TW201525389A - Refrigeration circulation device - Google Patents

Abstract

An object of the present invention is to suppress the temperature of a discharge gas of a compressor and also to suppress lowering of performance coefficient. A refrigeration circulation device 1 comprises an oil separator 3, which is arranged between a discharge side of a compressor 2 and a condenser 4 to separate the refrigerant and refrigerator oil contained in the refrigerant that are discharged from a high-stage compression section 2b; an oil return passage 20, which allows the refrigerator oil that is separated in the oil separator 3 to return to the low-stage compression section 2a and the high-stage compression section 2b; a feeding passage 10 that feeds the refrigerant from the condenser 4 into an intermediate pressure chamber; and an oil cooler 30, which conducts heat exchange between the refrigerator oil flowing through the oil return passage 20 and the refrigerant flowing through the feeding passage 10. The feeding passage 10 comprises: a first branch pipe 11 that feeds the refrigerant from the condenser 4 directly into the intermediate pressure chamber 2c and a second branch pipe 12 that feeds the refrigerant from the condenser 4 through the oil cooler 30 into the intermediate pressure chamber 2c.

Description

Refrigeration cycle device

The present invention relates to a refrigeration cycle apparatus including a compressor having a low stage side compression unit and a high stage side compression unit.

In the past, a refrigeration cycle apparatus having a two-stage screw compressor having a low-stage side compression portion and a high-stage side compression portion has been known. In the multi-stage compressor, after the refrigerant is compressed in the low-stage compression unit, the refrigerant is further compressed in the high-stage compression unit. The components used in such a two-stage screw compressor have a temperature limit and an upper limit for the temperature of the discharge gas. Therefore, various methods have been proposed in order to reduce the temperature of the discharge gas (for example, refer to Patent Documents 1 and 2).

Patent Document 1 discloses a two-stage compression refrigerator having an oil cooler that performs heat exchange between the refrigerator oil separated in the oil separator and the refrigerant condensed in the condenser. The refrigerator oil cooled in the oil cooler is injected into the low stage side compression portion, and the refrigerant flowing through the oil cooler is injected into the intermediate pressure chamber. Patent Document 2 discloses a refrigeration cycle in which an economizer is disposed between an evaporator and an expansion valve, and a refrigerant in a vapor state or a refrigerant in a liquid state is injected from an economizer into an intermediate pressure chamber of the compressor or The suction side of the low-stage compressor.

Advanced technical literature Patent literature

Patent Document 1: Japanese Patent No. 3903409 (Fig. 1 and paragraph 0007)

Patent Document 2: Japanese Patent Publication No. 2010-525292 (Fig. 1 and paragraph 0026)

In Patent Document 1, in order to suppress the temperature of the discharge gas, the refrigerating machine oil cooled by the refrigerant is injected into the low-stage compression unit, and the temperature of the refrigerating machine oil injected into the low-stage compression unit must be low. In order to make the temperature of the refrigerating machine oil low, it is necessary to increase the flow rate of the refrigerant flowing into the oil cooler and to increase the amount of the refrigerant injected into the intermediate pressure chamber. As a result, the intermediate pressure of the intermediate pressure chamber rises, and the compression ratio of the low-stage compression portion (=low-stage discharge pressure (that is, intermediate pressure)/(low-stage suction pressure) becomes large. As the compression ratio of the low-stage side compression portion increases, the volumetric efficiency of the low-stage-side compression portion deteriorates, and the cooling amount of the refrigeration cycle is lowered. Further, when the amount of the refrigerant injected into the intermediate pressure chamber is large, the amount of the refrigerant sucked in the high-stage side compression portion is increased to increase the compression power. As a result, the coefficient of achievement (COP = cooling capacity / compressor power) is lowered.

Accordingly, the present invention has been made to solve the above problems, and an object of the invention is to provide a refrigeration cycle apparatus capable of suppressing a decrease in a coefficient of achievement and suppressing a temperature of a discharge gas from a high-stage compression unit.

