JP2002022295A - Ejector cycle - Google Patents

Abstract

PROBLEM TO BE SOLVED: To assure a required refrigerating capacity even in the case wherein thermal load of an evaporator decreases so that the flow rate is lowered. SOLUTION: When the flow rate (thermal load) is not less than a specified value, an ON/OFF valve 710 is opened to suck a refrigerant in an evaporator 300 by an ejector 400, and when the flow rate (thermal load) is less than the specified value, a decompression valve 700 is fully opened and simultaneously the ON/OFF valve 710 is closed to supply the refrigerant the pressure of which is reduced by a nozzle 410 (ejector 400) to the evaporator 300. Thus, an operation same as that of a vapor compression type refrigeration cycle is performed. By this method, even when the flow rate (thermal load) is less than a specified value, the flow rate of the refrigerant flowing in the evaporator 300 becomes a flow rate proportional to the flow rate discharged from the compressor 100 without being influenced by the flow speed of the refrigerant. Thus, a required refrigerating capacity is surely assured even in the case the thermal load of the evaporator 300 becomes small and the flow rate of the refrigerant is decreased.

Description

DETAILED DESCRIPTION OF THE INVENTION

[0001]

BACKGROUND OF THE INVENTION The present invention relates to a method for reducing the pressure of a refrigerant, expanding the refrigerant, and sucking a vapor-phase refrigerant evaporated in an evaporator.
The present invention relates to an ejector cycle having an ejector that converts expansion energy into pressure energy to increase a suction pressure of a compressor.

[0002]

2. Description of the Related Art An ejector applied to an ejector cycle converts pressure energy of a high-pressure refrigerant flowing out of a radiator such as a condenser into velocity energy to decompress and expand the refrigerant as described in Japanese Patent No. 2838917. Nozzle, a mixing section that sucks the gas-phase refrigerant evaporated in the evaporator by the high-speed refrigerant flow injected from the nozzle,
And a diffuser that converts velocity energy into pressure energy while increasing the pressure of the refrigerant while mixing the refrigerant injected from the nozzle and the refrigerant sucked from the evaporator.

[0003]

By the way, in the ejector, the gas-phase refrigerant in the evaporator is sucked by the high-speed refrigerant flow jetted from the nozzle, and the amount of the sucked refrigerant flows out of the radiator. The mass flow rate (hereinafter, abbreviated as flow rate) of the refrigerant flowing into the nozzle increases and the flow rate of the refrigerant injected from the nozzle increases, and the flow rate decreases.

However, since the change in the amount of suction refrigerant does not change linearly with the change in the flow rate, the heat load on the evaporator decreases, and as the flow rate decreases, the amount of suction refrigerant increases more than the decrease in flow rate. And the required refrigerating capacity cannot be secured.

[0005] In view of the above points, the present invention provides a method for reducing the heat load in the evaporator and reducing the flow rate.
The purpose is to secure the necessary refrigeration capacity.

[0006]

According to the present invention, in order to achieve the above object, according to the first aspect of the present invention, a compressor (100) for sucking and compressing a refrigerant and a compressor discharged from the compressor (100) are provided. A radiator (200) for cooling the refrigerant and at least one evaporator (300, 310) for evaporating the refrigerant
And an ejector (400) having a nozzle (410) for reducing and expanding the high-pressure refrigerant flowing out of the radiator (200).
In the ejector cycle including the radiator (20)
0), when the mass refrigerant flow rate flowing out of the ejector (400) is equal to or greater than a predetermined value,
Evaporator (300) by high-speed refrigerant flow injected from the
When the mass refrigerant flow rate flowing out of the radiator (200) is smaller than a predetermined value, the refrigerant decompressed by the nozzle (410) is removed by the evaporator (300, 31).
0) to evaporate the refrigerant.

