CN103791645B - Refrigerating circulatory device - Google Patents

Abstract

It is an object of the present invention to improve the capacity of the condenser while ensuring long-term reliability and maintaining the pressure in the back pressure chamber in a refrigeration cycle device using R32. The refrigerating cycle device of the present invention includes: a circulation flow path in which a compressor, an oil separator, a first on-off valve, a condenser, a decompression device, and an evaporator are sequentially connected by piping, and R32, which is a refrigerant, circulates; The first bypass flow path connecting the oil separator and the compressor through piping; the cooler installed in the first bypass flow path; the second bypass flow path connecting the compressor and condenser through piping; installed in the second bypass flow path The second on-off valve of the two-bypass flow path; a control mechanism that opens any one of the first on-off valve and the second on-off valve and closes the other.

Description

Refrigeration cycle device

technical field

The invention relates to a refrigeration cycle device.

Background technique

Difluoromethane (hereinafter referred to as "R32") has zero ozone destruction coefficient, and the global warming coefficient of R32 is about 1/3 of that of R410A. Therefore, by using R32 instead of R410A widely used in refrigeration cycle devices at present, it is possible to contribute to the reduction of environmental load.

For example, Patent Document 1 describes a refrigerant compressor using R32.

prior art literature

patent documents

Patent Document 1: Japanese Patent Laid-Open No. 2001-115963

Summary of the invention

The problem to be solved by the invention

However, a refrigerant compressor using R32 has a higher discharge gas temperature than a refrigerant compressor using R410A or the like.

Therefore, compared with refrigerant compressors using R410A or the like, a refrigerant compressor using R32 has a problem that resin components and oil tend to deteriorate, and long-term reliability cannot be ensured.

In addition, when the temperature of the discharged gas rises, the amount of R32 dissolved in the engine oil (refrigerant dissolved amount) decreases, so the refrigerant compressor using R32 also has the problem of a decrease in the pressure of the back pressure chamber.

On the other hand, the characteristic property of R32 that the temperature of the ejected gas is high can also provide an advantage of improving the performance of the condenser (in the air conditioner, the heating performance of the room is improved during heating operation).

Contents of the invention

In contrast, an object of the present invention is to improve the capacity of the condenser while ensuring long-term reliability and maintaining the pressure in the back pressure chamber in a refrigeration cycle device using R32.

solution

The refrigerating cycle device of the present invention includes: a circulation flow path in which a compressor, an oil separator, a first on-off valve, a condenser, a decompression device, and an evaporator are sequentially connected by piping, and R32, which is a refrigerant, circulates; The first bypass flow path connecting the oil separator and the compressor through piping; the cooler installed in the first bypass flow path; the second bypass flow path connecting the compressor and condenser through piping; installed in the second bypass flow path The second on-off valve of the two-bypass flow path; a control mechanism that opens any one of the first on-off valve and the second on-off valve and closes the other.

Invention effect

According to the present invention, in a refrigeration cycle device using R32, it is possible to ensure long-term reliability and maintain the pressure in the back pressure chamber, while improving the capacity of the condenser.

Description of drawings

FIG. 1 is an explanatory view showing the configuration of a refrigeration cycle apparatus according to the present embodiment.

Fig. 2 is a longitudinal sectional view of a compressor constituting the refrigeration cycle device.

Fig. 3 is an enlarged cross-sectional view of a compression mechanism unit in the compressor.

Fig. 4 is a graph showing the relationship between the theoretical ejection gas temperature and the pressure ratio of R32 and R410A.

FIG. 5 is a graph showing the relationship between the refrigerant dissolution ratio of R32 to polyol ester-based oil and the temperature of the discharged gas.

Fig. 6 is a graph showing the relationship between the motor efficiency and the temperature of the compressor.

Fig. 7 is an explanatory view of the structure of the compressor when a discharge chamber is provided in the compression mechanism section.

Fig. 8 is a first structure when an annular wall is provided in the airtight container in the compressor.

Fig. 9 is a second structure when an annular wall is provided in the airtight container in the compressor.

Fig. 10 is an explanatory view showing the configuration of the refrigeration cycle device according to the present embodiment.