A refrigeration cycle apparatus according to the present invention includes a refrigeration cycle having a compressor, a condenser, and an expansion valve, the compressor having a low-stage compression unit that compresses the refrigerant, and a refrigerant that is compressed in the low-stage compression unit. An intermediate pressure chamber and a high-stage side compression portion that sucks the refrigerant of the intermediate pressure chamber and compresses the same The refrigeration cycle apparatus includes an oil separator that is disposed between the discharge side of the compressor and the condenser, and separates the refrigerant discharged from the high-stage compression unit and the refrigerator oil contained in the refrigerant; and the return flow path; The refrigerator oil separated in the oil separator is returned to the low stage side compression portion and the high stage side compression portion; the injection flow path is injected into the intermediate pressure chamber from the refrigerant flowing from the condenser; the oil cooler is in the flow Heat exchange between the refrigerating machine oil passing through the return flow path and the refrigerant flowing through the injection flow path; wherein the injection flow path includes: a first branch pipe, and the refrigerant is directly injected into the intermediate pressure chamber from the condenser; In the second branch pipe, the refrigerant is injected from the condenser through the oil cooler into the intermediate pressure chamber.

According to the refrigeration cycle apparatus of the present invention, the refrigerator oil cooled in the oil cooler is injected into the low stage side compression portion, and the injection path to the intermediate pressure chamber has a path through the oil cooler and a path directly from the condenser. Therefore, when the temperature of the discharge gas discharged from the high-stage side compression unit is lowered, the flow rate of the refrigerant to the oil cooler is not increased, and the amount of the refrigerant directly injected from the condenser can be increased, so that the temperature of the discharge gas is lowered. It is possible to suppress a decrease in the coefficient of achievement accompanying an increase in the amount of injection, and to suppress the temperature of the discharge gas. .

1‧‧‧ refrigeration cycle device

2‧‧‧Compressor

2a‧‧‧low section compression

2b‧‧‧High section side compression section

2c‧‧‧Intermediate pressure chamber

3‧‧‧ oil separator

4‧‧‧Condenser

5‧‧‧Main expansion valve

6‧‧‧Evaporator

10‧‧‧Injection flow path

11‧‧‧1st divergent piping

12‧‧‧2nd divergent piping

13‧‧‧1st flow regulator

14‧‧‧2nd flow regulator

20‧‧‧return flow path

21‧‧‧Low section return oil piping

22‧‧‧High section side return oil piping

30‧‧‧Oil cooler

40‧‧‧Opening Control Department

100‧‧‧ refrigeration cycle device

120‧‧‧return flow path

122‧‧‧High section side return oil piping

200‧‧‧ refrigeration cycle device

201‧‧‧heater

202‧‧‧Sub-expansion valve

Fig. 1 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.

Fig. 2 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention.

Fig. 3 is a refrigerant circuit diagram showing an example of a conventional refrigeration cycle apparatus.

Fig. 4 is a refrigerant circuit diagram showing an example of a conventional refrigeration cycle apparatus.

Fig. 5 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to a second embodiment of the present invention.

Fig. 6 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to a third embodiment of the present invention.

Embodiment 1

Embodiments of the outdoor unit of the refrigeration cycle apparatus of the present invention will be described below with reference to the drawings. Fig. 1 and Fig. 2 are refrigerant circuit diagrams showing a refrigeration cycle apparatus according to Embodiment 1 of the present invention. In the refrigeration cycle apparatus 1 of Fig. 1, the refrigeration cycle apparatus 1 forms a refrigeration cycle in which the compressor 2, the condenser 4, the main expansion valve 5, and the evaporator 6 are connected by piping. The refrigerant flowing through the refrigeration cycle apparatus 1 is used, for example, a single refrigerant of R32 refrigerant or a mixed refrigerant containing R32 refrigerant, or a refrigerant having a large difference in thermal compression compression such as R410A, that is, the discharge gas is easily heated. The refrigerant.

The compressor 2 is a device that sucks in a refrigerant, compresses the refrigerant to a high temperature and high pressure state, and discharges the refrigerant. The compressor 2 is a two-stage screw compressor including a low stage side compression unit 2a and a high stage side compression unit 2b, and the low stage side compression unit 2a and the high stage side compression unit 2b are rotationally driven by a common motor, and the motor Then it is driven by an inverter circuit. An intermediate pressure chamber 2c is provided between the low stage side compression portion 2a and the high stage side compression portion 2b, and the low stage side compression portion 2a discharges the compressed refrigerant to the intermediate pressure chamber 2c, and the high stage side compression portion 2b attracts the middle. The refrigerant in the pressure chamber 2c is compressed and compressed. Further, an injection port is provided in the intermediate pressure chamber 2c, and the refrigerant is injected into the intermediate pressure chamber 2c from the injection port.