Accordingly, when the mass refrigerant flow rate is less than the predetermined value, the refrigerant depressurized by the nozzle (410) is supplied to the evaporator (30, 310) to evaporate the refrigerant, so that the evaporator (300, 310) The mass flow rate of the refrigerant flowing through the inside of the compressor (10
The flow rate is proportional to the flow rate discharged from 0).

Therefore, even when the heat load is reduced and the mass refrigerant flow rate is reduced, the required refrigerating capacity can be reliably ensured.

According to the second aspect of the present invention, the compressor (100) for sucking and compressing the refrigerant, the radiator (200) for cooling the refrigerant discharged from the compressor (100), and the evaporator (200) for evaporating the refrigerant. 300) and an ejector cycle (400) having a nozzle (410) for decompressing and expanding the high-pressure refrigerant flowing out of the radiator (200), the mass refrigerant flow rate flowing out of the radiator (200) is equal to or more than a predetermined value. In the case of, in the ejector (400), the vapor-phase refrigerant evaporated in the evaporator (300) is sucked by the high-speed refrigerant flow injected from the nozzle (410),
While mixing the suctioned refrigerant and the refrigerant injected from the nozzle (410), the velocity energy of the refrigerant is converted into pressure energy to increase the pressure of the refrigerant, and the increased pressure refrigerant is supplied to the suction side of the compressor (100). Spill the radiator (2
When the mass refrigerant flow rate flowing out of the nozzle (410) is less than the predetermined value, the refrigerant decompressed by the nozzle (410) is discharged to the evaporator (30)
0) to evaporate the refrigerant.

Accordingly, when the mass refrigerant flow rate is less than the predetermined value, the refrigerant decompressed by the nozzle (410) is supplied to the evaporator (300) to evaporate the refrigerant, so that the refrigerant flows through the evaporator (300). The mass flow rate of the refrigerant is proportional to the flow rate discharged from the compressor (100) without being affected by the flow rate of the refrigerant.

Therefore, even when the heat load on the evaporator (300) is reduced and the flow rate of the refrigerant is reduced, the required refrigeration capacity can be reliably ensured.

When the heat load at which the mass refrigerant flow rate is equal to or more than a predetermined value is large, the expansion energy is converted into pressure energy by the ejector (400) to convert the expansion energy into pressure energy.
Since the suction pressure of 0) is increased, the required refrigeration capacity can be exhibited while reducing the power consumption of the compressor (100).

As described above, according to the ejector cycle of the present invention, the required refrigerating capacity can be ensured even when the heat load on the evaporator (300) decreases and the flow rate of the refrigerant decreases. When the heat load is large, the required refrigeration capacity can be exhibited while reducing the power consumption of the compressor (100).

According to the third aspect of the present invention, the compressor (100) for sucking and compressing the refrigerant, the radiator (200) for cooling the refrigerant discharged from the compressor (100), and the first, 2 evaporator (300, 310) and radiator (2
An ejector (400) having a nozzle (410) for decompressing and expanding the high-pressure refrigerant flowing out of the ejector (400) when the mass refrigerant flow rate flowing out of the radiator (200) is equal to or more than a predetermined value. The vapor-phase refrigerant evaporated in the first evaporator (300) is sucked by the high-speed refrigerant flow injected from the (410), and when the mass refrigerant flow rate flowing out of the radiator (200) is less than a predetermined value, the ejector ( 400) at the first evaporator (31).
The refrigerant decompressed by the nozzle (410) is supplied to the second evaporator (310) to evaporate the refrigerant without sucking the refrigerant from 0).

Thus, when the mass refrigerant flow rate is less than the predetermined value, the refrigerant decompressed by the nozzle (410) is supplied to the second evaporator (310) without sucking the refrigerant from the first evaporator (300). As a result, the mass flow rate of the refrigerant flowing through the second evaporator (300) is proportional to the flow rate discharged from the compressor (100) without being affected by the flow rate of the refrigerant. .

Therefore, even when the heat load on the evaporator (300) is reduced and the flow rate of the refrigerant is reduced, the required refrigerating capacity can be reliably ensured.

