Multi-cylinder rotary compressor and refrigeration cycle device

Abstract

The present invention provides a multi-cylinder rotary compressor comprising: a sealed vessel constituting an outer shell; a rotating electrical machine accommodated inside the sealed vessel; a rotating shaft which is accommodated inside the sealed vessel and rotated by the rotating electrical machine, and has an eccentric shaft portion; a compression mechanism which is accommodated inside the sealed vessel and has a cylinder chamber for compressing refrigerant by eccentric motion of the eccentric shaft portion; and a supercharging mechanism accommodated inside the sealed vessel. The compression mechanism comprises a cylinder in which is formed an intake channel to take in low-pressure refrigerant from outside the sealed vessel into the cylinder chamber, a piston fitted on the eccentric shaft portion, a vane dividing the cylinder chamber formed by the inner circumference of the cylinder and the outer circumference of the piston into an intake chamber and a compression chamber, a bearing secured to one side of the cylinder in the height direction to occlude one side of the cylinder chamber, an occluding member which is secured to the other side of the cylinder in the height direction to occlude the other side of the cylinder chamber and in which is formed a discharge channel to discharge compressed refrigerant out of the compression chamber, and a discharge valve which is provided to the occluding member to occlude the discharge channel and which opens the discharge channel once the refrigerant compressed in the compression chamber of the cylinder chamber has reached a preset pressure. The supercharging mechanism comprises a coupling shaft rotatably supported by the occluding member, a turbine which is coupled to one end of the coupling shaft and which is rotated by the refrigerant discharged from the opened discharge channel, and an impeller which is coupled to the other end of the coupling shaft and which rotates in conjunction with the rotation of the turbine to promote the flow of the refrigerant through the intake channel.

Description

Multi-cylinder rotary compressor and refrigeration cycle device

[0001] The present disclosure relates to a multi-cylinder rotary compressor and a refrigeration cycle device.

[0002] Conventionally, there has been a turbocharger equipped with a supercharging mechanism (see, for example, Patent Document 1). The turbocharger of Patent Document 1 includes a casing, a motor, a rotor, rotating blades, a supercharger, a shaft, and a discharge pipe. The casing includes a main casing in which the motor, rotating blades, supercharger, and shaft are disposed, and an auxiliary casing in which the rotor is disposed. The main casing and the auxiliary casing are fixed to each other, and a partition wall is provided within the main casing. The partition wall defines a motor chamber and an accommodation chamber within the main casing. A shaft is rotatably supported by the partition wall, and rotating blades housed in the accommodation chamber are fixed to one end of the shaft, and a supercharger housed in the motor chamber is fixed to the other end of the shaft. The motor chamber accommodates a motor, and the auxiliary casing accommodates a rotor. An outlet provided in the auxiliary casing and a communication hole provided to communicate with the accommodation chamber of the main casing are connected via the discharge pipe. The main casing is formed with a discharge hole that communicates with the accommodation chamber and discharges compressed gas, and a suction hole that communicates with the motor chamber and draws in intake gas from outside the main casing.

[0003] In a turbocharger configured as described above, the rotor is rotated by the rotation of the motor, and gas compressed by the rotor in the sub-casing flows from the outlet of the sub-casing through the discharge pipe and into the accommodation chamber of the main casing via the communication hole. The gas flowing into the accommodation chamber of the main casing via the communication hole then drives the rotating impeller to rotate, and the gas is discharged from the discharge hole of the main casing. Meanwhile, intake gas flows in through the intake hole and is pressurized by the turbocharger rotating together with the rotating impeller, becoming denser and being drawn into the sub-casing.

[0004] Japanese Unexamined Patent Publication No. 51-3445

[0005] However, the turbocharger of Patent Document 1 is structured so that gas compressed by a rotor in a sub-casing is introduced into a housing chamber of the main casing through a discharge pipe provided outside the main casing and is then blown onto the rotating blades. As a result, there is a problem in that pressure loss occurs as the gas compressed by the rotor passes through the discharge pipe, making it impossible to rotate the rotating blades efficiently.

[0006] The present disclosure has been made to solve the above-mentioned problems, and aims to provide a multi-cylinder rotary compressor and a refrigeration cycle device that can reduce pressure loss by providing a compression mechanism with a supercharging mechanism that is driven by refrigerant discharged from the compression mechanism.

[0007] A multi-cylinder rotary compressor according to the present disclosure includes a sealed container forming an outer shell, a rotating electric machine housed in the sealed container, a rotating shaft housed in the sealed container and rotated by the rotating electric machine and having an eccentric shaft portion, a compression mechanism housed in the sealed container and having a cylinder chamber that compresses a refrigerant by eccentric motion of the eccentric shaft portion, and a supercharging mechanism housed in the sealed container, wherein the compression mechanism includes a cylinder formed with an intake passage that draws low-pressure refrigerant from outside the sealed container into the cylinder chamber, a piston fitted to the eccentric shaft portion, a vane that separates the cylinder chamber, which is formed by an inner periphery of the cylinder and an outer periphery of the piston, into an intake chamber and a compression chamber, and a cylinder support fixed to one side in a height direction of the cylinder. a closing member fixed to the other side of the cylinder in the height direction to close the other side of the cylinder chamber and having a discharge flow path formed therein for discharging compressed refrigerant to the outside of the compression chamber; and a discharge valve provided on the closing member to close the discharge flow path and to open the discharge flow path when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, and the supercharging mechanism comprises: a connecting shaft rotatably supported on the closing member; a turbine connected to one end of the connecting shaft and rotated by refrigerant discharged from the open discharge flow path; and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of refrigerant through the suction flow path.

[0008] In addition, the refrigeration cycle device according to the present disclosure includes the above-mentioned multi-cylinder rotary compressor, a radiator in which the refrigerant compressed by the multi-cylinder rotary compressor radiates heat, a pressure reducer that reduces the pressure of the refrigerant flowing out of the radiator, and an evaporator in which the refrigerant flowing out of the pressure reducer evaporates.

[0009] In the multi-cylinder rotary compressor and refrigeration cycle apparatus according to the present disclosure, the supercharging mechanism includes a connecting shaft rotatably supported by a closing member, a turbine connected to one end of the connecting shaft and rotated by refrigerant discharged from an open discharge passage, and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of refrigerant through the suction passage. In other words, because the compression mechanism is provided with a supercharging mechanism driven by refrigerant discharged from the compression mechanism, pressure loss as in the conventional system does not occur, and pressure loss can be reduced.

[0010] 1 is a longitudinal cross-sectional view showing an overall configuration of a multi-cylinder rotary compressor according to a first embodiment; 2 is a transverse cross-sectional view of a first cylinder of a compression mechanism of the multi-cylinder rotary compressor according to the first embodiment; 3 is a transverse cross-sectional view of a second cylinder of the compression mechanism of the multi-cylinder rotary compressor according to the first embodiment; 4 is a schematic explanatory diagram showing a refrigeration cycle apparatus including the multi-cylinder rotary compressor according to the first embodiment; 5 is a bottom perspective view showing a first partition plate, a first cylinder, and a first turbine of the multi-cylinder rotary compressor according to the first embodiment; 6 is a longitudinal cross-sectional view showing the first partition plate, the first cylinder, and a first turbine of the multi-cylinder rotary compressor according to the first embodiment; 7 is a bottom perspective view showing the first partition plate, the first cylinder, and a first turbine of the multi-cylinder rotary compressor according to the first embodiment; 8 is a bottom perspective view showing the first partition plate of the multi-cylinder rotary compressor according to the first embodiment; 9 is a top view showing the first partition plate of the multi-cylinder rotary compressor according to the first embodiment; 10 is a top perspective view showing a second partition plate, a second cylinder, and a second turbine of the multi-cylinder rotary compressor according to the first embodiment. 18 is a longitudinal cross-sectional view showing a second partition plate, a second cylinder, and a second turbine of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a top view showing the second partition plate, the second cylinder, and the second turbine of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a top perspective view showing the second partition plate of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a bottom view showing the second partition plate of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a longitudinal cross-sectional view showing a first cylinder of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a bottom view showing the first cylinder of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a bottom view showing the first cylinder and a first impeller of the multi-cylinder rotary compressor according to the first embodiment. FIG. 19 is a cross-sectional view taken along the arrows A-A in FIG. 18. FIG. 19 is a longitudinal cross-sectional view showing a second cylinder of the multi-cylinder rotary compressor according to the first embodiment. FIG. 20 is a top view showing the second cylinder of the multi-cylinder rotary compressor according to the first embodiment. 23 is a bottom view showing a second cylinder of the multi-cylinder rotary compressor according to Embodiment 1. FIG. 24 is a top view showing a second cylinder and a second impeller of the multi-cylinder rotary compressor according to Embodiment 1. FIG. 25 is a cross-sectional view taken along the line B-B of FIG.Fig. 1 is a longitudinal sectional view showing a compression mechanism of the multi-cylinder rotary compressor according to embodiment 1. Fig. 2 is a side view of a supercharging mechanism of the multi-cylinder rotary compressor according to embodiment 1. Fig. 3 is a view showing an impeller alone of the multi-cylinder rotary compressor according to embodiment 1. Fig. 4 is a view showing a turbine alone of the multi-cylinder rotary compressor according to embodiment 1. Fig. 5 is a view showing a connecting shaft alone of the multi-cylinder rotary compressor according to embodiment 1.