The oil separator 3 is for pressing the refrigerating machine oil from the high side of the compressor 2 The device for separating the refrigerant discharged from the constricted portion 2b. Further, the oil separator 3 supplies the refrigerant separated from the refrigerating machine oil to the condenser 4 side, and returns the refrigerating machine oil to the compressor 2 side. The condenser 4 is a device for exchanging heat between the refrigerant discharged from the compressor 2 and air or water, and has a heat transfer tube containing, for example, a refrigerant, and a refrigerant for increasing the flow of the heat transfer tube and the outside. The configuration of the heat sink of the heat transfer area between the gases. The main expansion valve 5 is a device for adjusting the pressure of the refrigerant passing through the evaporator 6, and is constituted by, for example, an electronic expansion valve or the like. The evaporator 6 is a device for exchanging heat between a refrigerant and an external gas or water or brine, and has a heat transfer tube containing, for example, a refrigerant, and a refrigerant for increasing the flow of the heat transfer tube and the outside. The configuration of the heat sink of the heat transfer area between the gases.

Further, the refrigeration cycle apparatus 1 includes an injection flow path 10 through which the refrigerant flowing out of the condenser 4 is injected into the intermediate pressure chamber 2c, and the return oil flow path 20, and the refrigerant oil separated in the oil separator 3 is returned to the low stage side compression portion. 2a and the high-stage side compression unit 2b. The injection flow path 10 has a first branch pipe 11 and a second branch pipe 12 which are branched from between the condenser 4 and the main expansion valve 5, respectively. The first branch pipe 11 is a device that directly connects the condenser 4 and the intermediate pressure chamber 2c, and the second branch pipe 12 is connected to the condenser 4 and the intermediate pressure chamber 2c via the oil cooler 30. The first flow rate adjuster 13 is provided in the first branch pipe 11, and the second flow rate adjuster 14 is provided in the second branch pipe 12. The first flow rate adjuster 13 and the second flow rate adjuster 14 are configured by, for example, an electronic expansion valve, and adjust the opening degree of the first flow rate adjuster 13 and the second flow rate adjuster 14 to adjust the flow to the first branch pipe. 11 and the refrigerant flow rate (injection amount) of the second branch pipe 12.

The return oil passage 20 includes a low-stage return oil pipe 21 and a high-stage return oil pipe 22 that are connected to the outlet side of the refrigerating machine oil of the oil separator 3, the low-stage side compression unit 2a, and the high-stage side compression unit 2b, respectively. Low-stage side return oil pipe 21 for freezing The oil is returned from the oil separator 3 through the oil cooler 30 to the lower stage side compression unit 2a, and the high stage side return oil pipe 22 is a device for returning the refrigerator oil directly from the oil separator 3 to the high stage side compression unit 2b.

In addition, the oil cooler 30 is provided in the refrigeration cycle apparatus 1, and heat exchange is performed between the refrigerant flowing through the second branch pipe 12 and the refrigerator oil flowing into the low stage side compression unit 2a in the oil return flow path 20. In other words, the oil cooler 30 is a device that combines the second branch pipe 12 and the low-stage return oil pipe 21, and uses the refrigerant injected into the intermediate pressure chamber 2c to cool the refrigerator oil. Therefore, the refrigerating machine oil is returned to the high stage side compression portion 2b while being cooled by the oil cooler 30.

The opening degrees of the first flow rate adjuster 13 and the second flow rate adjuster 14 are controlled by the opening degree control unit 40. The opening degree control unit 40 controls the opening degree of the first flow rate adjuster 13 or the second flow rate adjuster 14 such that the temperature of the discharge gas of the refrigerant discharged from the high stage side compression unit 2b is the target discharge temperature (for example, 85 ° C). . In other words, when the opening degree of the first flow rate adjuster 13 is larger, the amount of refrigerant directly injected into the intermediate pressure chamber 2c from the condenser 4 is increased. Further, when the opening degree of the second flow rate adjuster 14 is larger, the temperature of the returned refrigerating machine oil is lower, and the amount of refrigerant injected into the intermediate pressure chamber 2c is increased. For example, a temperature sensor in which the temperature of the discharge gas is not detected is provided on the discharge side of the high-stage side compression unit 2b, and the discharge gas temperature and the first flow rate adjuster 13 and the second flow rate are previously stored in the opening degree control unit 40. The table associated with the opening degree of the regulator 14 causes the opening degree control unit 40 to control the opening degrees of the first flow rate adjuster 13 and the second flow rate adjuster 14 based on the discharge gas temperature.