According to the fourth aspect of the invention, when the air blown into the room is cooled by the ejector cycle according to the third aspect, the second evaporator (310).
Is desirably disposed upstream of the first evaporator (300) in the air flow.

Incidentally, the reference numerals in parentheses of the above means are examples showing the correspondence with specific means described in the embodiments described later.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS (First Embodiment)
FIG. 1 is a schematic view of an ejector cycle (vehicle air conditioner) according to the present embodiment, in which an ejector cycle according to the present invention is applied to a vehicle air conditioner.

Reference numeral 100 denotes a compressor for sucking and compressing the refrigerant, and reference numeral 200 denotes a condenser (radiator) for cooling and condensing the refrigerant by exchanging heat between the refrigerant discharged from the compressor 100 and outdoor air.

The compressor 100 is driven by an electric motor (not shown). When the heat load on the evaporator 300 described later increases, the rotation speed of the compressor 100 is increased to increase the rotation speed of the compressor 100. When the flow rate of the refrigerant discharged from the compressor 100 is increased, while the heat load on the evaporator 300 is reduced, the rotation speed of the compressor 100 is reduced to decrease the flow rate of the refrigerant discharged from the compressor 100.

Incidentally, in this embodiment, the heat load in the evaporator 300 is estimated from the air temperature immediately after passing through the evaporator 300.

Reference numeral 300 denotes an evaporator which exhibits a refrigerating ability by exchanging heat between the air blown into the room and the liquid-phase refrigerant to evaporate the liquid-phase refrigerant.
This is an ejector that decompresses and expands the refrigerant flowing out of the evaporator, sucks the gas-phase refrigerant evaporated in the evaporator 300, and converts the expansion energy into pressure energy to increase the suction pressure of the compressor 100.

Here, the ejector 400 converts the pressure energy (pressure head) of the high-pressure refrigerant flowing out of the condenser 200 into velocity energy (velocity head) to decompress and expand the refrigerant. Evaporator 30 by the refrigerant flow (jet flow)
The mixing unit 420 that sucks the vapor-phase refrigerant evaporated at 0, and converts the velocity energy into pressure energy while mixing the refrigerant injected from the nozzle 410 and the refrigerant sucked from the evaporator 300 to increase the pressure of the refrigerant. It is composed of a diffuser 430 and the like.

Reference numeral 441 denotes an inlet into which the refrigerant flowing out of the condenser 200 flows, and 442 denotes an inflow port of the evaporator 30.
It is a communication port that communicates with zero, and is an outlet that allows the refrigerant to flow out to the gas-liquid separation 600 side.

Reference numeral 600 denotes a gas-liquid separator for storing the refrigerant into which the refrigerant flowing out of the ejector 400 flows, separates the refrigerant into the gas-phase refrigerant and the liquid-phase refrigerant, and stores the refrigerant. The refrigerant is sucked into the compressor 100,
The separated liquid-phase refrigerant is sucked into the evaporator 300 side.

Reference numeral 700 denotes a gas-liquid separator 600 to an evaporator 30.
The decompressor 700 is a decompressor (throttling means) for decompressing the refrigerant flowing through the refrigerant to zero. 2 (not to depressurize the refrigerant)
It can be adjusted in stages.

Reference numeral 710 denotes an on-off valve for opening and closing a refrigerant passage connecting the refrigerant outlet of the ejector 400 (diffuser 430) and the gas-liquid separator 60. ), And 820 is a blower that blows cooling air to the condenser 200.

Next, the operation of the ejector cycle according to this embodiment will be described.

1. Normal operation mode (see FIG. 2) This operation mode is executed when the mass flow rate (hereinafter, referred to as a refrigerant flow rate) of the refrigerant flowing out of the condenser 200 and flowing into the nozzle 410 (the ejector 400) is equal to or more than a predetermined value. Specifically, the compressor 100 is operated in a state in which the on-off valve 710 is opened and the opening of the pressure reducing valve 700 is reduced to generate a predetermined pressure loss. In the present embodiment, the compressor 10
The refrigerant flow rate is estimated from the number of rotations of zero.