[0011] Hereinafter, embodiments of the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. Also, the size relationships of the components in the drawings may differ from those in reality.

[0012] Embodiment 1. Fig. 1 is a longitudinal cross-sectional view showing the overall configuration of a multi-cylinder rotary compressor 1 according to Embodiment 1. Fig. 2 is a transverse cross-sectional view of a first cylinder 21A of a compression mechanism 20 of the multi-cylinder rotary compressor 1 according to Embodiment 1. Fig. 3 is a transverse cross-sectional view of a second cylinder 21B of the compression mechanism 20 of the multi-cylinder rotary compressor 1 according to Embodiment 1.

[0013] [Configuration of Multi-Cylinder Rotary Compressor 1] The multi-cylinder rotary compressor 1 according to the first embodiment is a two-cylinder rotary compressor having two cylinders (a first cylinder 21A and a second cylinder 21B) as shown in FIG. 1 , i.e., a twin rotary compressor. The overall configuration of the multi-cylinder rotary compressor 1, which is a twin rotary compressor, will be described below. The multi-cylinder rotary compressor 1 includes a sealed container 10, a first suction pipe 2A, a second suction pipe 2B, a suction muffler 3, a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, and a discharge pipe 4. The sealed container 10 forms the outer shell of the multi-cylinder rotary compressor 1. The first suction pipe 2A and the second suction pipe 2B supply refrigerant into the sealed container 10. The suction muffler 3 is connected to the first suction pipe 2A and the second suction pipe 2B. The compression mechanism 20 is connected to the first suction pipe 2A and the second suction pipe 2B and compresses the refrigerant. The rotating electric machine 30 includes a rotor 31 and a stator 32. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31. The discharge pipe 4 discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. The configuration of the multi-cylinder rotary compressor 1 will be described in detail below.

[0014] (Sealed casing 10) The sealed casing 10 that forms the outer casing of the multi-cylinder rotary compressor 1 houses the compression mechanism 20, the rotating electric machine 30, the rotating shaft 40, etc. The sealed casing 10 includes a head 11, a bottom 13, and a body 12. The head 11 forms the outer casing of the upper part of the multi-cylinder rotary compressor 1. The bottom 13 forms the outer casing of the lower part of the multi-cylinder rotary compressor 1. The body 12 forms the outer casing of the middle part of the multi-cylinder rotary compressor 1, with the head 11 attached to its upper part and the bottom 13 attached to its lower part.

[0015] The head portion 11 constituting the upper portion of the sealed container 10 has, for example, a substantially bowl shape as shown in Fig. 1. A discharge pipe 4 that connects the inside and outside of the sealed container 10 is connected to the head portion 11.

[0016] As shown in Fig. 1 , the body portion 12 constituting the middle portion of the sealed container 10 has, for example, a substantially cylindrical shape. A first suction pipe 2A and a second suction pipe 2B for supplying refrigerant into the sealed container 10 are connected to the body portion 12. A stator 32 of a rotating electric machine 30 is attached to the inner circumferential surface of the body portion 12. A compression mechanism 20 is also attached to the inner circumferential surface of the body portion 12. In the first embodiment, a rolling piston type compression mechanism is used as the compression mechanism 20. In such cases, the compression mechanism 20 is often attached to the inner circumferential surface of the body portion 12, below the position where the stator 32 is attached.

[0017] The bottom 13 constituting the lower part of the sealed container 10 has, for example, a substantially bowl shape as shown in Fig. 1. Refrigerating machine oil 6, which is a lubricating oil, is stored in the bottom 13. That is, the refrigerating machine oil 6 is stored inside the sealed container 10. Then, this refrigerating machine oil 6 is supplied to the compression mechanism 20 and the like, thereby reducing friction at sliding parts of the compression mechanism 20 and the like.

[0018] (First Intake Pipe 2A and Second Intake Pipe 2B) As described above, the first intake pipe 2A and the second intake pipe 2B are connected to the body 12 of the sealed container 10. One end of the first intake pipe 2A is connected to a first intake passage 52A (see FIG. 25 ) of a first cylinder 21A of the compression mechanism 20 (described later). The other end of the first intake pipe 2A is connected to the intake muffler 3. One end of the second intake pipe 2B is connected to a second intake passage 52B (see FIG. 25 ) of a second cylinder 21B of the compression mechanism 20 (described later). The other end of the second intake pipe 2B is connected to the intake muffler 3. Note that, hereinafter, names beginning with "first" or "second" may be collectively referred to as names without the "first" or "second" prefix. For example, the "first cylinder 21A" and the "second cylinder 21B" are collectively referred to as "cylinder."

[0019] (Suction muffler 3) The suction muffler 3 functions as a muffler that reduces refrigerant noise and other noise generated when refrigerant flows into the multi-cylinder rotary compressor 1. The suction muffler 3 also functions as an accumulator that can store liquid refrigerant. As described above, the suction muffler 3 is connected to the first suction passage 52A of the first cylinder 21A and the second suction passage 52B of the second cylinder 21B via the first suction pipe 2A and the second suction pipe 2B.

[0020] (Compression mechanism 20) The compression mechanism 20 is connected to the rotating shaft 40 and compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40. In the first embodiment, the refrigerant that flows into the suction muffler 3 is supplied to the compression mechanism 20 via the first suction pipe 2A and the second suction pipe 2B. That is, the compression mechanism 20 draws in the external refrigerant via the first suction pipe 2A and the second suction pipe 2B and compresses this refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the sealed container 10. As described above, in the first embodiment, a rolling piston type compression mechanism is adopted as the compression mechanism 20.

[0021] 1 to 3, rotating shaft 40 according to the first embodiment includes first eccentric shaft portion 40A and second eccentric shaft portion 40B. Compression mechanism 20 includes first cylinder 21A, first piston 22A, first vane 50A, first spring 51A, upper bearing 24A, second cylinder 21B, second piston 22B, second vane 50B, second spring 51B, lower bearing 24B, first partition plate 25A, and second partition plate 25B. Note that, hereinafter, first partition plate 25A and second partition plate 25B are also referred to as bearings or blocking members.

[0022] The first cylinder 21A is cylindrical and defines a first cylinder chamber 55A in its center. The first cylinder 21A includes a first intake passage 52A through which refrigerant is drawn from the first suction pipe 2A, and a first discharge passage 53A through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. The first suction pipe 2A is press-fitted into the first intake passage 52A on the outer circumferential surface of the first cylinder 21A. The first piston 22A is fitted into the first eccentric shaft portion 40A of the rotary shaft 40 and rotates eccentrically together with the first eccentric shaft portion 40A to compress the refrigerant.

[0023] The first vane 50A is located between the first intake passage 52A and the first discharge passage 53A and is disposed in a first vane groove 56A formed to extend radially of the first cylinder 21A, separating the first cylinder chamber 55A into a first intake chamber 57A and a first compression chamber 58A. The first intake chamber 57A communicates with the first intake passage 52A, and the first compression chamber 58A communicates with the first discharge passage 53A.

[0024] The first spring hole 54A is formed at the radially outer end of the first vane groove 56A of the first cylinder 21A, penetrates the first cylinder 21A in the axial direction, and communicates with the first vane groove 56A. The first spring 51A is housed in the first spring hole 54A and presses the first vane 50A, which is attached to the tip of the first spring 51A, against the outer peripheral surface of the first piston 22A. The upper bearing 24A is disposed so as to abut against the upper end surface of the first cylinder 21A and closes the first cylinder chamber 55A. The upper bearing 24A rotatably supports the rotary shaft 40.

