JP2018004159A - Refrigeration cycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a refrigeration cycle capable of maintaining a refrigerant input to an evaporator in a supercooling state.SOLUTION: A refrigeration cycle includes: a compressor 1 for compressing a gas phase refrigerant supplied from a gas liquid separator 4; a radiator 2 for radiating heat from the refrigerant compressed by the compressor; an evaporator 5 for evaporating a liquid phase refrigerant from the gas liquid separator; an ejector that forms a drive current by injecting, from a refrigerant injection section, the refrigerant supplied from the radiator 2 and forms a suction current of the refrigerant supplied from the evaporator, mixing the refrigerants with each other and supplying the mixture to the gas liquid separator 4; and a supercooling control section 7 for causing the liquid phase refrigerant to be supplied to the evaporator to become a supercooling state.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a refrigeration cycle including an ejector for energy saving.

As this type of refrigeration cycle, for example, a refrigeration cycle described in Patent Document 1 has been proposed.
In the refrigeration cycle described in Patent Document 1, a high-pressure refrigerant compressed by a compressor is radiated by a radiator, the refrigerant is depressurized by a decompression unit, and the refrigerant is further depressurized by a nozzle portion of the ejector. The refrigerant supplied from the evaporator is sucked into the refrigerant suction port by the refrigerant flow injected from the section.

Japanese Patent No. 3322263

By the way, in the refrigeration cycle, the liquid phase refrigerant separated by the gas-liquid separator is decompressed by the decompressor and then evaporated by the evaporator to exchange heat with the air, thereby exhibiting the refrigerating capacity. For this reason, when the cooling degree of the refrigerant | coolant of an evaporator inlet is insufficient, it will not be in a supercooling state, but a refrigerating capacity will fall compared with a supercooling state.
Therefore, the present invention has been made paying attention to the problems of the above-described conventional example, and an object thereof is to provide a refrigeration cycle capable of maintaining the refrigerant supplied to the evaporator in a supercooled state.

  In order to solve the above-described problems, an aspect of the refrigeration cycle according to the present invention includes a compressor that compresses a gas-phase refrigerant supplied from a gas-liquid separator, and a radiator that dissipates heat from the refrigerant compressed by the compressor. And an evaporator for evaporating the liquid-phase refrigerant supplied from the gas-liquid separator, a refrigerant supplied from the radiator is jetted from a nozzle as a driving flow, and a refrigerant supplied from the evaporator is used as a suction flow. And a supercooling adjusting unit for bringing the liquid phase refrigerant supplied to the evaporator into a supercooled state.

  According to one aspect of the present invention, the liquid-phase refrigerant separated by the gas-liquid separator supplied to the evaporator is adjusted so as to maintain the supercooled state by the supercooling adjustment unit. A decrease in ability can be suppressed.

It is a whole lineblock diagram showing a 1st embodiment of a refrigerating cycle concerning the present invention. It is a Mollier diagram which shows the state of the refrigerant | coolant of 1st Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant when not providing the supercooling adjustment part of 1st Embodiment. It is a whole block diagram which shows the modification of the 1st Embodiment of this invention. It is a Mollier diagram which shows the state of the refrigerant | coolant of the modification of 1st Embodiment. It is a whole block diagram which shows 2nd Embodiment of the refrigerating cycle which concerns on this invention. It is a Mollier diagram which shows the state of the refrigerant | coolant of 2nd Embodiment. It is a whole block diagram which shows 3rd Embodiment of the refrigerating cycle which concerns on this invention. It is a schematic diagram which shows the winding state of the refrigerant | coolant piping to the ejector of 3rd Embodiment. It is a Mollier diagram which shows the state of the refrigerant | coolant of 3rd Embodiment. It is a whole block diagram which shows 4th Embodiment of the refrigerating cycle which concerns on this invention. It is sectional drawing which shows the ejector applied to 4th Embodiment. It is a whole block diagram which shows the 5th Embodiment of this invention.