In this mode, the gas-liquid separation 600
The refrigerant sucked and compressed from the compressor is discharged from the compressor 100, condensed in the condenser 200, and ejected by the ejector 400.
(Nozzle 410).

The high-pressure refrigerant flowing into the ejector 400 has its pressure energy converted into velocity energy at the nozzle 410 and is jetted into the mixing section 420 as a low-pressure jet stream. For this reason, the gas-phase refrigerant in the evaporator 300 is sucked into the ejector 400 from the communication port 442, so that the sucked gas-phase refrigerant and the jet flow merge in the mixing section 420, and thereafter, the mixed refrigerant Is pressurized by the diffuser 430 and flows out toward the gas-liquid separation 600.

Here, the ejector 40 is connected through the communication port 442.
The refrigerant sucked into the chamber is not only a gas-phase refrigerant evaporated in the evaporator 300 but is not a gas-phase two-phase refrigerant depending on the operation state (heat load) of the cycle. Is also possible.

On the other hand, the evaporator 300
The liquid-phase refrigerant in the gas-liquid separator 600 flows into the evaporator 300 because the gas-phase refrigerant in the liquid is sucked. At this time, the refrigerant flowing from the gas-liquid separator 600 to the evaporator 300 is decompressed by the decompressor 700, flows into the evaporator 300, and exchanges heat with air blown into the room to evaporate.

FIG. 3 shows p in the normal operation mode.
FIG. 3 is a -h diagram, in which the numbers shown in FIG. 3 indicate the state of the refrigerant at the positions of the numbers shown in FIG. 2.

2. Low-load operation mode (see FIG. 4) This operation mode is a mode that is executed when the flow rate of refrigerant flowing out of the condenser 200 and flowing into the nozzle 410 (ejector 400) is less than a predetermined value. The compressor 100 is operated with the on-off valve 710 closed and the pressure reducing valve 700 fully opened.

Thus, the high-temperature and high-pressure refrigerant discharged from the compressor 100 is condensed by the condenser 200 and then flows into the ejector 400. And the ejector 400
The refrigerant flowing into the evaporator 300 is depressurized by the nozzle 410, flows through the communication port 422, flows into the evaporator 300, and then evaporates by exchanging heat with air blown into the room in the evaporator 300 to evaporate. The gas flows into the gas-liquid separator 600 via 700.

FIG. 5 is a ph diagram in the low load operation mode, and the numbers shown in FIG. 5 indicate the state of the refrigerant at the positions of the numbers shown in FIG. And as is clear from FIG. 5, in the low load operation mode,
Exhibits refrigeration capacity with the same behavior as a normal vapor compression refrigeration cycle.

Next, the features of this embodiment will be described.

According to the present embodiment, when the flow rate of the refrigerant flowing into the nozzle 410 is less than the predetermined value, the refrigerant decompressed by the nozzle 410 is supplied to the mixing section 420 and the diffuser 430.
Since the refrigerant is supplied to the evaporator 300 to evaporate the refrigerant without being injected to the side, the mass flow rate of the refrigerant flowing through the evaporator 300 is not affected by the flow velocity of the jet flow,
The flow rate is proportional to the flow rate discharged from the compressor 100.

Therefore, even when the heat load on the evaporator 300 is reduced and the flow rate of the refrigerant is reduced, the required refrigerating capacity can be reliably ensured.

When the heat load at which the flow rate of the refrigerant flowing into the nozzle 410 exceeds a predetermined value is large, the expansion energy is converted into pressure energy by the ejector 400 to increase the suction pressure of the compressor 100. 100
Required refrigeration capacity (cooling capacity) while reducing power consumption
Can be demonstrated.