[0025] The second cylinder 21B is cylindrical and disposed below the first cylinder 21A, forming a second cylinder chamber 55B in its center. The second cylinder 21B has a second intake passage 52B through which refrigerant is drawn from the second suction pipe 2B and a second discharge passage 53B through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. The second suction pipe 2B is press-fitted into the second intake passage 52B on the outer circumferential surface of the second cylinder 21B. The second piston 22B is fitted into the second eccentric shaft portion 40B of the rotary shaft 40 and rotates eccentrically together with the second eccentric shaft portion 40B to compress the refrigerant.

[0026] The second vane 50B is located between the second intake passage 52B and the second discharge passage 53B, and is disposed in a second vane groove 56B formed to extend radially of the second cylinder 21B, separating the second cylinder chamber 55B into a second intake chamber 57B and a second compression chamber 58B. The second intake chamber 57B communicates with the second intake passage 52B, and the second compression chamber 58B communicates with the second discharge passage 53B.

[0027] The second spring hole 54B is formed at the radially outer end of the second vane groove 56B of the second cylinder 21B, penetrates the second cylinder 21B in the axial direction, and communicates with the second vane groove 56B. The second spring 51B is housed in the second spring hole 54B and presses the second vane 50B attached to the tip of the second spring 51B against the outer peripheral surface of the second piston 22B. The lower bearing 24B is disposed so as to abut against the lower end surface of the second cylinder 21B and closes the second cylinder chamber 55B. The lower bearing 24B rotatably supports the rotary shaft 40.

[0028] The first partition plate 25A is disposed so as to abut against the lower end surface of the first cylinder 21A and closes the first cylinder chamber 55A. The second partition plate 25B is disposed so as to abut against the upper end surface of the second cylinder 21B and closes the second cylinder chamber 55B. The lower end surface of the first partition plate 25A and the upper end surface of the second partition plate 25B are configured to abut against each other.

[0029] The first piston 22A rotates slidably within the first cylinder 21A. This first piston 22A is configured to be able to rotate eccentrically within the first cylinder 21A with respect to the center of rotation of the rotary shaft 40. Hereinafter, rotation eccentrically with respect to the center of rotation of the rotary shaft 40 will be referred to as eccentric rotation. Furthermore, the second piston 22B rotates slidably within the second cylinder 21B. This second piston 22B is configured to be able to rotate eccentrically within the second cylinder 21B.

[0030] Furthermore, the first piston 22A is connected to the rotary shaft 40 so as to be able to rotate within the first cylinder 21A with a phase shift of 180 degrees relative to the rotational phase of the second piston 22B when it rotates within the second cylinder 21B. In other words, the second piston 22B is connected to the rotary shaft 40 so as to be able to rotate within the second cylinder 21B with a phase shift of −180 degrees relative to the rotational phase of the first piston 22A when it rotates within the first cylinder 21A.

[0031] The upper bearing 24A is provided with a first discharge valve 26A (see FIG. 6 ), which discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A. When the first discharge valve 26A opens, the first discharge flow path 53A communicates with the first discharge muffler 23A. The lower bearing 24B is provided with a second discharge valve 26B (see FIG. 11 ), which discharges the refrigerant compressed by the second cylinder 21B and the second piston 22B. When the second discharge valve 26B opens, the second discharge flow path 53B communicates with the second discharge muffler 23B.

[0032] (Rotating electric machine 30 and rotating shaft 40) As shown in Figure 1, the rotating electric machine 30 has a rotor 31 that transmits its own rotation to the rotating shaft 40, and a stator 32 that is configured by attaching multiple phase windings to a laminated core.

[0033] The rotating shaft 40 is connected to the rotating electric machine 30 and rotates by the power of the rotating electric machine 30. The rotating shaft 40 also transmits the power of the rotating electric machine 30 to the compression mechanism 20. In the first embodiment, an upper end side of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30. As a result, the rotating shaft 40 rotates together with the rotation of the rotor 31. The rotating shaft 40 shown in FIG. 1 rotates around an axis extending in the vertical direction of the page. The lower end side of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end side of the rotating shaft 40 is rotatably supported by an upper bearing 24A and a lower bearing 24B of the compression mechanism 20. The rotating shaft 40 has a first eccentric shaft portion 40A and a second eccentric shaft portion 40B provided between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B. The rotating shaft 40 is connected such that the first piston 22A fitted to the first eccentric shaft portion 40A and the second piston 22B fitted to the second eccentric shaft portion 40B are capable of eccentric rotation. As a result, the rotating shaft 40 also rotates in conjunction with the rotation of the rotor 31, causing the first piston 22A and the second piston 22B to perform eccentric rotation. The refrigerant is compressed by the first cylinder 21A and the first piston 22A, and the refrigerant is compressed by the second cylinder 21B and the second piston 22B. In other words, the compression mechanism 20 compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

[0034] (Discharge Pipe 4) The discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. In other words, the discharge pipe 4 is a pipe that discharges the high-temperature, high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10.

[0035] (Centrifugal pump 45) The rotating shaft 40 is formed with an oil feed hole 42 that opens at the lower end 41 of the rotating shaft 40. The oil feed hole 42 extends along the rotation center of the rotating shaft 40. The rotating shaft 40 also has a first oil feed port 43 and a second oil feed port 44. The first oil feed port 43 and the second oil feed port 44 serve as flow paths that supply refrigeration oil 6 sucked into the oil feed hole 42 to sliding parts of the compression mechanism 20. One end of each of the first oil feed port 43 and the second oil feed port 44 communicates with the oil feed hole 42. The other end of each of the first oil feed port 43 and the second oil feed port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 that faces the compression mechanism 20. In the first embodiment, the other end of the first oil feed port 43 opens at a location that faces the upper bearing 24A of the compression mechanism 20. The other end of the second oil fill port 44 opens at a location facing the lower bearing 24B of the compression mechanism 20.

[0036] A centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is formed by twisting a plate-like member. The centrifugal pump 45 is a fluid machine that uses centrifugal force generated by the rotational motion of the rotating shaft 40 to pump up refrigerating machine oil 6 as a lubricant stored in the bottom 13 of the sealed container 10. The refrigerating machine oil 6 pumped up into the oil supply hole 42 by the centrifugal pump 45 is supplied to sliding parts of the compression mechanism 20. Specifically, a portion of the refrigerating machine oil 6 pumped up into the oil supply hole 42 is supplied through a first oil supply port 43 to a sliding part between the upper bearing 24A of the compression mechanism 20 and the rotating shaft 40. A portion of the refrigerating machine oil 6 pumped up into the oil supply hole 42 is supplied through a second oil supply port 44 to a sliding part between the lower bearing 24B of the compression mechanism 20 and the rotating shaft 40. As the refrigeration oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil or the like is used.

[0037] [Operation of the rotating electric machine 30] A current is supplied from a power source (not shown) to windings provided on the laminated core of the stator 32, generating a rotating magnetic field in the stator 32. This causes the rotating magnetic field of the stator 32 to act on the permanent magnets provided in the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted to the first piston 22A and the second piston 22B via the rotating shaft 40, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.

[0038] [Refrigerant Flow] The eccentric rotation of the first piston 22A and the second piston 22B draws refrigerant into the multi-cylinder rotary compressor 1. Specifically, the eccentric rotation of the first piston 22A and the second piston 22B causes low-pressure refrigerant outside the multi-cylinder rotary compressor 1 to flow into the suction muffler 3. Then, of the low-pressure refrigerant that has flowed into the suction muffler 3, low-pressure gaseous refrigerant flows into the compression mechanism 20 of the multi-cylinder rotary compressor 1 via the first suction pipe 2A and the second suction pipe 2B. A portion of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the first cylinder 21A and the first piston 22A to become high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the first discharge muffler 23A through the first discharge flow path 53A and a first outlet hole 151, a second outlet hole 152, and a third outlet hole 153 (see FIG. 25 ) described below. The high-temperature, high-pressure gaseous refrigerant that has flowed into the first discharge muffler 23A is released into the space within the sealed container 10 from a discharge hole 23Aa (see FIG. 25 ) provided in the first discharge muffler 23A and described below. The high-temperature, high-pressure gaseous refrigerant that has been released into the space within the sealed container 10 then moves to the upper part of the space within the sealed container 10 through gaps between the rotating electrical machine 30 and the like, and is discharged from the discharge piping 4.