Next, an embodiment of the present invention will be described with reference to the drawings. In the following description of the drawings, the same or similar parts are denoted by the same or similar reference numerals. However, it should be noted that the drawings are schematic, and the relationship between the thickness and the planar dimensions, the ratio of the thickness of each layer, and the like are different from the actual ones. Therefore, specific thicknesses and dimensions should be determined in consideration of the following description. Moreover, it is a matter of course that portions having different dimensional relationships and ratios are included between the drawings.
Further, the embodiment described below exemplifies an apparatus and a method for embodying the technical idea of the present invention, and the technical idea of the present invention is the material, shape, structure, The layout is not specified as follows. The technical idea of the present invention can be variously modified within the technical scope defined by the claims described in the claims.

[First Embodiment]
First, a first embodiment of a refrigeration cycle representing one aspect of the present invention will be described with reference to FIGS. 1 and 2.
As shown in FIG. 1, the refrigeration cycle according to the present invention includes a compressor 1, a radiator 2, an ejector 3, a gas-liquid separator 4, and an evaporator 5. This refrigeration cycle is used for a refrigeration showcase, a vending machine, an air conditioner, and the like.
The compressor 1 compresses the gas-phase refrigerant and raises the temperature and pressure, and can be selected from compressors such as a reciprocating compressor, a rotary compressor, and a scroll compressor. The refrigerant compressed by the compressor 1 is supplied to the radiator 2 through the refrigerant pipe RP1.
The radiator 2 radiates the refrigerant compressed by the compressor 1 by heat exchange with the outside air. The refrigerant radiated by the radiator 2 is supplied to the ejector 3 through the refrigerant pipe RP2 with the throttle unit 6 serving as a decompression unit interposed.

The ejector 3 ejects the refrigerant decompressed by the throttle portion 6 of the refrigerant pipe RP2 from the nozzle 3a to generate a driving flow, and sucks the refrigerant evaporated in the evaporator 5 by the driving flow from the suction port 3b. In addition, the ejector 3 mixes the driving flow and the suction flow with the refrigerant mixing unit 3c, increases the pressure with the diffuser unit 3d, and outputs it. The refrigerant mixed in the ejector 3 is supplied to the gas-liquid separator 4 through the refrigerant pipe RP3.
The gas-liquid separator 4 separates the refrigerant supplied from the ejector 3 into a gas phase refrigerant and a liquid phase refrigerant. The gas-phase refrigerant separated by the gas-liquid separator 4 is supplied to the compressor 1 through the refrigerant pipe RP4.

Further, the liquid phase refrigerant separated by the gas-liquid separator 4 passes through the refrigerant pipe RP5, and passes through the refrigerant pipe RP5, the supercooling adjusting unit 7 provided in the middle of the refrigerant pipe RP5, and the decompression unit 8 serving as the throttle unit. 5 is supplied. The supercooling adjustment unit 7 is supplied as a cooling heat medium for the other part of the liquid-phase refrigerant supplied from the gas-liquid separator 4.
In this cooling heat medium, the liquid-phase refrigerant output from the gas-liquid separator 4 passes through the refrigerant pipe RP5a branched from the refrigerant pipe RP5, and is depressurized by the decompression section 9 serving as a throttle section provided in the middle thereof. Thus, a low-temperature cooling heat medium is obtained.

The supercooling adjustment unit 7 is configured such that the cooling heat medium and the liquid phase refrigerant flow in parallel flow, cool the liquid phase refrigerant with the cooling heat medium, and bring the liquid phase refrigerant into a supercooled state. . The cooling heat medium output from the supercooling adjustment unit 7 is joined to the refrigerant pipe RP6 output from the evaporator 5 through the refrigerant pipe RP7.
The evaporator 5 cools the air by expanding the liquid phase refrigerant decompressed by the decompression unit 8 and exchanging heat with the air. At this time, it is preferable that heat exchange is performed so that the gas-phase refrigerant has a predetermined degree of superheat when passing through the evaporator 5. The refrigerant evaporated in the evaporator 5 is supplied to the suction port 3b of the ejector 3 through the refrigerant pipe RP6.

Next, the operation of the first embodiment will be described with reference to the Mollier diagram of FIG. Symbols A to K indicated by black circles in FIG. 2 indicate the state of the refrigerant at the positions of symbols A to K indicated by black circles in FIG.
First, the gas-liquid separator 4 separates the gas-liquid two-phase refrigerant supplied from the ejector 3 through the refrigerant pipe RP3 into a gas-phase refrigerant and a liquid-phase refrigerant. The separated gas-phase refrigerant is in a state represented by point A in FIG. This gas-phase refrigerant changes from point A to point B in FIG.