As described above, according to the ejector cycle of the present embodiment, even when the heat load on the evaporator 300 is reduced and the flow rate of the refrigerant is reduced, the necessary refrigerating capacity can be ensured. On the other hand, when the heat load is large, the required refrigeration capacity (cooling capacity) can be exhibited while reducing the power consumption of the compressor 100.

(Second Embodiment) In this embodiment, as shown in FIG. 6, the ejector cycle according to the first embodiment (see FIG. 1) is omitted, and the ejector 400 and the gas-liquid A second evaporator 310 is provided between the second evaporator 310 and the separator 600.
And reducing the pressure of the refrigerant flowing from the gas-liquid separator 600 to the evaporator 300 in place of the pressure reducing valve 700, and closing the refrigerant passage connecting the gas-liquid separator 600 and the evaporator 300. Is provided with an electromagnetic valve 720 which can be switched to a case where the flow of the air is blocked.

Hereinafter, the evaporator 300 will be referred to as the first evaporator 3.
00, and the evaporator 310 is referred to as a second evaporator 310.

Next, the operation of this embodiment will be described.

1. Normal operation mode (see FIG. 7) This operation mode is performed by the nozzle 410 (ejector 400).
This mode is executed when the flow rate of the refrigerant flowing into the solenoid valve is equal to or more than a predetermined value. Specifically, a state in which the opening degree of the solenoid valve 720 is adjusted so that a predetermined pressure loss occurs in the solenoid valve 720 To operate the compressor 100.

In this mode, the refrigerant sucked and compressed from the gas-liquid separator 600 by the compressor 100 is discharged from the compressor 100 and condensed by the condenser 200.
It flows into the ejector 400 (nozzle 410).

The high-pressure refrigerant that has flowed into the ejector 400 has its pressure energy converted into velocity energy at the nozzle 410 and is jetted into the mixing section 420 as a low-pressure jet stream. For this reason, the gas-phase refrigerant in the evaporator 300 is sucked into the ejector 400 from the communication port 442, so that the sucked gas-phase refrigerant and the jet flow merge in the mixing section 420, and thereafter, the mixed refrigerant Is pressurized by the diffuser 430 and flows through the second evaporator 310 to flow into the gas-liquid separator 600.

On the other hand, the first evaporator 3
00, the gas-phase refrigerant in the gas-liquid separator 600 is sucked.
The liquid refrigerant inside flows into the first evaporator 300. At this time, the refrigerant flowing from the gas-liquid separator 600 to the first evaporator 300 is decompressed by the solenoid valve 720,
00, and exchanges heat with the air blown into the room to evaporate.

Since the refrigerant flowing out of the ejector 400 is in a gas-liquid two-layer state, the liquid-phase refrigerant also evaporates in the second evaporator 310 to generate a refrigerating capacity, but the refrigerant is pressurized by the diffuser 430. Therefore, the pressure in the second evaporator 310 is higher than that in the first evaporator 300. Therefore,
In the present embodiment, the second evaporator 310 whose evaporating temperature is high
Is disposed on the upstream side of the air flow from the first evaporator 300, and the air blown into the room is efficiently cooled by both the evaporators 300 and 310.

2. Low load operation mode (see FIG. 8) This operation mode is a mode executed when the flow rate of the refrigerant flowing out of the condenser 200 and flowing into the nozzle 410 (ejector 400) is less than a predetermined value. The compressor 100 is operated while the solenoid valve 720 is closed.

Thus, the high-temperature and high-pressure refrigerant discharged from the compressor 100 is condensed by the condenser 200, flows into the ejector 400, and is depressurized by the nozzle 410. At this time, since the electromagnetic valve 720 is closed, the refrigerant ejected from the nozzle 410 flows through the mixing unit 420 and the diffuser 430 without sucking the refrigerant from the first evaporator 300, and flows through the second evaporator 310. Into the chamber and evaporate by exchanging heat with the air blown into the room.
Flow into 00.