[0039] The remainder of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the first discharge muffler 23A via the second discharge flow path 53B and a first outlet hole 151, a second outlet hole 152, and a third outlet hole 153 (see FIG. 25 ), which will be described later. The high-temperature, high-pressure gaseous refrigerant sent into the first discharge muffler 23A is then released into the space within the sealed container 10 from a discharge hole 23Aa (see FIG. 25 ), which will be described later, provided in the first discharge muffler 23A. The high-temperature, high-pressure gaseous refrigerant released into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., between the rotating electrical machine 30 and the like, and is then discharged from the discharge piping 4.

[0040] Furthermore, refrigeration oil 6 stored in bottom 13 within sealed container 10 is sucked up from lower end 41 of oil feed hole 42 by centrifugal pump 45, which rotates together with rotating shaft 40. Refrigeration oil 6 sucked up from lower end 41 of oil feed hole 42 flows as lubricating oil from first oil feed port 43 into the gap between upper bearing 24A and rotating shaft 40. Furthermore, refrigeration oil 6 flows as lubricating oil from second oil feed port 44 into the gap between lower bearing 24B and rotating shaft 40. By refrigeration oil 6 flowing between these gaps, rotating shaft 40 can smoothly transmit rotational driving force to first piston 22A and second piston 22B.

[0041] Furthermore, a portion of the refrigeration oil 6 that flows from the first oil supply port 43 between the upper bearing 24A and the rotating shaft 40 flows between the upper bearing 24A and the upper surface of the first piston 22A. A portion of the refrigeration oil 6 that flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40 flows between the lower bearing 24B and the lower surface of the second piston 22B. The refrigeration oil 6 is used to smoothly rotate the first piston 22A and the second piston 22B, but a portion of the refrigeration oil 6 is compressed together with the low-pressure gaseous refrigerant and is discharged in a state contained in the high-temperature, high-pressure gaseous refrigerant.

[0042] [Configuration and Operation of Refrigeration Cycle Apparatus 200] FIG. 4 is a schematic diagram illustrating a refrigeration cycle apparatus 200 including a multi-cylinder rotary compressor 1 according to the first embodiment. Next, the refrigeration cycle apparatus 200 including the multi-cylinder rotary compressor 1 will be described with reference to FIG. 4. The refrigeration cycle apparatus 200 is used for various purposes, such as an air conditioner, a hot water heater, and a refrigeration apparatus. FIG. 4 illustrates an example in which the refrigeration cycle apparatus 200 is used as an air conditioner. Therefore, the refrigeration cycle apparatus 200 illustrated in FIG. 4 includes an indoor heat exchanger 204 that functions as a radiator during heating operation and an outdoor heat exchanger 202 that functions as an evaporator during heating operation. The refrigeration cycle apparatus 200 illustrated in FIG. 4 is also capable of cooling operation. Therefore, the refrigeration cycle apparatus 200 includes a flow path switching valve 201. The refrigeration cycle device 200 comprises a multi-cylinder rotary compressor 1 equipped with an intake muffler 3 connected to the intake side of the multi-cylinder rotary compressor 1, a flow path switching valve 201 connected to the discharge side of the multi-cylinder rotary compressor 1, an outdoor heat exchanger 202, a pressure reducer 203, and an indoor heat exchanger 204, which are connected in sequence via piping to form a refrigerant circuit through which the refrigerant circulates.

[0043] The refrigerant circulating in the refrigerant circuit may be a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential (GWP). Examples of the refrigerant include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixture of two or more of these, or a mixture of any of these with another refrigerant. Examples of the refrigerant include a mixture containing R1132(E) or a mixture containing R1123. Furthermore, examples of the refrigerant include mixed refrigerants of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, R459A, and R410A.

[0044] The flow path switching valve 201 is, for example, a four-way valve that switches the refrigerant flow direction to switch between cooling and heating operation. Note that the flow path switching valve 201 may be a combination of a two-way valve and a three-way valve instead of a four-way valve. The pressure reducer 203 reduces the pressure of the refrigerant to expand it. The pressure reducer 203 is, for example, an electronic expansion valve with an adjustable throttle opening. By adjusting the throttle opening, the pressure of the refrigerant flowing into the indoor heat exchanger 204 during cooling operation and the pressure of the refrigerant flowing into the outdoor heat exchanger 202 during heating operation is controlled. The outdoor heat exchanger 202 functions as an evaporator or a radiator, exchanging heat between the air and the refrigerant to evaporate and gasify the refrigerant or condense and liquefy the refrigerant. The outdoor heat exchanger 202 functions as an evaporator during heating operation and as a radiator during cooling operation. The indoor heat exchanger 204 functions as an evaporator or a radiator, and exchanges heat between the air and the refrigerant to evaporate and gasify or condense and liquefy the refrigerant. The indoor heat exchanger 204 functions as a radiator during heating operation and as an evaporator during cooling operation.

[0045] When the refrigeration cycle apparatus 200 is used as an air conditioner, for example, the indoor heat exchanger 204 is mounted in an indoor apparatus, and the flow path switching valve 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor apparatus.

[0046] Next, the operation of the refrigeration cycle apparatus 200 during heating operation and cooling operation will be described. When the refrigeration cycle apparatus 200 performs heating operation, the flow path switching valve 201 switches to the flow path shown by the solid line in FIG. 4 . As a result, the discharge pipe 4 of the multi-cylinder rotary compressor 1 is connected to the indoor heat exchanger 204, and the suction muffler 3 of the multi-cylinder rotary compressor 1 is connected to the outdoor heat exchanger 202. That is, the indoor heat exchanger 204 functions as a radiator, and the outdoor heat exchanger 202 functions as an evaporator. In this state, when high-temperature, high-pressure gaseous refrigerant compressed by the multi-cylinder rotary compressor 1 is discharged from the multi-cylinder rotary compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that flows into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, becoming a high-pressure liquid refrigerant that flows out of the indoor heat exchanger 204. At this time, the indoor air is heated. Note that some types of refrigerants, such as carbon dioxide refrigerants, do not condense when releasing heat. When a refrigerant that condenses when releasing heat is used, the radiator may also be called a condenser.

[0047] The high-pressure liquid refrigerant flowing out from the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant flowing into the pressure reducer 203 is reduced in pressure by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out from the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant flowing out from the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure two-phase gas-liquid refrigerant flowing into the outdoor heat exchanger 202 absorbs heat from the outdoor air and evaporates, flowing out from the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant flowing out from the outdoor heat exchanger 202 is drawn into the suction muffler 3 of the multi-cylinder rotary compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerant sucked into the suction muffler 3 of the multi-cylinder rotary compressor 1 is compressed by the compression mechanism 20 of the multi-cylinder rotary compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the multi-cylinder rotary compressor 1. That is, when the refrigeration cycle apparatus 200 performs heating operation, the refrigerant circulates as shown by the solid arrows in Figure 4.

[0048] When the refrigeration cycle apparatus 200 performs cooling operation, the flow path switching valve 201 switches to the flow path indicated by the dashed line in FIG. 4 . As a result, the discharge pipe 4 of the multi-cylinder rotary compressor 1 is connected to the outdoor heat exchanger 202, and the suction muffler 3 of the multi-cylinder rotary compressor 1 is connected to the indoor heat exchanger 204. That is, the outdoor heat exchanger 202 functions as a radiator, and the indoor heat exchanger 204 functions as an evaporator. In this state, when high-temperature, high-pressure gaseous refrigerant compressed by the multi-cylinder rotary compressor 1 is discharged from the multi-cylinder rotary compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that has flowed into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, becoming a high-pressure liquid refrigerant that flows out of the outdoor heat exchanger 202.

[0049] The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flowed into the pressure reducer 203 is then decompressed by the pressure reducer 203 to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows into the indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, and flows out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. At this time, the indoor air is cooled. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant that flows out of the indoor heat exchanger 204 is drawn into the suction muffler 3 of the multi-cylinder rotary compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerant drawn into the suction muffler 3 of the multi-cylinder rotary compressor 1 is compressed by the compression mechanism 20 of the multi-cylinder rotary compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the multi-cylinder rotary compressor 1. That is, when the refrigeration cycle apparatus 200 performs cooling operation, the refrigerant circulates as shown by the dashed arrows in FIG. 4.