Next, the refrigerant is radiated by the heat radiator 2 by heat exchange with the outside air. In this heat radiation process, the pressure is changed to change from point B to point C in FIG. The radiated refrigerant is decompressed by the decompression unit 6 and is ejected from the nozzle 3a of the ejector 3 as a driving flow. During this time, the refrigerant changes from point C to point D in FIG.
In the ejector 3, the refrigerant from the evaporator 5 is sucked as a suction flow by the driving flow, and the driving flow and the suction flow are mixed. The refrigerant rises in pressure in the diffuser portion 3 c of the ejector 3. It changes to E point of 2.

The refrigerant flow output from the diffuser portion 3c is separated into a gas phase refrigerant and a liquid phase refrigerant by the gas-liquid separator 4. At this time, the state of the gas-phase refrigerant returns from point E in FIG. 2 to point A on the saturated vapor line, and the state of the liquid-phase refrigerant changes from point E in FIG. 2 to point F before the saturated liquid line.
A part of the liquid-phase refrigerant output from the gas-liquid separator 4 passes through the refrigerant pipe RP5a branched from the refrigerant pipe RP5 and is decompressed by the decompression unit 9 to become a low-temperature cooling heat medium. 2 and changes heat from point K to point J in FIG. 2 by exchanging heat with the liquid-phase refrigerant supplied from the gas-liquid separator 4 in the supercooling adjustment unit 7.

On the other hand, the other part of the liquid-phase refrigerant output from the gas-liquid separator 4 is heat-exchanged with the cooling heat medium in the supercooling adjustment unit 7 and changes from the point F to the point G in FIG. . The refrigerant in the supercooled state is decompressed by the decompression unit 8 and changes from the G point to the H point in FIG. This refrigerant is evaporated by the evaporator 5 and changes from the H point to the I point in FIG.
The refrigerant output from the evaporator is sucked from the suction port 3a of the ejector 3 through the refrigerant pipe RP6 and mixed at the point J in FIG.
As described above, in the refrigeration cycle using the ejector 3 according to the present embodiment, the refrigerant output from the gas-liquid separator 4 and supplied to the evaporator 5 through the decompression unit 8 is cooled by the supercooling adjustment unit 7. The supercooled refrigerant is cooled to a supercooled state, and the supercooled refrigerant is decompressed by the decompression unit 8 and then supplied to the evaporator 5 to be evaporated. Then, the evaporated refrigerant is supplied to the suction port 3 b of the ejector 3.

For this reason, according to this embodiment, the refrigerating capacity of the refrigerating cycle becomes the enthalpy difference ΔH between the point G and the point I, and a large refrigerating capacity can be exhibited.
On the other hand, when the supercooling adjusting unit 7, the branch pipe RP5a, and the pressure reducing unit 9 are not provided, the point F and the point G are the same as shown in the Mollier diagram of FIG. From the point, the pressure is reduced by the decompression unit 8 to become the H point. Then, by evaporating with the evaporator 5, it changes from the H point to the I point, and then changes to the J point.
Therefore, when the supercooling adjustment unit 7, the branch pipe RP5a, and the decompression unit 9 are not provided, the refrigerant cooling to be supplied to the evaporator 5 becomes less and is supplied to the evaporator 5, so that the enthalpy of the present embodiment. It is reduced to an enthalpy difference ΔH ′ that is smaller than the difference ΔH. For this reason, the refrigerating capacity is reduced.

  In the first embodiment, the case where the supercooling adjustment unit 7 is a parallel flow type has been described. However, the present invention is not limited to this, and as shown in FIG. The phase refrigerant and the cooling heat medium may be configured to flow in opposite directions. In this case, the degree of cooling of the liquid phase refrigerant by the cooling heat medium can be improved. Therefore, as shown in the Mollier diagram of FIG. 5, the degree of supercooling of the liquid refrigerant can be increased from the point G to the point G ″, and the enthalpy difference ΔH is increased to a larger enthalpy difference ΔH ″ for freezing. The ability can be further improved.