Next, the features of this embodiment will be described.

According to the present embodiment, when the flow rate of the refrigerant flowing into the nozzle 410 is less than the predetermined value, the first evaporator 30
Since the refrigerant decompressed by the nozzle 410 is supplied to the second evaporator 310 to evaporate the refrigerant without sucking the refrigerant from 0, the mass flow rate of the refrigerant flowing through the second evaporator 300 is equal to the jet flow. The flow rate is proportional to the flow rate discharged from the compressor 100 without being affected by the flow velocity.

Therefore, even when the heat load on the evaporator 300 is reduced and the flow rate of the refrigerant is reduced, the required refrigerating capacity can be ensured.

As described above, according to the ejector cycle of the present embodiment, even when the heat load on the evaporator 300 is reduced and the flow rate of the refrigerant is reduced, the necessary refrigerating capacity is ensured. On the other hand, when the heat load is large, the required refrigeration capacity (cooling capacity) can be exhibited while reducing the power consumption of the compressor 100.

Note that the present embodiment is not limited to those shown in FIGS.
0 and the second evaporator 310 may be integrated, or the first and second evaporators 300 and 310 and the ejector 400 may be integrated.

(Other Embodiments) In the above embodiment, the pressure reducing valve 70
0 and the solenoid valve 720 adjust the opening in two stages, but the present invention is not limited to this, and 3
It is good also as multi-stage (stepless) more than a stage.

Further, the application of the present invention is not limited to a vehicle air conditioner, but may be applied to other devices such as a home air conditioner, a building air conditioner and a refrigerator.

By the way, according to the present invention, when the heat load at which the flow rate of the refrigerant is equal to or higher than the predetermined flow rate is relatively large, the refrigerant is decompressed and expanded to suck the vapor-phase refrigerant evaporated by the evaporator, and the expansion energy is reduced to the pressure energy. When the heat load at which the refrigerant flow rate is less than the predetermined flow rate is relatively small, the nozzle 410 of the ejector 400 is operated.
Function as a simple vapor compression refrigeration cycle by functioning as a simple pressure reducing means. Therefore, it is necessary to switch the ejector cycle and the normal vapor compression refrigeration cycle according to the refrigerant flow rate (heat load). However, the configuration of the present invention is not limited to the above-described embodiment as long as it is possible.

In the above embodiment, the nozzle 410
Is a fixed type having a fixed opening, but a variable nozzle capable of variably controlling the nozzle opening may be used. In this case, it is desirable to reduce the nozzle opening in accordance with the decrease in the refrigerant flow rate (heat load).

In the above-described embodiment, the pressure on the high pressure side (discharge side of the compressor 100) is lower than the critical pressure of the refrigerant. However, the pressure on the high pressure side exceeds the critical pressure of the refrigerant. It can also be applied to supercritical cycles.

In the above embodiment, the compressor 100
Is driven by an electric motor, but the present invention is not limited to this, and may be driven by an engine (internal combustion engine). Further, the type of the compressor 100 (for example, a fixed capacity type, a variable capacity type, a piston type, a scroll type, or the like) does not matter.

[Brief description of the drawings]

FIG. 1 is a schematic diagram of an ejector cycle according to a first embodiment of the present invention.

FIG. 2 is a schematic diagram illustrating a refrigerant flow in a normal operation mode in the ejector cycle according to the first embodiment of the present invention.

FIG. 3 is a ph diagram in a normal operation mode in the ejector cycle according to the first embodiment of the present invention.

FIG. 4 is a schematic diagram illustrating a refrigerant flow in a low-load operation mode in the ejector cycle according to the first embodiment of the present invention.

FIG. 5 is a ph diagram in a low load operation mode in the ejector cycle according to the first embodiment of the present invention.

FIG. 6 is a schematic view of an ejector cycle according to a second embodiment of the present invention.

FIG. 7 is a schematic diagram showing a refrigerant flow in a normal operation mode in an ejector cycle according to a second embodiment of the present invention.