The reference signs are explained as follows:

1 compressor

2 airtight containers

2d suction tube

2e first ejection pipe

2f Second ejection pipe

2g return tube

3 Compression Mechanism Department

4 motors

5 fixed scroll

6 orbiting scroll

6a slewing bearing

7 crankshaft

7c oil supply passage

9 frames

9a main bearing

12 Euclidean ring

14 back pressure chamber

15 cooler

18 indoor heat exchanger

19 pressure relief device

20 outdoor heat exchanger

21 first opening and closing valve

22 second opening and closing valve

23 relief valve

24 ring wall

24a inner space

24b Outer space

25 oil separator

26 control mechanism

35 The first bypass flow path

36 Second bypass flow path

37 cover body

38 First Space

39 Second Space

A1 refrigeration cycle device

A2 refrigeration cycle device

detailed description

The main feature of the refrigeration cycle device of this embodiment is that the discharged gas and oil, or only the oil is cooled by a cooler and returned to the compressor to lower the temperature of the compressor. The refrigeration cycle device of this embodiment can be applied to refrigerators, refrigerators, heat pump water heaters, air conditioners, and the like. Hereinafter, assuming that this refrigeration cycle device is applied to an air conditioner, the present embodiment will be described with reference to the drawings as appropriate.

FIG. 1 is an explanatory view showing the configuration of a refrigeration cycle apparatus according to the present embodiment. As shown in FIG. 1 , the refrigeration cycle apparatus A1 according to this embodiment is sequentially connected to a compressor 1, an oil separator 25, a first on-off valve 21, an outdoor heat exchanger 18, a decompression device 19 (expansion valve), and The indoor heat exchanger 20 constitutes a refrigerant circulation flow path.

Furthermore, the refrigeration cycle apparatus A1 is provided with the 1st bypass flow path 35 which connects the oil separator 25 and the compressor 1, and the 2nd bypass flow path 36 which connects the compressor 1 and the condenser. It should be noted that, as shown in FIG. 1 , the second bypass flow path 36 connects the compressor 1 and the condenser via a four-way valve 40 .

In the present embodiment, it is assumed that R32 is used as the refrigerant, and a polyol ester oil having good compatibility with R32 is assumed to be used as the engine oil (lubricating oil).

During the cooling operation, when the refrigeration cycle device A1 receives the instruction of the cooling operation through the remote controller, the control mechanism 26 is used to open the second on-off valve 22 and close the first on-off valve 21 to block the refrigerant from the oil separator 25 directly to the refrigerant. The outdoor heat exchanger 18 (condenser) flows into the flow path so that the refrigerant returns from the oil separator 25 to the compressor 1 .

The high-temperature and high-pressure refrigerant (hot gas) and engine oil compressed by the compressor 1 flow into the oil separator 25 through the first discharge pipe 2 e of the compressor 1 . Here, since the first on-off valve 21 is closed, the refrigerant and the oil are not separated in the oil separator 25 , and both flow to the cooler 15 . The refrigerant and oil are cooled in the cooler 15 , and returned to the compressor 1 through the first bypass passage 35 .

The refrigerant and oil returned to the compressor 1 are separated inside the compressor 1 , the refrigerant is discharged from the second discharge pipe 2 f , and the oil is accumulated in the lower portion of the compressor 1 . The refrigerant discharged from the discharge pipe 2f flows into the outdoor heat exchanger 18 (condenser) through the second on-off valve 22, and is condensed by exchanging heat with air and radiating heat. Thereafter, the refrigerant is supplied to the decompression device 19 , expands isenthalpically while passing through the decompression device 19 , and becomes a gas-liquid two-phase flow in which gas refrigerant and liquid refrigerant are mixed at low temperature and low pressure. The refrigerant in this gas-liquid two-phase flow flows into the indoor heat exchanger 20 (evaporator).

The liquid refrigerant in the indoor heat exchanger 20 (evaporator) passes through refrigerant pipes (not shown) and fins attached to these refrigerant pipes, and is vaporized into gas refrigerant by absorbing heat from the air. That is, when the liquid refrigerant is vaporized, the indoor heat exchanger 20 (evaporator) cools the surrounding air, whereby the refrigeration cycle device A1 performs a cooling function. Next, the refrigerant that has left the indoor heat exchanger 20 (evaporator) is sucked into the suction pipe 2 d of the compressor 1 through the four-way valve 40 . Then, the refrigerant is compressed to a high temperature and high pressure in the compressor 1, and is discharged from the first discharge pipe 2e of the compressor 1 again to circulate through the circulation flow path.

During the heating operation, when the refrigeration cycle A1 receives the instruction of the heating operation through the remote controller, the second on-off valve 22 is closed by the control mechanism 26, and the first on-off valve 21 is opened, so that the oil separator 25 and the The refrigerant from which the oil has been separated flows into the indoor heat exchanger 20 (condenser).