[Second Embodiment]
Next, a second embodiment of the present invention will be described with reference to FIGS.
In the second embodiment, the gas-liquid separator is directly cooled and the supercooled liquid phase refrigerant is supplied to the evaporator.
That is, in the second embodiment, as shown in FIG. 6, the supercooling adjustment unit 7 in the first embodiment described above is omitted, and instead, the outlet side of the decompression unit 9 is connected to the refrigerant pipe RP6 through the refrigerant pipe RP7. It is connected to. Here, the refrigerant pipe RP7 is supercooled having an internal heat exchange function by being wound spirally from the bottom side so that the intermediate part covers the periphery of the liquid-phase refrigerant storage part 4a on the lower end side of the gas-liquid separator 4 The adjustment part 11 is formed.

About another structure, it has the structure similar to 1st Embodiment mentioned above, the same code | symbol is attached | subjected to the corresponding part with FIG. 1, and the detailed description is abbreviate | omitted.
According to the second embodiment, the liquid-phase refrigerant output from the liquid-phase refrigerant storage unit 4a of the gas-liquid separator 4 is decompressed by the decompression unit 9 to become a low-temperature cooling heat medium, and passes through the refrigerant pipe RP7. The cooling adjustment unit 11 spirally passes around the liquid-phase refrigerant storage unit 4a of the gas-liquid separator 4 and then merges with the refrigerant pipe RP6.
For this reason, in the supercooling adjustment unit 11, the liquid-phase refrigerant storage unit 4 a of the gas-liquid separator 4 is cooled by the low-temperature cooling heat medium output from the decompression unit 9. Therefore, the liquid phase refrigerant stored in the liquid phase refrigerant flow section 4a of the gas-liquid separator 4 is heat-exchanged with the cooling heat medium and cooled to a supercooled state. The liquid refrigerant cooled to the supercooled state is decompressed by the decompression unit 8 and then supplied to the evaporator 5. On the other hand, the cooling heat medium after heat exchange with the liquid refrigerant in the liquid refrigerant storage unit 4a of the gas-liquid separator 4 merges with the refrigerant pipe RP6.

Accordingly, when the state of the refrigerant is represented by the Mollier diagram shown in FIG. 7, the liquid phase refrigerant separated from the gas-liquid separator 4 is cooled to the supercooled state in the liquid phase refrigerant storage section 4a. It changes from the point E to the supercooled state at the point F. The supercooled liquid-phase refrigerant is depressurized by the depressurization unit 8 and changes from the F point to the H point in FIG. Thereafter, the liquid-phase refrigerant is evaporated by the evaporator 5 to change from the H point to the I point in FIG. 7, and is sucked from the suction port 3a of the ejector 3 at the J point in FIG.
On the other hand, the liquid-phase refrigerant output from the liquid-phase refrigerant storage unit 4a of the gas-liquid separator 4 and supplied to the decompression unit 9 is changed from the F point to the K point in FIG. Then, it merges with the refrigerant from the evaporator 5 and is sucked from the suction port 3a of the ejector 3 at the point J in FIG.

  As described above, according to the second embodiment, the cooling heat medium decompressed by the decompression unit 9 spirally winds the liquid-phase refrigerant reservoir 4a of the gas-liquid separator 4 by the refrigerant pipe RP7, and then the refrigerant pipe RP6. To join. For this reason, the liquid phase refrigerant stored in the liquid phase refrigerant reservoir 4a is cooled to the supercooled state only by spirally winding the refrigerant pipe RP5a around the liquid phase refrigerant reservoir 4 of the gas-liquid separator 4. The supercooling adjustment unit 11 can be configured. Therefore, it is not necessary to provide the supercooling adjustment unit 7 as in the first embodiment, and the number of parts can be reduced by this amount.

[Third Embodiment]
Next, a third embodiment of the present invention will be described with reference to FIGS.
In the third embodiment, the liquid-phase refrigerant output from the gas-liquid separator is cooled to a supercooled state at the outer periphery of the ejector and supplied to the evaporator.
That is, in the third embodiment, as shown in FIGS. 8, 9, and 10, the supercooling adjustment unit 7 and the decompression unit 9 in the first embodiment described above are omitted, and gas-liquid separation is performed instead. After the refrigerant pipe RP5 connecting the evaporator 4 and the evaporator 5 is spirally wound around the refrigerant mixing unit 3d where the drive flow and suction flow of the ejector 3 are mixed to form the supercooling adjustment unit 21 It is connected to the evaporator 5 with a decompression unit 8 interposed.