FIG. 8 is a schematic diagram illustrating a refrigerant flow in a normal operation mode in an ejector cycle according to a second embodiment of the present invention.

[Explanation of symbols]

Reference Signs List 100 compressor, 200 condenser, 300 evaporator, 400 ejector, 410 nozzle, 420 mixing unit, 430 diffuser, 600 gas-liquid separator, 7
00: pressure reducer, 710: open / close valve.

 ────────────────────────────────────────────────── ─── Continuing on the front page (72) Inventor Kunio Iriya 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture Inside of Denso Corporation (72) Inventor Toshio Hirata 1-1-1, Showa-cho, Kariya-shi, Aichi Prefecture (72) Inventor Yoshitaka Tomatsu 1-1-1 Showa-cho, Kariya-shi, Aichi Prefecture Inside DENSO Corporation

Claims (4)

[Claims] 1. A compressor (100) for sucking and compressing a refrigerant.
A radiator (200) for cooling the refrigerant discharged from the compressor (100); and at least one evaporator (300,
310) and an ejector (400) having a nozzle (410) for reducing and expanding the high-pressure refrigerant flowing out of the radiator (200).
In the ejector cycle comprising: when the mass refrigerant flow rate flowing out of the radiator (200) is equal to or more than a predetermined value, the evaporator (400) uses the high-speed refrigerant flow injected from the nozzle (410) in the evaporator (400). The gaseous phase refrigerant evaporated in (300) is sucked, and when the mass refrigerant flow rate flowing out of the radiator (200) is less than a predetermined value, the refrigerant decompressed in the nozzle (410) is reduced in the evaporator (300, 310), wherein the refrigerant is supplied to evaporate the refrigerant. 2. A compressor (100) for sucking and compressing a refrigerant.
A radiator (200) for cooling the refrigerant discharged from the compressor (100); an evaporator (300) for evaporating the refrigerant; and a nozzle () for decompressing and expanding the high-pressure refrigerant flowing out of the radiator (200). Ejector (400) having (410)
In the ejector cycle comprising: when the mass refrigerant flow rate flowing out of the radiator (200) is equal to or more than a predetermined value, the evaporator (400) uses the high-speed refrigerant flow injected from the nozzle (410) in the evaporator The vapor phase refrigerant evaporated in (300) is suctioned, and while mixing the suctioned refrigerant and the refrigerant injected from the nozzle (410), the velocity energy of the refrigerant is converted into pressure energy to increase the pressure of the refrigerant. The pressurized refrigerant flows out to the suction side of the compressor (100), and when the mass refrigerant flow rate flowing out of the radiator (200) is less than a predetermined value, the refrigerant decompressed by the nozzle (410) An ejector cycle, wherein the ejector cycle is supplied to an evaporator (300) to evaporate a refrigerant. 3. A compressor (100) for sucking and compressing a refrigerant.
A radiator (200) for cooling the refrigerant discharged from the compressor (100); and first and second evaporators (300, 310) for evaporating the refrigerant.
And an ejector (400) having a nozzle (410) for reducing and expanding the high-pressure refrigerant flowing out of the radiator (200).
When the mass refrigerant flow rate flowing out of the radiator (200) is equal to or more than a predetermined value, the ejector (400) uses the high-speed refrigerant flow injected from the nozzle (410) to generate the first evaporator ( When the mass-phase refrigerant flowing out from the radiator (200) is less than a predetermined value, the refrigerant is discharged from the first evaporator (310) by the ejector (400). An ejector cycle wherein the refrigerant decompressed by the nozzle (410) is supplied to the second evaporator (310) to evaporate the refrigerant without suction. 4. An air conditioner for cooling air blown into a room in the ejector cycle according to claim 3, wherein the second evaporator (310) is replaced with the first evaporator (300).
An air conditioner, wherein the air conditioner is disposed further upstream in the air flow.