[0050] FIG. 5 is a bottom perspective view showing a first partition plate 25A, a first cylinder 21A, and a first turbine 28A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 6 is a vertical cross-sectional view showing the first partition plate 25A, the first cylinder 21A, and the first turbine 28A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 7 is a bottom perspective view showing the first partition plate 25A, the first cylinder 21A, and the first turbine 28A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 8 is a bottom perspective view showing the first partition plate 25A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 9 is a top perspective view showing the first partition plate 25A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 10 is a top perspective view showing a second partition plate 25B, a second cylinder 21B, and a second turbine 28B of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 11 is a longitudinal cross-sectional view showing a second partition plate 25B, a second cylinder 21B, and a second turbine 28B of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 12 is a top view showing the second partition plate 25B, the second cylinder 21B, and the second turbine 28B of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 13 is a top perspective view showing the second partition plate 25B of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 14 is a bottom view showing the second partition plate 25B of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 15 is a longitudinal cross-sectional view showing a first cylinder 21A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 16 is a bottom view showing the first cylinder 21A of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 17 is a top view showing the first cylinder 21A of the multi-cylinder rotary compressor 1 according to the first embodiment. Figure 18 is a bottom view showing the first cylinder 21A and the first impeller 29A of the multi-cylinder rotary compressor 1 according to the first embodiment. Figure 19 is a cross-sectional view taken along the line A-A in Figure 18. Figure 20 is a vertical cross-sectional view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to the first embodiment. Figure 21 is a top view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to the first embodiment. Figure 22 is a bottom view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to the first embodiment.Fig. 23 is a top view showing the second cylinder 21B and the second impeller 29B of the multi-cylinder rotary compressor 1 according to embodiment 1. Fig. 24 is a cross-sectional view taken along the line B-B in Fig. 23. Note that Fig. 6 and Fig. 24 are shown upside down.

[0051] (Supercharging Mechanisms T1, T2) Next, the supercharging mechanisms T1, T2 according to the first embodiment will be described. As shown in FIGS. 5 to 9 , a first through-hole 25Ab is formed in the first partition plate 25A, penetrating it in the axial direction. A first connecting shaft 27A is rotatably attached to the first through-hole 25Ab formed in the first partition plate 25A. One end of the first connecting shaft 27A protrudes below the upper surface of the first partition plate 25A, and the other end protrudes above the upper surface of the first partition plate 25A. A first turbine 28A is attached to one end of the first connecting shaft 27A and is disposed below the first cylinder 21A. A first impeller 29A is attached to the other end of the first connecting shaft 27A and is disposed above the first partition plate 25A. As shown in FIGS. 6 and 15 to 19 , the first impeller 29A is disposed in the first communication chamber 21Ab, which is part of the first intake passage 52A. The refrigerant discharged into the space partitioned by the first partition plate 25A is blown onto the first turbine 28A attached to one end of the first connecting shaft 27A, which is rotatably attached to the first through-hole 25Ab of the first partition plate 25A, causing the first turbine 28A to rotate. The rotation of the first turbine 28A also rotates the first impeller 29A attached to the other end of the first connecting shaft 27A, thereby promoting the flow of refrigerant through the first intake passage 52A and supercharging the refrigerant into the first intake chamber 57A. The first turbine 28A, the first connecting shaft 27A, and the first impeller 29A constitute a supercharging mechanism T1.

[0052] As shown in FIGS. 10 to 14 , a second through-hole 25Bb is formed in the second partition plate 25B, penetrating it in the axial direction. A second connecting shaft 27B is rotatably attached to the second through-hole 25Bb formed in the second partition plate 25B. One end of the second connecting shaft 27B protrudes above the lower surface of the second partition plate 25B, and the other end protrudes below the lower surface of the second partition plate 25B. A second turbine 28B is attached to one end of the second connecting shaft 27B and is disposed above the second cylinder 21B. A second impeller 29B is attached to the other end of the second connecting shaft 27B and is disposed below the second partition plate 25B. As shown in FIGS. 11 and 20 to 24 , the second impeller 29B is disposed in a second communication chamber 21Bb, which is part of the second intake passage 52B. The refrigerant discharged into the space partitioned by the second partition plate 25B is blown onto a second turbine 28B attached to one end of a second connecting shaft 27B rotatably attached to the second through-hole 25Bb of the second partition plate 25B, causing the second turbine 28B to rotate. The rotation of the second turbine 28B also rotates a second impeller 29B attached to the other end of the second connecting shaft 27B, thereby promoting the flow of refrigerant through the second intake passage 52B and supercharging the refrigerant into the second suction chamber 57B. The second turbine 28B, the second connecting shaft 27B, and the second impeller 29B form a supercharging mechanism T2.

[0053] As shown in FIGS. 5 to 9 , a first recess 124A recessed in the height direction is provided on the surface of the first partition plate 25A opposite the first cylinder 21A. The first discharge valve 26A, the first valve guard 15A, and the first turbine 28A are disposed in the first recess 124A of the first partition plate 25A. A first discharge flow path 53A is formed in a first bottom surface 124Aa of the first recess 124A. That is, the first discharge flow path 53A is formed in the first cylinder 21A and the first partition plate 25A. The side surface of the first recess 124A forms a first guide surface 124Ab that guides the refrigerant discharged from the first discharge flow path 53A to the first turbine 28A.

[0054] As shown in Figures 10 to 14, a second recess 124B recessed in the height direction is provided on the surface of the second partition plate 25B opposite the second cylinder 21B. The second discharge valve 26B, the second valve guard 15B, and the second turbine 28B are disposed in the second recess 124B of the second partition plate 25B. The second discharge flow path 53B is formed on a second bottom surface 124Ba of the second recess 124B. That is, the second discharge flow path 53B is formed in the second cylinder 21B and the second partition plate 25B. The side surface of the second recess 124B forms a second guide surface 124Bb that guides the refrigerant discharged from the second discharge flow path 53B to the second turbine 28B.

[0055] With this configuration, the refrigerant discharged from the first discharge passage 53A to the outside of the first compression chamber 58A can be guided along the first guide surface 124Ab to the first turbine 28A, thereby efficiently rotating the first turbine 28A. Similarly, the refrigerant discharged from the second discharge passage 53B to the outside of the second compression chamber 58B can be guided along the second guide surface 124Bb to the second turbine 28B, thereby efficiently rotating the second turbine 28B.

[0056] 5 to 9, the side surfaces of the first recess 124A define two first guide surfaces 124Ab, and the two first guide surfaces 124Ab are configured to approach each other as they approach the first turbine 28A. Therefore, when the refrigerant discharged from the first discharge passage 53A to the outside of the first compression chamber 58A is guided along the first guide surfaces 124Ab to the first turbine 28A, the density of the refrigerant guided from the first discharge passage 53A toward the first turbine 28A can be increased, thereby enabling the first turbine 28A to rotate efficiently. Similarly, as shown in FIGS. 10 to 14, the side surfaces of the second recess 124B define two second guide surfaces 124Bb, and the two second guide surfaces 124Bb are configured to approach each other as they approach the second turbine 28B. Therefore, when the refrigerant discharged from the second discharge flow path 53B out of the second compression chamber 58B is guided along the second guide surface 124Bb to the second turbine 28B, the density of the refrigerant guided from the second discharge flow path 53B toward the second turbine 28B can be increased, allowing the second turbine 28B to rotate efficiently.

[0057] As shown in FIG. 6 , the first discharge valve 26A is movable like a cantilever and includes a first distal end 26Aa, whose distal end closes or opens the first discharge flow path 53A, and a first proximal end 26Ab, whose proximal end is fixed to the first partition plate 25A. The first discharge valve 26A is supported by a first valve stopper 15A. The first valve stopper 15A is a long plate-like member that is thicker than the first discharge valve 26A and protects the first discharge valve 26A from deformation while restricting the movable range of the first discharge valve 26A. The first turbine 28A is located on the opposite side of the first distal end 26Aa of the first discharge valve 26A from the first proximal end 26Ab of the first discharge valve 26A. As shown in FIG. 11 , the second discharge valve 26B is movable like a cantilever and includes a second distal end 26Ba, whose distal end closes or opens the second discharge flow path 53B, and a second proximal end 26Bb, whose proximal end is fixed to the second partition plate 25B. The second discharge valve 26B is supported by a second valve stopper 15B. The second valve stopper 15B is a long plate-like member that is thicker than the second discharge valve 26B and protects the second discharge valve 26B from deformation while restricting the movable range of the second discharge valve 26B. The second turbine 28B is located on the opposite side of the second distal end 26Ba of the second discharge valve 26B from the second proximal end 26Bb of the second discharge valve 26B.