The high-temperature and high-pressure refrigerant (hot gas) compressed by the compressor 1 flows into the oil separator 25 from the first discharge pipe 2 e of the compressor 1 . Here, the refrigerant and the oil are separated in the oil separator 25 , and the oil flows into the cooler 15 . The engine oil cooled in the cooler 15 returns to the compressor 1 through the first bypass flow path 35 . On the other hand, the refrigerant flows into the indoor heat exchanger 20 (condenser), and condenses by releasing heat through heat exchange with air. Thereafter, the refrigerant is supplied to the decompression device 19 , expands isenthalpically while passing through the decompression device 19 , and becomes a gas-liquid two-phase flow in which gas refrigerant and liquid refrigerant are mixed at low temperature and low pressure. The refrigerant in this gas-liquid two-phase flow flows into the outdoor heat exchanger 18 (evaporator). Thereafter, the outdoor heat exchanger 18 (evaporator) is as described in the cooling operation.

Next, the compressor 1 will be described. Fig. 2 is a longitudinal sectional view of a compressor constituting the refrigeration cycle device. Fig. 3 is an enlarged sectional view of a compression mechanism unit in the compressor of Fig. 2 . As shown in FIG. 2 , the compressor 1 in this embodiment is composed of a high-pressure chamber type hermetic scroll compressor, and is used under a wide range of operating conditions.

The compressor 1 includes: a compression mechanism unit 3 composed of an orbiting scroll 6 and a fixed scroll 5 ; a motor 4 that drives the compression mechanism unit 3 ; and an airtight container 2 that accommodates the compression mechanism unit 3 and the motor 4 . Compression mechanism part 3 is arranged in the upper part in airtight container 2, and electric motor 4 is arranged in the lower part. Also, organic oil is stored at the bottom of the airtight container 2 .

The airtight container 2 is constituted by welding a lid chamber 2b and a bottom chamber 2c up and down a cylindrical case 2a. A suction pipe 2d and a first discharge pipe 2e are provided in the lid chamber 2b. The first discharge pipe 2 e is connected to the discharge port 5 e of the fixed scroll 5 . The first discharge pipe 2e is fixed to the fixed scroll 5, and the refrigerant flowing out from the discharge port 5e flows out of the compressor 1 through the first discharge pipe 2e without circulating in the airtight container 2.

A second discharge pipe 2f and a return pipe 2g are provided on the side surface of the casing 2a. The compression mechanism unit 3 includes: a fixed scroll 5 ; an orbiting scroll 6 ; and a frame 9 fastened to the fixed scroll 5 with fasteners such as bolts to support the orbiting scroll 6 .

A freely revolving orbiting scroll 6 is disposed opposite to the fixed scroll 5 , and a suction chamber 10 and a compression chamber 11 are formed by both.

The outer peripheral side of the frame 9 is fixed to the inner wall surface of the airtight container 2 by welding, and is equipped with the main bearing 9a which supports the crankshaft 7 rotatably. The eccentric portion 7 b of the crankshaft 7 is connected to the lower surface side of the orbiting scroll 6 .

Oldham's ring 12 is disposed between the lower surface side of orbiting scroll 6 and frame 9 , and Oldham's ring 12 is fitted into a groove formed on the lower surface side of orbiting scroll 6 and a groove formed in frame 9 . The Oldham ring 12 functions to allow the orbiting scroll 6 to perform an orbital motion by receiving the eccentric rotation of the eccentric portion 7 b of the crankshaft 7 without autorotation.

The motor 4 includes a stator 4a and a rotor 4b. Stator 4a is fixed to airtight container 2 by press fitting, welding, or the like. The rotor 4b is rotatably arranged inside the stator 4a. A crankshaft 7 is fixed to the rotor 4b.

The crankshaft 7 includes a main shaft 7 a and an eccentric portion 7 b, and is supported by a main bearing 9 a and a lower bearing 17 provided on the frame 9 . The eccentric portion 7 b is integrally formed eccentrically with respect to the main shaft 7 a of the crankshaft 7 , and is fitted to the orbiting bearing 6 a provided on the back surface of the orbiting scroll 6 . The crankshaft 7 is driven by the electric motor 4, and the eccentric portion 7b eccentrically rotates relative to the main shaft 7a, thereby causing the orbiting scroll 6 to orbit. In addition, the crankshaft 7 is provided with an oil supply passage 7c that guides the oil to the main bearing 9a, the lower bearing 17, and the swing bearing 6a, and an oil supply pipe 7d that draws the engine oil and guides the oil supply passage 7c is attached to the shaft end on the motor 4 side. .