Next, an operation example of the refrigeration cycle apparatus 1 will be described with reference to FIGS. 1 and 2 . Further, the first flow rate adjuster 13 and the second flow rate adjuster 14 are opened while the compressor 2 is operating. First, the high-pressure refrigerant discharged from the high-stage side compression unit 2b The gas, which is a low-pressure gas, is first compressed in the compressor 2 into a high-temperature and high-pressure gas state. The refrigerant in a high-temperature gas state is heat-exchanged with the outside air or water in the condenser 4, and the energy of the refrigerant is transferred to a heat source (air or water) to be condensed into a high-pressure liquid refrigerant. Then, the refrigerant is decompressed by the main expansion valve 5 into a low-pressure two-phase state and enters the evaporator 6.

In the evaporator 6, the refrigerant absorbs energy such as external gas or water and evaporates into a low pressure gas. At this time, external air or water after heat exchange with the refrigerant is cooled. Thereafter, the low-temperature low-pressure refrigerant gas flowing out of the evaporator 6 is sucked into the low-stage compression unit 2a of the compressor 2, and the first stage is compressed. Then, the refrigerant gas compressed in the low stage side compression portion 2a is discharged to the intermediate pressure chamber 2c. In the intermediate pressure chamber 2c, the refrigerant gas to be discharged is sucked into the high stage side compression portion 2b and compressed in the second stage.

At this time, a part of the high-pressure low-temperature liquid refrigerant is injected into the intermediate pressure chamber 2c through the first branch pipe 11 and the second branch pipe 12 from between the condenser 4 and the main expansion valve 5. On the other hand, the low-side oil return pipe 21 directly returns to the high-stage side compression portion 2b side, and passes through the oil cooler 30 to return to the low-stage side compression portion from the high-stage return oil pipe 22 through the oil cooler 30. 2a. In the oil cooler 30, the refrigerant flowing through the second branch pipe 12 and the refrigerating machine oil flowing through the high-stage return oil pipe 22 exchange heat, and return to the low stage side compression portion 2a while the refrigerator oil is cooled. At this time, the opening degree control unit 40 controls the opening degree of the first flow rate adjuster 13 and the second flow rate adjuster 14 so that the temperature of the discharge gas of the refrigerant discharged from the high stage side compression unit 2b is the target discharge temperature (for example, 85 ° C). .

As described above, since the temperature of the discharge gas is controlled to be the target discharge temperature, the temperature of the discharge gas of the refrigerant discharged from the high stage side compression unit 2b can be suppressed. Degree so that the temperature of the component does not exceed the upper temperature limit. At this time, after the refrigerator oil is cooled, the low-stage compression unit 2a is returned, and the power consumption can be reduced, and the coefficient of achievement (COP) can be suppressed from being lowered. In addition, even when the oil cooler 30 is introduced in a state where the temperature of the refrigerating machine oil is high, the oil cooler is not added to the oil cooler as in the past refrigeration cycle apparatus shown in FIGS. 3 and 4 . The refrigerant amount of 30 is controlled to increase the temperature of the discharge gas, and is controlled so as to add the injection from the first branch pipe 11 side to the intermediate pressure chamber 2c so that the discharge gas temperature is the target discharge temperature. Therefore, it is possible to suppress a decrease in cooling ability and a decrease in coefficient of achievement (COP) due to an increase in the amount of injection.

In other words, the intermediate pressure of the intermediate pressure chamber 2c can be reduced by increasing the amount of injection into the intermediate pressure chamber 2c in order to cool the refrigeration oil as in the past, so that the compression ratio of the low stage side compression portion 2a can be controlled to a low value. , reduce the leakage loss during the compression process. That is, the volumetric efficiency of the low-stage side compression portion 2a is increased, and the cooling ability is improved. In addition, since the amount of the refrigerant that cools the amount of the refrigerating machine oil that is merged in the intermediate pressure chamber 2c is reduced, the compression power of the high stage side compression unit 2b is lowered, so that the compressor power can be reduced.