According to the third embodiment, the supercooling adjustment unit 21 is configured by winding the refrigerant pipe RP5 connecting the gas-liquid separator 4 and the evaporator 5 around the refrigerant mixing unit 3d of the ejector 3. The refrigerant mixing unit 3d has the lowest pressure in the refrigeration cycle. In other words, in the refrigeration cycle, the refrigerant mixing section 3c is at the lowest temperature, so that the liquid output from the gas-liquid separator 4 can be obtained by spirally winding the refrigerant pipe RP5 around the outer periphery of the refrigerant mixing section 3c. The phase refrigerant can be cooled to a supercooled state.
That is, as represented by the Mollier diagram shown in FIG. 10, the refrigerant output from the ejector 3 is supplied to the gas-liquid separator 4 and separated into a gas phase refrigerant and a liquid phase refrigerant. The separated liquid phase refrigerant changes from point E to point F in FIG. 10 and is heat-exchanged with the refrigerant mixing part 3d of the ejector 3 in the middle of the refrigerant pipe RP5, so that point F to point G in FIG. Changes to a supercooled state.

The supercooled liquid-phase refrigerant is decompressed by the decompression unit 8 to change from the point G in FIG. 10 to the point H, is evaporated by the evaporator 5, and changes from the point H to the point I in FIG. Thereafter, the air is sucked into the suction port 3a of the ejector 3 at the point I in FIG.
Thus, according to the third embodiment, the liquid-phase refrigerant output from the gas-liquid separator 4 is supercooled by heat exchange around the refrigerant mixing portion 3d of the ejector 3 at which the refrigeration cycle has the lowest temperature. Cooled to state. For this reason, the refrigerant pipe RP5 through which the liquid-phase refrigerant output from the gas-liquid separator 4 is passed is simply wound around the refrigerant mixing portion 3d of the ejector 3 in a spiral manner so that the supercooled state can be achieved. Therefore, since the decompression unit 9 in the second embodiment is not required, the liquid-phase refrigerant output from the gas-liquid separator 4 and supplied to the evaporator 5 can be cooled to a supercooled state with a small number of parts. And a cheaper refrigeration cycle can be constructed.

[Fourth Embodiment]
Next, the 4th Embodiment of this invention is described with FIG.11 and FIG.12.
In the fourth embodiment, the liquid-phase refrigerant output from the gas-liquid separator is cooled to a supercooled state by passing through the ejector and supplied to the evaporator.
That is, in the fourth embodiment, as shown in FIG. 11, the supercooling adjustment unit 30 is formed in the ejector 3. The supercooling adjusting unit 30 includes a through refrigerant passage 31 formed on the base side of the nozzle 3a of the ejector 3 in a direction crossing the axial direction. A refrigerant suction port 3b communicating with the nozzle 3a is formed on the refrigerant mixing portion 3c side of the through refrigerant passage 31.
As shown in FIG. 11, the refrigerant pipe RP5 to which the liquid-phase refrigerant of the gas-liquid separator 4 is supplied is divided into two in the middle to form refrigerant pipes RP5b and RP5c, and the open end of the refrigerant pipe RP5b is the through refrigerant passage. The open end of the refrigerant pipe RP5 c is connected to the other end of the through refrigerant passage 31.

According to the fourth embodiment, the supercooling adjusting unit 30 divides the refrigerant pipe RP5 that connects the gas-liquid separator 4 and the evaporator 5, and this divided unit is connected through the through refrigerant passage 31 formed in the ejector 3. Has been. Therefore, the through refrigerant passage 31 itself functions as a heat exchanger, and the liquid phase refrigerant supplied from the gas-liquid separator 4 is heat-exchanged with the refrigerant from the radiator 2 passing through the nozzle 3a and cooled to a supercooled state. The The supercooled liquid phase refrigerant is decompressed by the decompression unit 8 and input to the evaporator 5.
Also in the fourth embodiment, since the decompression unit 9 in the second embodiment is not required, the liquid-phase refrigerant output from the gas-liquid separator 4 and supplied to the evaporator 5 with a small number of parts is supercooled. It can cool to a state and can constitute a cheaper refrigeration cycle.

