medium flowing through the low-pressure side internal heat exchanger decreases. Cycle equipment. The decompression unit has a temperature sensing unit that detects the degree of superheat of the refrigerant that has flowed out of the low-pressure-side internal heat exchanger,
The control part (30) which controls operation of the flow control part so that the heat carrier may flow into the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger when the compressor is started. The refrigeration cycle apparatus according to any one of 1 to 3.   When a predetermined time has elapsed since the compressor was started, the high-pressure side internal heat exchanger and the low-pressure side internal heat exchanger are compared with before the predetermined time has elapsed since the compressor was started. The refrigeration cycle apparatus according to claim 6, further comprising a control unit (30) that controls the operation of the flow rate adjusting unit so that the flow rate of the heat medium flowing through the flow rate decreases.   The refrigeration cycle apparatus according to any one of claims 1 to 7, wherein the high-pressure side heat exchanger and the low-pressure side heat exchanger are arranged in series with each other in the flow of the heat medium. The flow rate control unit can independently control the flow rate of the heat medium flowing through the high-pressure side internal heat exchanger and the flow rate of the heat medium flowing through the low-pressure side internal heat exchanger,
When it is necessary to heat the temperature control device, the flow rate of the heat medium flowing through the high pressure side internal heat exchanger is increased, or the flow rate of the heat medium flowing through the low pressure side internal heat exchanger is decreased. The refrigeration cycle apparatus according to claim 2 or 3, further comprising a control unit (30) for controlling the operation of the flow rate adjusting unit. The flow rate control unit can independently control the flow rate of the heat medium flowing through the high-pressure side internal heat exchanger and the flow rate of the heat medium flowing through the low-pressure side internal heat exchanger,
When it is necessary to cool the temperature control device, the flow rate of the heat medium flowing through the high-pressure side internal heat exchanger is decreased, or the flow rate of the heat medium flowing through the low-pressure side internal heat exchanger is increased. The refrigeration cycle apparatus according to claim 2 or 3, further comprising a control unit (30) for controlling the operation of the flow rate adjusting unit. The high-pressure side internal heat exchanger and the low-pressure side heat exchanger are integrated by having a common tank portion (41d, 41e) that performs at least one of distribution and collection of the heat medium,
The refrigeration cycle apparatus according to any one of claims 1 to 10, wherein the flow rate adjusting unit adjusts the flow rate of the heat medium flowing through the tank unit (41d, 41e). A heat medium air heat exchanger (60) for exchanging heat between the air blown into the passenger compartment and the heat medium;
The switching unit selectively transfers the heat medium to or from at least one of the high-pressure side internal heat exchanger, the low-pressure side heat exchanger, and the temperature control device with respect to the heat medium air heat exchanger. The refrigeration cycle apparatus according to claim 3 circulated. A heat medium refrigerant heat exchanger (66) for exchanging heat between the refrigerant discharged from the compressor and flowing into the high pressure side heat exchanger and the heat medium;
A state in which the high-pressure side heat exchanger is located upstream of the decompression unit in the refrigerant flow and the low-pressure side heat exchanger is located downstream of the decompression unit in the refrigerant flow; Refrigerant flow switching for switching between a state in which the side heat exchanger is positioned downstream of the decompression unit in the refrigerant flow and the state of the low pressure side heat exchanger upstream of the decompression unit in the refrigerant flow Part (65),
2. A heat medium flow switching unit (71, 72) that switches the flow of the heat medium with respect to the high pressure side internal heat exchanger, the low pressure side internal heat exchanger, and the heat medium refrigerant heat exchanger. The refrigeration cycle apparatus described. A heat medium distribution device (75, 76) through which the heat medium flows;
A heat medium air heat exchanger (73, 74) for exchanging heat between the heat medium and air blown into the passenger compartment;
Circulating the heat medium between the high-pressure side internal heat exchanger, the low-pressure side heat exchanger and the heat medium refrigerant heat exchanger and at least one of the heat medium circulation device and the heat medium air heat exchanger The refrigeration cycle apparatus according to claim 13, further comprising a heat medium circuit (12) to be operated.

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