In particular, when the motor of the compressor 2 is driven by the inverter, in the deceleration region operating at a frequency lower than 50 Hz, the effect of reducing the leakage loss is larger, and the coefficient of achievement can be greatly improved.

Further, the refrigerant uses a refrigerant having a large difference in heat-insulating compression represented by R32 or R410A, that is, in the case of using a refrigerant which is easy to make the temperature of the discharge gas high, the control is as described above so that the gas is discharged. The effect of lowering the coefficient of achievement (COP) when the temperature is the target discharge temperature becomes large.

Embodiment 2

Fig. 5 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to a second embodiment of the present invention, and the refrigeration cycle apparatus 100 will be described with reference to Fig. 5. In the refrigeration cycle apparatus 100 of Fig. 5, the same components as those of the refrigeration cycle apparatus 1 of Fig. 1 and Fig. 2 are denoted by the same reference numerals, and their description is omitted. The difference between the refrigeration cycle apparatus 100 of Fig. 5 and the refrigeration cycle apparatus 1 of Fig. 1 and Fig. 2 is that the return oil passage 120 returns the refrigerator oil cooled in the oil cooler 30 to the high section side compression section. 2b.

The return oil passage 120 of the fifth embodiment is divided into a low-stage side return oil pipe 21 and a high-stage side oil return pipe 122 at the outlet side of the oil cooler 30, and the refrigerating machine oil is returned to the low-stage side compression portion 2a and the high section, respectively. Side compression unit 2b. In other words, the refrigerating machine oil cooled in the oil cooler 30 is also returned from the high stage side return oil pipe 122 to the high stage side compression portion 2b. In this case, since the cooled refrigerating machine oil is also injected into the high stage side compression portion 2b, the temperature of the discharge gas can be lowered, and the temperature of the discharge gas can be lowered, and the coefficient of achievement (COP) can be suppressed from being lowered.

Embodiment 3

Fig. 6 is a refrigerant circuit diagram showing a refrigeration cycle apparatus according to a third embodiment of the present invention, and the refrigeration cycle apparatus 200 will be described with reference to Fig. 6. In the refrigeration cycle apparatus 200 of the sixth embodiment, the same components as those of the refrigeration cycle apparatus 1 of the first and second drawings are denoted by the same reference numerals, and their description will be omitted. The difference between the refrigeration cycle apparatus 200 of Fig. 6 and the refrigeration cycle apparatus 1 of Fig. 1 and Fig. 2 is that the refrigeration cycle apparatus 200 has an economizer (intermediate heat exchanger) 201, which constitutes an economizer cycle.

The refrigeration cycle apparatus 200 of FIG. 6 includes a sub-expansion valve 202 that expands a portion of the condensed refrigerant in the condenser 4, and in the condenser 4 The economizer 201 that exchanges heat between the condensed liquid refrigerant and the expanded refrigerant in the sub-expansion valve 202. The economizer 201 is connected such that the refrigerant bypassed from the condenser 4 flows out to the main expansion valve 5, and the refrigerant that has branched away from the main expansion valve 5 flows out to the first branch pipe 11 and the second branch pipe 12 . Therefore, the liquid refrigerant having a large degree of supercooling flows into the first branch pipe 11 and the second branch pipe 12.

In this case, since the cooled refrigerating machine oil is also injected into the high stage side compression portion 2b, the temperature of the discharge gas can be lowered, and the temperature of the discharge gas can be lowered, and the coefficient of achievement (COP) can be suppressed from being lowered. In particular, since the supercooled refrigerant can flow into the first branch pipe 11 and the second branch pipe 12 by the economizer 201, the amount of refrigerant injected into the intermediate pressure chamber 2c can be reduced, and the coefficient of achievement (COP) can be further suppressed. The reduction. In the refrigeration cycle apparatus 200 of Fig. 6, the oil return flow path 20 of Fig. 1 is exemplified, but the oil return flow path 120 as shown in Fig. 5 may be provided.