[Fifth Embodiment]
Next, a fifth embodiment of the present invention will be described with reference to FIG.
In the fifth embodiment, in the configuration of the first embodiment described above, the throttle unit 6 is an ejector variable throttle unit 41, the decompression unit 8 is an evaporator variable throttle unit 42, and the decompression unit 9 is a heat exchanger. The variable aperture unit 43 is used. In addition, a temperature sensor 44 that detects the outside air temperature of the radiator 2, a refrigerant temperature sensor 45 that detects the refrigerant temperature at the outlet of the radiator 2, and a first refrigerant temperature sensor 46 that detects the refrigerant temperature at the inlet of the evaporator 5. And a second refrigerant temperature sensor 47 for detecting the refrigerant temperature at the outlet of the evaporator 5 is provided.
And each variable throttle | throttle part 41-43, each temperature sensor 44-47, and the compressor 1 are connected to the control apparatus 48, and each variable is based on the temperature detection of each temperature sensor 44-47 by this control apparatus 48. The throttle amount of the throttle parts 41 to 43 is controlled and the rotation speed of the compressor 1 is controlled. Here, the control device 48 includes an evaporator temperature difference control unit 49 that controls the refrigerant temperature difference between the inlet and the outlet of the evaporator 5, and an evaporation temperature that controls the evaporation temperature of the liquid-phase refrigerant supplied to the evaporator 5. And a control unit 50.

The evaporator temperature difference control unit 49 refers to the outside air temperature detected by the temperature sensor 44 or the outlet refrigerant temperature of the radiator 2 detected by the refrigerant temperature sensor 45, and the refrigerant temperature difference between the inlet and outlet of the evaporator 5 is constant. The throttle amounts of the ejector variable throttle unit 41 and the evaporator variable throttle unit 42 are controlled so that
The evaporation temperature control unit 50 calculates the optimum evaporation temperature at that time in a state where the evaporator temperature difference control unit 49 controls the refrigerant temperature difference between the inlet and the outlet of the evaporator to be constant, and the first refrigerant temperature It is determined whether or not the refrigerant temperature detected by the sensor 46 exceeds the optimum evaporation temperature, and it is determined whether or not the refrigerant supplied from the gas-liquid separator 4 is in a supercooled state. When the determination result indicates that the refrigerant temperature detected by the first refrigerant temperature sensor 46 exceeds the optimum evaporation temperature, it is determined that the liquid-phase refrigerant temperature is not in the supercooled state, and the throttle of the heat exchanger variable throttle unit 43 is determined. Control to reduce the amount. For this reason, the temperature of the cooling heat medium supplied to the supercooling adjustment unit 7 is lowered, and the liquid-phase refrigerant heat-exchanged by the supercooling adjustment unit 7 is controlled to a supercooled state.

On the other hand, when the determination result indicates that the refrigerant temperature detected by the first refrigerant temperature sensor 46 is below the optimum evaporating temperature, control is performed so that the throttle amount of the heat exchanger variable throttle unit 43 is increased. For this reason, the temperature of the cooling heat medium supplied to the supercooling adjustment unit 7 is increased, and the liquid phase refrigerant heat-exchanged by the supercooling adjustment unit 7 is controlled to the optimum evaporation temperature. At this time, when the liquid-phase refrigerant is maintained at the optimum evaporation temperature, the flow rate can be controlled to be zero with the throttle amount of the heat exchanger variable throttle portion 43 being maximized.
As described above, according to the fifth embodiment, the supercooled state of the liquid-phase refrigerant from the gas-liquid separator 4 supplied to the evaporator 5 can be controlled to the optimum evaporation temperature, which is exhibited by the evaporator 5. The refrigeration efficiency can be optimally controlled, and fluctuations in the refrigeration efficiency can be suppressed by controlling the refrigerant temperature difference between the inlet and the outlet of the evaporator 5 to be constant.