When the orbiting scroll 6 is orbited by the crankshaft 7 driven by the electric motor 4 , the gas refrigerant is guided from the suction pipe 2 d to the compression chamber 11 formed by the orbiting scroll 6 and the fixed scroll 5 . Then, the gas refrigerant is compressed and reduced in volume as it moves toward the center between the orbiting scroll 6 and the fixed scroll 5 . The compressed gas refrigerant flows out to the outside through the discharge pipe 2 e from the discharge port 5 e provided in the substantially center of the fixed scroll 5 .

Next, operations and effects of the refrigeration cycle apparatus A1 according to the present embodiment will be described. The adiabatic index of R32 used as a refrigerant in the refrigeration cycle apparatus A1 is larger than that of R410A widely used as a refrigerant for air conditioners.

Fig. 4 is a graph showing the relationship between the theoretical ejection gas temperature and the pressure ratio of R32 and R410A. As shown in FIG. 4 , the higher the pressure ratio between the suction pressure and the discharge pressure, the higher the temperature of the discharge gas. In addition, the temperature of the discharged gas of R32 is higher than that of R410A. Therefore, the temperature of the gas discharged from the compressor 1 becomes higher in the refrigeration cycle apparatus A1 using R32 as the refrigerant than in the refrigeration cycle apparatus using R410A as the refrigerant. Therefore, in the high-pressure chamber system in which the airtight container is filled with the blown gas, when R32 is used as the refrigerant, deterioration of resin components and the like in the motor 4 of the compressor 1 tends to progress. In contrast, in the refrigeration cycle apparatus A1 according to the present embodiment, the discharged refrigerant and oil are cooled and returned to the compressor 1 to lower the temperature of the compressor 1 .

In more detail, during the cooling operation, the high-temperature and high-pressure refrigerant discharged from the first discharge pipe 2e of the compressor 1 shown in FIG. 1 flows into the oil separator 25, and the oil discharged together with the refrigerant passes through the cooler 15 and returns to compressor 1. At this time, the refrigerant and oil returned to the compressor 1 are cooled by the cooler 15, and the temperature of the compressor 1 decreases due to the inflow of the refrigerant and oil.

During the heating operation, the high-temperature and high-pressure refrigerant discharged from the first discharge pipe 2e of the compressor 1 shown in FIG. Returns to the compressor 1 through the cooler 15 . The amount of oil returned to the compressor 1 is as little as about 1% by weight of the refrigerant flow rate, and the cooling effect of the compressor 1 is small, but the ambient temperature of the compressor 1 during heating operation is the outside air temperature in winter, and the compressor 1 1 The temperature is lowered by the cooling of the external air. On the other hand, since the refrigerant separated from the oil in the oil separator 25 directly flows into the condenser 18, high-temperature refrigerant gas can be supplied to the condenser 18 without reducing the heating capacity. In particular, among refrigerants such as R32, which have a property of increasing the temperature of the discharged gas, the heating capability is improved compared with R410A which is currently widely used.

Next, the back pressure control valve 16 as a pressure adjustment mechanism of the back pressure chamber 14 will be described. As shown in FIG. 3 , a spring receiving hole 5 f is formed in the fixed scroll 5 . Moreover, 5 g of through holes are formed in the back pressure chamber 14 side of 5 f of spring accommodation holes. In addition, the spring housing hole 5f communicates with the compression chamber 11 via the communication hole 5b. The spring 16d presses the spool 16c so that the through-hole 5g is closed in the spring accommodation hole 5f. The spring 16d is attached to the sealing member 16e. Furthermore, the sealing member 16e is press-fitted into the fixed scroll 5 so as to partition the spring housing hole 5f and the inside of the airtight container 2 .

Next, the operation of the back pressure control valve 16 will be described. As shown in FIG. 2, the engine oil accumulated in the oil storage place 13 at the bottom of the airtight container 2 is supplied to each bearing part through the oil supply pipe 7d and the oil supply passage 7c by virtue of the pressure difference between the airtight container 2 and the back pressure chamber 14. Oil. The oil supplied to the main bearing 9 a and the swing bearing 6 a enters the back pressure chamber 14 , where the refrigerant dissolved in the oil foams to increase the pressure in the back pressure chamber 14 .