[0058] As described above, the first discharge valve 26A moves in a cantilevered manner. Therefore, when the refrigerant compressed in the first compression chamber 58A of the first cylinder chamber 55A reaches a predetermined pressure, the cantilevered first tip 26Aa of the first discharge valve 26A is lifted, opening the first discharge flow path 53A. The refrigerant discharged from the open first discharge flow path 53A is then blown toward the first turbine 28A, and the pressure energy of the blown refrigerant efficiently rotates the first turbine 28A. Similarly, the second discharge valve 26B moves in a cantilevered manner. Therefore, when the refrigerant compressed in the second compression chamber 58B of the second cylinder chamber 55B reaches a predetermined pressure, the cantilevered second tip 26Ba of the second discharge valve 26B is lifted, opening the second discharge flow path 53B. The refrigerant discharged from the opened second discharge flow path 53B is blown out toward the second turbine 28B, and the pressure energy of the blown out refrigerant efficiently rotates the second turbine 28B.

[0059] Figure 25 is a longitudinal cross-sectional view showing the compression mechanism 20 of the multi-cylinder rotary compressor 1 according to the first embodiment. As shown in Figure 25, a first discharge muffler 23A is fixed to the upper bearing 24A on the side opposite the first cylinder 21A. A discharge hole 23Aa is formed in the first discharge muffler 23A. Furthermore, a second discharge muffler 23B is fixed to the lower bearing 24B on the side opposite the second cylinder 21B.

[0060] Conventionally, rotary compressors have been known to include a discharge muffler covering the discharge valve to reduce the discharge noise of refrigerant discharged from the discharge flow path when the discharge valve is open. The muffler prevents the refrigerant from impinging on the sealed container and instead collides with the discharge muffler, resulting in a loss of pressure. However, in the first embodiment, the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B is configured to impinge on the first turbine 28A and the second turbine 28B, respectively, before impinging on the first discharge muffler 23A and the second discharge muffler 23B. This allows the pressure energy of the refrigerant to be used to efficiently rotate the first turbine 28A and the second turbine 28B.

[0061] Furthermore, the first discharge muffler 23A and the second discharge muffler 23B can muffle noise by preventing the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B from colliding with the first discharge muffler 23A and the second discharge muffler 23B, respectively, rather than colliding with the sealed container 10. In this manner, the first discharge muffler 23A and the second discharge muffler 23B can reduce the discharge noise of the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B. Furthermore, the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B is configured to collide with the first turbine 28A and the second turbine 28B, respectively, before colliding with the first discharge muffler 23A and the second discharge muffler 23B. Therefore, the pressure energy of the refrigerant can be utilized to efficiently rotate the first turbine 28A and the second turbine 28B.

[0062] As shown in Figures 5 to 9, a first closing member wall 25Aa is formed around the entire outer periphery of the surface of the first partition plate 25A opposite to the first cylinder 21A. Also, as shown in Figures 10 to 14, a second closing member wall 25Ba is formed around the entire outer periphery of the surface of the second partition plate 25B opposite to the second cylinder 21B. The entire periphery of the first closing member wall 25Aa of the first partition plate 25A and the entire periphery of the second closing member wall 25Ba of the second partition plate 25B are configured to abut against each other.

[0063] 25 , the first partition plate 25A has a first outlet hole 151 that penetrates from the side opposite the first cylinder 21A toward the first cylinder 21A and discharges the refrigerant. The first cylinder 21A has a second outlet hole 152 that communicates with the first outlet hole 151 and penetrates from the first partition plate 25A toward the upper bearing 24A. The upper bearing 24A has a third outlet hole 153 that communicates with the second outlet hole 152 and penetrates from the first cylinder 21A toward the surface opposite the first cylinder 21A. Therefore, the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B can be discharged from the first blocking member wall portion 25Aa and the second blocking member wall portion 25Ba via the first outlet hole 151, the second outlet hole 152, and the third outlet hole 153.

[0064] 25 , the first discharge muffler 23A has a discharge hole 23Aa. The refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged into the first discharge muffler 23A and then released into the sealed container 10 from the discharge hole 23Aa. The refrigerant compressed by the second cylinder 21B and the second piston 22B flows into the first discharge muffler 23A through the first outlet hole 151, the second outlet hole 152, and the third outlet hole 153. The refrigerant that has flowed into the first discharge muffler 23A is released into the sealed container 10 from the discharge hole 23Aa of the first discharge muffler 23A.

[0065] As the rotary shaft 40 is rotated by the rotary electric machine 30, the first eccentric shaft portion 40A and the second eccentric shaft portion 40B of the rotary shaft 40 perform eccentric motion within the first cylinder chamber 55A and the second cylinder chamber 55B, respectively. As a result, when the refrigerant compressed in the first compression chamber 58A of the first cylinder chamber 55A and the refrigerant compressed in the second compression chamber 58B of the second cylinder chamber 55B reach their respective preset pressures, they lift the first tip portion 26Aa of the first discharge valve 26A and the second tip portion 26Ba of the second discharge valve 26B. This opens the first discharge flow path 53A and the second discharge flow path 53B, and the refrigerant is discharged from the first discharge flow path 53A and the second discharge flow path 53B to the outside of the first compression chamber 58A and the outside of the second compression chamber 58B, respectively. The refrigerant discharged from the first compression chamber 58A and the second compression chamber 58B rotates the first turbine 28A and the second turbine 28B, respectively. The rotation of the first turbine 28A and the second turbine 28B then rotates the first impeller 29A and the second impeller 29B. The rotation of the first impeller 29A and the second impeller 29B promotes the flow of refrigerant through the first intake passage 52A and the second intake passage 52B.

[0066] In this way, the pressure energy of the refrigerant discharged from the first discharge passage 53A and the second discharge passage 53B to the outside of the first compression chamber 58A and the outside of the second compression chamber 58B is utilized to rotate the first impeller 29A and the second impeller 29B. This promotes the flow of refrigerant through the first suction passage 52A and the flow of refrigerant through the second suction passage 52B, respectively. As a result, the refrigerant is supercharged to the first suction chamber 57A and the second suction chamber 57B, thereby increasing the capacity of the multi-cylinder rotary compressor 1. Furthermore, by increasing the pressure in the first suction chamber 57A and the second suction chamber 57B, the amount of work per rotation of the multi-cylinder rotary compressor 1 can be reduced.

[0067] More specifically, in the turbocharger of the related art, gas is guided from an outlet provided in the sub-casing to the rotary vanes via a discharge pipe provided outside the main casing, thereby recovering power. In contrast, in the multi-cylinder rotary compressor 1 according to the first embodiment, refrigerant is guided from the first discharge flow path 53A and the second discharge flow path 53B provided in the first partition plate 25A and the second partition plate 25B to the first turbine 28A and the second turbine 28B of the supercharging mechanisms T1 and T2 provided in the first partition plate 25A and the second partition plate 25B, thereby recovering power. Therefore, unlike the conventional system, pressure loss does not occur, and power recovery can be performed efficiently. In this way, by providing the supercharging mechanisms T1 and T2, which are driven by the refrigerant discharged from the compression mechanism 20, in the compression mechanism 20, pressure loss can be reduced.

[0068] FIG. 26 is a side view of the supercharging mechanisms T1 and T2 of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 27 is a view of the impeller alone of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 28 is a view of the turbine alone of the multi-cylinder rotary compressor 1 according to the first embodiment. FIG. 29 is a view of the connecting shaft alone of the multi-cylinder rotary compressor 1 according to the first embodiment. Note that (a) of FIG. 26 shows a side view of the supercharging mechanism T1, and (b) shows a side view of the supercharging mechanism T2. Also, (a) of FIG. 27 and FIG. 28 show a top view, (b) a side view, (c) a bottom view, and (d) a perspective view, respectively. Also, (a) of FIG. 29 shows a top view, (b) a side view, and (c) a perspective view, respectively. 27 shows the first impeller 29A, but the second impeller 29B has the same shape and is therefore not shown. Also, FIG. 28 shows the first turbine 28A, but the second turbine 28B has the same shape and is therefore not shown. Also, FIG. 29 shows the first connecting shaft 27A, but the second connecting shaft 27B has the same shape and is therefore not shown.