Embodiments of the present invention are not limited to the above-described first to third embodiments. For example, in the above-described first to third embodiments, the first flow rate adjuster 13 and the second flow rate adjuster 14 are both configured by an electronic expansion valve, but the first flow rate adjuster 13 and the second flow rate adjustment are used. Either or both of the devices 14 may be a temperature type expansion valve. Thereby, the opening degree control can be easily performed. Further, either or both of the first flow rate adjuster 13 and the second flow rate adjuster 14 may be configured as a fixed orifice having an opening degree at which the discharge gas temperature is the target discharge temperature. Thereby, it is possible to achieve a reduction in the temperature of the discharge gas and a decrease in the coefficient of achievement at a low price.

In this case, the first flow rate adjuster 13 and the second flow rate adjuster 14 may be formed of any one of an electronic expansion valve, a temperature expansion valve, or a fixed orifice. Composition. For example, when the first flow rate adjuster 13 and the second flow rate adjuster 14 are a combination of an electronic expansion valve, a temperature expansion valve, and a fixed orifice, high-precision control can be realized at low cost.

1‧‧‧ refrigeration cycle device

2‧‧‧Compressor

2a‧‧‧low section compression

2b‧‧‧High section side compression section

2c‧‧‧Intermediate pressure chamber

3‧‧‧ oil separator

4‧‧‧Condenser

5‧‧‧Main expansion valve

6‧‧‧Evaporator

10‧‧‧Injection flow path

11‧‧‧1st divergent piping

12‧‧‧2nd divergent piping

13‧‧‧1st flow regulator

14‧‧‧2nd flow regulator

20‧‧‧return flow path

21‧‧‧Low section return oil piping

22‧‧‧High section side return oil piping

30‧‧‧Oil cooler

40‧‧‧Opening Control Department

Claims (8)

A refrigeration cycle apparatus comprising: a refrigeration cycle having a compressor, a condenser, and an expansion valve, the compressor having a low-stage side compression portion that compresses the refrigerant, and an intermediate pressure that discharges the refrigerant compressed in the low-stage side compression portion a chamber, and a high-stage side compression unit that sucks and compresses the refrigerant in the intermediate pressure chamber, the refrigeration cycle apparatus comprising: an oil separator disposed between the discharge side of the compressor and the condenser, and will be high The refrigerant discharged from the segment side compression unit and the refrigerating machine oil contained in the refrigerant are separated; and the recirculation flow path returns the refrigerating machine oil separated in the oil separator to the low stage side compression unit and the high stage side compression unit; and the injection flow path And discharging the refrigerant flowing out from the condenser into the intermediate pressure chamber; the oil cooler performs heat exchange between the refrigerator oil flowing through the return flow path and the refrigerant flowing through the injection flow path; wherein the injection flow path The first branch pipe includes a refrigerant that is directly injected into the intermediate pressure chamber from the condenser, and a second branch pipe that injects refrigerant from the condenser through the oil cooler into the intermediate pressure chamber. The refrigeration cycle apparatus of claim 1, further comprising: The first flow rate adjuster is provided in the first branch pipe to adjust the flow rate of the refrigerant flowing through the first branch pipe; and the second flow rate adjuster is provided in the second branch pipe to adjust the flow through the second branch pipe Refrigerant flow. The refrigeration cycle device of claim 2, further comprising an opening degree The control unit controls the opening degree of the first flow rate adjuster or the second flow rate adjuster such that the temperature of the discharge gas of the refrigerant discharged from the high stage side compression unit is the set target discharge temperature. The refrigerating cycle device according to claim 1, wherein the return flow path includes: a high-stage side return oil pipe, and the refrigerating machine oil is directly returned from the oil separator to the high-stage side compression portion; and the low-stage side The oil return pipe returns the refrigerator oil from the oil separator to the high-stage side compression portion through the oil cooler. The refrigerating cycle device of claim 1, wherein the reflow passage includes diverging the refrigerating machine oil passing through the oil cooler from the oil separator and returning to the low section side compression portion and the high section side, respectively The low-stage side oil return pipe of the compression unit and the high-stage side oil return pipe. The refrigeration cycle apparatus of claim 1, further comprising: a secondary expansion valve that expands a portion of the refrigerant flowing out of the condenser; and an economizer that causes the refrigerant expanded by the secondary expansion valve to be After the heat exchange between the refrigerants flowing out of the condenser, the first branch pipe and the second branch pipe flow out. The refrigeration cycle apparatus of claim 1, wherein the compressor is driven by an inverter. The refrigeration cycle apparatus according to claim 1, wherein the refrigerant is composed of R32 or R410A.