  DESCRIPTION OF SYMBOLS 1 ... Compressor, 2 ... Radiator, 3 ... Ejector, 3a ... Nozzle, 3b ... Suction port, 3c ... Refrigerant mixing part, 3d ... Diffuser part, 4 ... Gas-liquid separator, 5 ... Evaporator, 6 ... Throttling part , 7 ... Supercooling adjustment unit, 8, 9 ... Decompression unit, 11, 21, 30 ... Supercooling adjustment unit, 31 ... Through refrigerant passage, 41 ... Variable throttle unit for ejector, 42 ... Variable throttle unit for evaporator, 43 ... Variable throttle section for heat exchanger, 44 ... temperature sensor, 45 ... refrigerant temperature sensor, 46 ... first refrigerant temperature sensor, 47 ... second refrigerant temperature sensor, 48 ... control device, 49 ... evaporator temperature difference control section, 50 ... Evaporation temperature controller

Claims (8)

A compressor for compressing the gas-phase refrigerant supplied from the gas-liquid separator;
A radiator that dissipates the gas-phase refrigerant compressed by the compressor;
An evaporator for evaporating the liquid-phase refrigerant supplied from the gas-liquid separator;
An ejector that injects a refrigerant supplied from the radiator from a refrigerant injection unit into a driving flow, mixes the refrigerant as a suction flow and supplies the refrigerant to the gas-liquid separator; ,
A refrigeration cycle, comprising: a supercooling adjustment unit configured to supercool the liquid phase refrigerant supplied to the evaporator.   The supercooling adjustment unit exchanges heat between the liquid-phase refrigerant supplied from the gas-liquid separator to the evaporator and the cooling heat medium obtained by reducing the pressure of the liquid-phase refrigerant supplied from the gas-liquid separator by the decompression unit. The refrigeration cycle according to claim 1, further comprising a heat exchanger.   3. The refrigeration cycle according to claim 2, wherein in the heat exchanger, a liquid-phase refrigerant and a cooling heat medium are passed in parallel flow.   3. The refrigeration cycle according to claim 2, wherein in the heat exchanger, a liquid-phase refrigerant and a cooling heat medium are passed as counterflows.   The supercooling adjustment unit performs heat exchange by winding a medium flow path to which a cooling heat medium obtained by reducing the pressure of the liquid-phase refrigerant supplied from the gas-liquid separator by the decompression unit is wound around the gas-liquid separator. The refrigeration cycle according to claim 1.   The supercooling adjustment unit includes a heat exchange unit in which a refrigerant pipe is wound around the refrigerant mixing unit of the ejector, and one end of the heat exchange unit is connected to a liquid phase refrigerant discharge port of the gas-liquid separator. 2. The refrigeration cycle according to claim 1, wherein the other end of the heat exchange unit is connected to the evaporator, and a supercooled refrigerant is supplied to the evaporator.   The subcooling adjusting unit has a through refrigerant pipe that intersects the driving flow formed in the ejector, and connects one end of the through refrigerant pipe to a liquid phase refrigerant discharge port of the gas-liquid separator, 2. The refrigeration cycle according to claim 1, wherein the other end of the pipe is connected to the evaporator, and a supercooled refrigerant is supplied to the evaporator. A temperature sensor that detects an outside air temperature, a first refrigerant temperature sensor that detects an inlet refrigerant temperature of the evaporator, a second refrigerant temperature sensor that detects an outlet refrigerant temperature of the evaporator, and the gas-liquid separator. A variable throttle portion for a heat exchanger using a liquid phase refrigerant supplied to the internal heat exchanger as a cooling heat medium, and a variable throttle portion for an evaporator that controls the liquid phase refrigerant supplied from the internal heat exchanger to the evaporator And an ejector variable throttle that controls decompression of the refrigerant supplied from the radiator to the ejector, and temperature detection values of the temperature sensor, the first refrigerant temperature sensor, and the second refrigerant temperature sensor. A control device for controlling the variable throttle for the heat exchanger, the variable throttle for the evaporator, and the variable throttle for the ejector;
The control device controls the evaporator variable throttle unit and the ejector variable throttle unit so that the temperature difference between the inlet refrigerant temperature and the outlet refrigerant temperature of the evaporator becomes constant with reference to the outside air temperature. 2. The apparatus according to claim 1, further comprising: a difference control unit; and an evaporation temperature control unit that controls the heat exchanger throttle unit so that the refrigerant temperature detected by the first refrigerant temperature sensor becomes an optimum evaporation temperature. The refrigeration cycle described in 1.

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