[0069] As shown in Figures 26 to 29, the first turbine 28A has a circular shape in plan view. The first turbine 28A also has a first turbine blade set 28Aa consisting of a plurality of blades that allow the refrigerant to flow in from the radially outer side and flow out toward the axial direction. The first impeller 29A also has a first impeller blade set 29Aa consisting of a plurality of blades that allow the refrigerant to flow in from the axial direction and flow out toward the radially outer side. Similarly, the second turbine 28B also has a circular shape in plan view. The second turbine 28B also has a second turbine blade set 28Ba consisting of a plurality of blades that allow the refrigerant to flow in from the radially outer side and flow out toward the axial direction. The second impeller 29B also has a second impeller blade set 29Ba consisting of a plurality of blades that allow the refrigerant to flow in from the axial direction and flow out toward the radially outer side.

[0070] In this way, by providing the first turbine blade set 28Aa and the second turbine blade set 28Ba, it is possible to arrange the first discharge valve 26A and the second discharge valve 26B radially outward from the first turbine 28A and the second turbine 28B. Furthermore, by providing the first impeller blade set 29Aa and the second impeller blade set 29Ba, it is possible to arrange the first suction chamber 57A and the second suction chamber 57B radially outward from the first impeller 29A and the second impeller 29B.

[0071] The compression mechanism 20 of the multi-cylinder rotary compressor 1 according to the first embodiment includes two cylinder chambers, a first cylinder chamber 55A and a second cylinder chamber 55B, and the first partition plate 25A and the second partition plate 25B that define the first cylinder chamber 55A are shared with the first partition plate 25A and the second partition plate 25B that define the second cylinder chamber 55B. That is, the multi-cylinder rotary compressor 1 according to the first embodiment is a twin rotary compressor. Therefore, the multi-cylinder rotary compressor 1 according to the first embodiment can increase the refrigerant compression capacity compared to a single rotary compressor that has one cylinder chamber.

[0072] Although the multi-cylinder rotary compressor 1 according to the first embodiment is a twin rotary compressor, the present invention is not limited to this and may be a triple rotary compressor or the like.

[0073] As described above, the multi-cylinder rotary compressor 1 according to the first embodiment includes a sealed container 10 that forms an outer shell, a rotating electric machine 30 housed in the sealed container 10, a rotating shaft 40 that is housed in the sealed container 10 and rotated by the rotating electric machine 30 and has an eccentric shaft portion, a compression mechanism 20 that is housed in the sealed container 10 and has a cylinder chamber that compresses refrigerant by eccentric motion of the eccentric shaft portion, and supercharging mechanisms T1 and T2 housed in the sealed container 10. The compression mechanism 20 includes a cylinder formed with an intake passage that draws low-pressure refrigerant from outside the sealed container 10 into the cylinder chamber, a piston fitted with the eccentric shaft portion, a vane that separates the cylinder chamber, which is formed by the inner periphery of the cylinder and the outer periphery of the piston, into a suction chamber and a compression chamber, and a cylinder height. a closing member fixed to the other side of the cylinder in the height direction and closing the other side of the cylinder chamber, with a discharge flow path formed therein for discharging compressed refrigerant out of the compression chamber; and a discharge valve provided on the closing member and closing the discharge flow path, which opens the discharge flow path when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure. The supercharging mechanisms T1 and T2 each include a connecting shaft rotatably supported by the closing member, a turbine connected to one end of the connecting shaft and rotated by the refrigerant discharged from the open discharge flow path, and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of refrigerant through the suction flow path.

[0074] In the multi-cylinder rotary compressor 1 according to the first embodiment, the supercharging mechanisms T1, T2 include a connecting shaft rotatably supported by a blocking member, a turbine connected to one end of the connecting shaft and rotated by the refrigerant discharged from the open discharge passage, and an impeller connected to the other end of the connecting shaft and rotating with the rotation of the turbine to promote the flow of the refrigerant through the suction passage. In other words, because the supercharging mechanisms T1, T2 driven by the refrigerant discharged from the compression mechanism 20 are provided in the compression mechanism 20, pressure loss as in the conventional system does not occur, and pressure loss can be reduced.

[0075] Furthermore, in the multi-cylinder rotary compressor 1 according to the first embodiment, the turbine includes a group of turbine blades made up of a plurality of blades that allow the refrigerant to flow in from the radially outer side and flow out in the axial direction, and the impeller includes a group of impeller blades made up of a plurality of blades that allow the refrigerant to flow in from the axial direction and flow out in the radially outer direction.

[0076] In the multi-cylinder rotary compressor 1 according to the first embodiment, the turbine includes a set of turbine blades, which allows a discharge valve to be disposed radially outside the turbine. Also, the impeller includes a set of impeller blades, which allows a suction chamber to be disposed radially outside the impeller.

[0077] Furthermore, in the multi-cylinder rotary compressor 1 according to the first embodiment, a blocking member wall portion is formed around the entire outer periphery of the surface of the blocking member opposite the cylinder, and the blocking member is formed with a first outlet hole 151 that communicates with the discharge flow path and penetrates from the side opposite the cylinder side toward the cylinder side, the cylinder is formed with a second outlet hole 152 that communicates with the first outlet hole 151 and penetrates from the blocking member side toward the bearing side, and the bearing is formed with a third outlet hole 153 that communicates with the second outlet hole 152 and penetrates from the cylinder side toward the surface opposite the cylinder.

[0078] According to the multi-cylinder rotary compressor 1 of embodiment 1, the refrigerant discharged from the discharge flow path can be discharged from within the wall portion of the blocking member through the first discharge hole 151, the second discharge hole 152, and the third discharge hole 153.

[0079] In addition, in the multi-cylinder rotary compressor 1 according to embodiment 1, the surface of the blocking member opposite the cylinder is provided with a recess in which a discharge valve and a turbine are disposed, and the recess has a discharge flow path formed on the bottom surface and a guide surface formed on the side surface for guiding the refrigerant discharged from the discharge flow path to the turbine.

[0080] According to the multi-cylinder rotary compressor 1 of embodiment 1, the refrigerant discharged from the discharge flow path to the outside of the compression chamber can be guided along the guide surface to the turbine, thereby allowing the turbine to rotate efficiently.

[0081] Furthermore, in the multi-cylinder rotary compressor 1 according to the first embodiment, the recessed portion has two guide surfaces, and the two guide surfaces are configured to approach each other as they approach the turbine.

[0082] According to the multi-cylinder rotary compressor 1 of embodiment 1, when the refrigerant discharged from the discharge flow path to the outside of the compression chamber is guided along the guide surface to the turbine, the density of the refrigerant guided from the discharge flow path to the turbine can be increased, and the turbine can be rotated efficiently.

[0083] Furthermore, in the multi-cylinder rotary compressor 1 according to the first embodiment, the discharge valve has a tip end that moves in a cantilevered manner and closes or opens the discharge flow path, and a base end that is fixed to the closing member, and the turbine is provided on the opposite side of the base end of the discharge valve relative to the tip end of the discharge valve.

[0084] In the multi-cylinder rotary compressor 1 according to the first embodiment, the discharge valve moves in a cantilevered manner, so that when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, the tip of the cantilevered discharge valve is lifted to open the discharge flow path, and the refrigerant discharged from the open discharge flow path is blown out toward the turbine. The pressure energy of the blown refrigerant can rotate the turbine efficiently.

[0085] In the multi-cylinder rotary compressor 1 according to the first embodiment, a discharge muffler is provided on the opposite side of the bearing from the cylinder, and the discharge muffler has a discharge hole 23Aa formed therein.

[0086] According to the multi-cylinder rotary compressor 1 of the first embodiment, the discharge muffler can reduce the discharge noise of the refrigerant discharged from the discharge flow path. Furthermore, since the refrigerant discharged from the discharge flow path is configured to collide with the impeller before colliding with the discharge muffler, the pressure energy of the refrigerant can be used to efficiently rotate the impeller.