As shown in FIG. 3, if the pressure difference between the back pressure chamber 14 and the spring receiving hole 5f is greater than the pressing force of the spring 16d, the spool 16c opens. As a result, the oil in the back pressure chamber 14 is supplied from the communication hole 5 b to the compression chamber 11 through the groove 5 a, and is discharged from the discharge port 5 e together with the refrigerant. The pressure of the back pressure chamber 14 becomes approximately a value obtained by adding a predetermined value (a constant value determined by the spring force of the spring 16d) to the suction pressure.

Generally, the amount of refrigerant dissolved in engine oil decreases as the temperature of the discharged gas rises. FIG. 5 is a graph showing the relationship between the refrigerant dissolution ratio of R32 to polyol ester-based oil and the temperature of the discharged gas. In addition, in FIG. 5 , the refrigerant dissolution amount ratio on the vertical axis represents a ratio where the refrigerant dissolution amount at the discharge gas temperature of 86° C. is “1”.

As shown in FIG. 5 , as the temperature of the discharged gas rises, the amount of R32 dissolved in the polyol ester-based engine oil (refrigerant dissolved amount ratio) decreases. When the amount of the refrigerant dissolved in the oil is insufficient, the pressure of the back pressure chamber 14 whose pressure is maintained by foaming of the refrigerant dissolved in the oil tends to decrease.

On the other hand, in the present embodiment, the temperature of the oil is lowered by the cooler 15 , so that the pressure drop in the back pressure chamber 14 can be suppressed. That is, according to the refrigeration cycle apparatus A1 according to the present embodiment, the balance between the suction pressure and the back pressure of the compressor 1 can be well maintained, and the pressing force of the orbiting scroll 6 with respect to the fixed scroll 5 can be maintained moderately.

Next, the efficiency of the electric motor used in the compressor 1 will be described. Fig. 6 is a graph showing the relationship between the motor efficiency and the temperature of the compressor. As shown in FIG. 6, as the temperature of the compressor 1 decreases, the motor efficiency increases. Therefore, according to the refrigeration cycle apparatus A1 according to the present embodiment, since the temperature of the compressor 1 is lowered, the motor efficiency can be improved. In addition, since the intake air heating loss is reduced, the input to the compressor 1 can be reduced.

Fig. 7 is a diagram showing a configuration of a compression mechanism when a relief valve is provided in the compressor of Fig. 2 . In the scroll compressor, when the pressure ratio between the suction pressure and the discharge pressure (discharge pressure/suction pressure) is low, most of the refrigerant is discharged from the relief valve 23 before being discharged from the discharge port 5e. In FIG. 7 , a cover 37 is provided above the fixed scroll 5 , and the cover 37 divides the airtight container 2 into a first space 38 and a second space 39 . The first space 38 communicates with the first discharge pipe 2e and the relief valve 23, and the refrigerant discharged from the relief valve 23 can be discharged from the first discharge pipe 2e without flowing into the airtight container 2.

In addition, the electric motor 4 may be arrange|positioned in the 2nd space 39, and the airtight container 2 may be divided into the 1st space 38 and the 2nd space 39 by the fixed scroll 5 instead of the cover 37.

Fig. 8 is a first structure when an annular wall is provided in the airtight container in the compressor of Fig. 2 . A cylindrical annular wall 24 is provided at the lower portion of the frame 9 to divide the second space 39 into an inner space 24a and an outer space 24b located outside the inner space 24a.

The return pipe 2g connected to the first bypass flow path 35 opens to the inner space 24a of the annular wall 24, and the second discharge pipe 2f connected to the second bypass flow path 36 opens to the outer space 24b of the annular wall 24. .

The refrigerant and oil that flowed in from the return pipe 2g are guided to the lower part of the compressor 1 through the gap between the stator 4a and the rotor 4b, and the oil is returned to the oil, and only the refrigerant with a low density is not shown in the outer periphery of the stator 4a. The groove flows into the outer space 24b of the annular wall 24, and is discharged from the second discharge pipe 2f. In addition, due to the action of the annular wall 24, the oil scattered by the rotation of the rotor 4b does not directly flow out from the second discharge pipe 2f. Therefore, the oil separation performance in the airtight container 2 can be improved.

Fig. 9 is a second structure when an annular wall is provided in the airtight container in the compressor of Fig. 2 . A return pipe 2g connected to the first bypass flow path 35 is provided between the electric motor 4 and the oil storage 13 to return the engine oil flowing in from the return pipe 2g to the oil storage 13 . On the other hand, the second discharge pipe 2f connected to the second bypass channel 36 is connected between the compressor 1 and the motor 4 . Therefore, only the low-density refrigerant passes through the gap of the motor 4 and is discharged from the second discharge pipe 2f connected to the second bypass flow path 36, so that the oil separation performance in the airtight container can be improved.

Next, a case where this embodiment is applied to a rotary compressor will be described. Fig. 10 is an explanatory view showing the configuration of the refrigeration cycle device according to the present embodiment.

A rotary compressor is mounted on the refrigeration cycle apparatus A3 in FIG. 10 . The first discharge pipe 2e, the second discharge pipe 2f, and the return pipe 2g may also be provided in the airtight container 2 of the rotary compressor, so that it can be implemented in compressors other than the scroll compressor.

As described above, the refrigerating cycle device of the present invention includes: the compressor 1, the oil separator 25, the first on-off valve 21, the condenser, the decompression device 19, and the evaporator are sequentially connected by piping and supplied as a refrigerant. The circulation flow path of the R32 circulation; the first bypass flow path 35 connecting the oil separator 25 and the compressor 1 by piping; the cooler 15 provided in the first bypass flow path 35; the compressor 1 and the condenser by piping The second bypass flow path 36 connected to the device; the second on-off valve 22 located in the second bypass flow path 36; any one of the first on-off valve 21 and the second on-off valve 22 is opened to open the other One side closes the control mechanism 26 .

In addition, in the refrigeration cycle device of the present invention, the first on-off valve 21 is closed and the second on-off valve 22 is opened during the cooling operation, and the first on-off valve 21 is opened and the second on-off valve is opened during the heating operation. The two on-off valves 22 are closed.

In addition, in the refrigerating cycle apparatus of the present invention, the compressor 1 has: the compression mechanism part 3; the motor 4; the first space 38 into which the refrigerant discharged from the compression mechanism part 3 flows; the second space 39 in which the motor 4 is located. The cover body 37 that divides the first space 38 and the second space 39 , the circulation flow path is connected to the first space 38 , and the first bypass flow path 35 and the second bypass flow path 36 are connected to the second space 39 .

In addition, in the refrigeration cycle apparatus of the present invention, the compressor 1 has the annular wall 24 that divides the second space 39 into an inner space 24a and an outer space 24b located outside the inner space 24a, and the first bypass flow path 35 is connected to the inner space 24a. The space 24a is connected, and the second bypass channel 36 is connected to the outer space 24b.

In addition, in the refrigeration cycle device of the present invention, the compressor 1 has an oil storage place 13 at the bottom, the first bypass flow path 35 is connected between the motor 4 and the oil storage place 13, and the second bypass flow path 36 is connected between the motor 4 and the oil storage place 13. 4 and the compression mechanism part 3.

Claims (4)

1. A refrigeration cycle device, wherein, The refrigeration cycle device has: The circulating flow path is formed by sequentially connecting a compressor, an oil separator, a first on-off valve, a condenser, a decompression device, and an evaporator through piping, and circulates R32 as a refrigerant; a first bypass flow path connecting the oil separator and the compressor through piping; a cooler disposed in the first bypass flow path; a second bypass flow path connecting the compressor and the condenser with piping; a second on-off valve, which is provided in the second bypass flow path; a control mechanism that opens either one of the first on-off valve and the second on-off valve and closes the other, During cooling operation, the first on-off valve is closed, and the second on-off valve is opened, During heating operation, the first on-off valve is opened, and the second on-off valve is closed. 2. The refrigeration cycle device according to claim 1, characterized in that, The compressor has: a compression mechanism; an electric motor; a first space into which the refrigerant ejected from the compression mechanism flows; a second space in which the electric motor is located; The cover that divides the two spaces, The circulation flow path is connected to the first space, The first bypass flow path and the second bypass flow path are connected to the second space. 3. The refrigeration cycle device according to claim 2, characterized in that, the compressor has an annular wall that divides the second space into an inner space and the outer space located outside the inner space, the first bypass channel is connected to the inner space, The second bypass channel is connected to the outer space. 4. The refrigeration cycle device according to claim 3, characterized in that, The compressor has an oil storage at the bottom, The first bypass flow path is connected between the electric motor and the oil reservoir, and the second bypass flow path is connected between the electric motor and the compression mechanism.