[0087] In addition, the refrigeration cycle device 200 according to the first embodiment includes the above-mentioned multi-cylinder rotary compressor 1, a radiator in which the refrigerant compressed by the multi-cylinder rotary compressor 1 radiates heat, a pressure reducer 203 that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer 203 evaporates.

[0088] Furthermore, the refrigeration cycle device 200 according to the first embodiment uses a single refrigerant selected from the group consisting of R1234yf, R1234ze, R32, and R290, or a mixed refrigerant of two or more of these, or a mixed refrigerant of any of these with another refrigerant, or a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123.

[0089] According to the refrigeration cycle apparatus 200 of the first embodiment, the same effects as those of the multi-cylinder rotary compressor 1 described above can be obtained.

[0090] 1 Multi-cylinder rotary compressor, 2A First suction pipe, 2B Second suction pipe, 3 Suction muffler, 4 Discharge piping, 6 Refrigerating machine oil, 10 Sealed container, 11 Head, 12 Body, 13 Bottom, 15A First valve stopper, 15B Second valve stopper, 20 Compression mechanism, 21A First cylinder, 21Ab First communication chamber, 21B Second cylinder, 21Bb Second communication chamber, 22A First piston, 22B Second piston, 23A First discharge muffler, 23Aa Discharge hole, 23B Second discharge muffler, 24A Upper bearing, 24B Lower bearing, 25A First partition plate, 25Aa First closing member wall portion, 25Ab First through hole, 25B Second partition plate, 25Ba Second closing member wall portion, 25Bb Second through hole, 26A First discharge valve, 26Aa: First tip portion, 26Ab: First base end portion, 26B: Second discharge valve, 26Ba: Second tip portion, 26Bb: Second base end portion, 27A: First connecting shaft, 27B: Second connecting shaft, 28A: First turbine, 28Aa: First turbine blade set, 28B: Second turbine, 28Ba: Second turbine blade set, 29A: First impeller, 29Aa: First impeller blade set, 29B: Second impeller, 29Ba: Second impeller blade set, 30: Rotating electric machine, 31: Rotor, 32: Stator, 40: Rotating shaft, 40A: First eccentric shaft portion, 40B: Second eccentric shaft portion, 41: Lower end portion, 42: Oil supply hole, 43: First oil supply port, 44: Second oil supply port, 45: Centrifugal pump, 50A: First vane, 50B: Second vane, 51A First spring, 51B second spring, 52A first suction passage, 52B second suction passage, 53A first discharge passage, 53B second discharge passage, 54A first spring hole, 54B second spring hole, 55A first cylinder chamber, 55B second cylinder chamber, 56A first vane groove, 56B second vane groove, 57A first suction chamber, 57B second suction chamber, 58A first compression chamber, 58B second compression chamber, 124A first recess, 124Aa first bottom surface, 124Ab first guide surface, 124B second recess, 124Ba second bottom surface, 124Bb second guide surface, 151 first outlet hole, 152 second outlet hole, 153 third outlet hole, 200 refrigeration cycle device, 201 flow passage switching valve, 202 outdoor heat exchanger, 203 Pressure reducer, 204 indoor heat exchanger, T1 supercharging mechanism, T2 supercharging mechanism.

Claims

1. The outer shell consists of a sealed container and A rotating electric machine housed in the aforementioned sealed container, A rotating shaft housed in the aforementioned sealed container and rotated by the aforementioned electric rotating machine, having an eccentric shaft portion, A compression mechanism having a cylinder chamber housed within the sealed container and which compresses the refrigerant by the eccentric motion of the eccentric shaft portion, The supercharging mechanism is housed within the sealed container, The compression mechanism is A cylinder having an intake passage formed for drawing low-pressure refrigerant from outside the sealed container into the cylinder chamber, The piston fitted to the eccentric shaft portion, A vane separates the cylinder chamber, formed by the inner circumference of the cylinder and the outer circumference of the piston, into an intake chamber and a compression chamber. A bearing fixed to one side of the cylinder in the height direction and closing one side of the cylinder chamber, A blocking member is fixed to the other side of the cylinder in the height direction, closing off the other side of the cylinder chamber, and having a discharge channel formed therein for discharging compressed refrigerant to the outside of the compression chamber, The system includes a discharge valve provided on the blocking member that blocks the discharge passage and opens the discharge passage when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, The supercharging mechanism is A connecting shaft rotatably supported by the aforementioned closing member, A turbine is connected to one end of the aforementioned connecting shaft and rotates by the refrigerant discharged from the open discharge channel, The system includes an impeller connected to the other end of the connecting shaft, which rotates in conjunction with the rotation of the turbine to promote the flow of refrigerant through the intake passage, The aforementioned discharge valve A tip portion that is movable in a cantilevered manner and closes or opens the discharge passage, It comprises a base end fixed to the closing member, The aforementioned turbine, With reference to the tip of the discharge valve, it is provided on the side opposite to the base end of the discharge valve. Multi-cylinder rotary compressor.

2. A sealed container forming the outer shell, A rotating electric machine housed in the aforementioned sealed container, A rotating shaft housed in the aforementioned sealed container and rotated by the aforementioned electric rotating machine, having an eccentric shaft portion, A compression mechanism having a cylinder chamber housed within the sealed container and which compresses the refrigerant by the eccentric motion of the eccentric shaft portion, The supercharging mechanism is housed within the sealed container, The compression mechanism is A cylinder having an intake passage formed for drawing low-pressure refrigerant from outside the sealed container into the cylinder chamber, The piston fitted to the eccentric shaft portion, A vane separates the cylinder chamber, formed by the inner circumference of the cylinder and the outer circumference of the piston, into an intake chamber and a compression chamber. A bearing fixed to one side of the cylinder in the height direction and closing one side of the cylinder chamber, A blocking member is fixed to the other side of the cylinder in the height direction, closing off the other side of the cylinder chamber, and having a discharge channel formed therein for discharging compressed refrigerant to the outside of the compression chamber, The system includes a discharge valve provided on the blocking member that blocks the discharge passage and opens the discharge passage when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, The supercharging mechanism is A connecting shaft rotatably supported by the aforementioned closing member, A turbine is connected to one end of the aforementioned connecting shaft and rotates by the refrigerant discharged from the open discharge channel, The system includes an impeller connected to the other end of the connecting shaft, which rotates in conjunction with the rotation of the turbine to promote the flow of refrigerant through the intake passage, A wall portion of the closing member is formed around the entire outer circumference of the side of the closing member opposite to the cylinder. The blocking member has a first discharge hole that communicates with the discharge passage and penetrates from the opposite side of the cylinder toward the cylinder side. The cylinder has a second outlet hole that communicates with the first outlet hole and penetrates from the closing member side toward the bearing side. The bearing has a third outlet hole that communicates with the second outlet hole and penetrates from the cylinder side toward the side opposite to the cylinder. A discharge muffler is provided on the bearing opposite to the cylinder. The aforementioned discharge muffler has a discharge hole formed therein. Multi-cylinder rotary compressor.

3. A sealed container forming the outer shell, A rotating electric machine housed in the aforementioned sealed container, A rotating shaft housed in the aforementioned sealed container and rotated by the aforementioned electric rotating machine, having an eccentric shaft portion, A compression mechanism having a cylinder chamber housed within the sealed container and which compresses the refrigerant by the eccentric motion of the eccentric shaft portion, The supercharging mechanism is housed within the sealed container, The compression mechanism is A cylinder having an intake passage formed for drawing low-pressure refrigerant from outside the sealed container into the cylinder chamber, The piston fitted to the eccentric shaft portion, A vane separates the cylinder chamber, formed by the inner circumference of the cylinder and the outer circumference of the piston, into an intake chamber and a compression chamber. A bearing fixed to one side of the cylinder in the height direction and closing one side of the cylinder chamber, A blocking member is fixed to the other side of the cylinder in the height direction, closing off the other side of the cylinder chamber, and having a discharge channel formed therein for discharging compressed refrigerant to the outside of the compression chamber, The system includes a discharge valve provided on the blocking member that blocks the discharge passage and opens the discharge passage when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure, The supercharging mechanism is A connecting shaft rotatably supported by the aforementioned closing member, A turbine is connected to one end of the aforementioned connecting shaft and rotates by the refrigerant discharged from the open discharge channel, The system includes an impeller connected to the other end of the connecting shaft, which rotates in conjunction with the rotation of the turbine to promote the flow of refrigerant through the intake passage, The side of the blocking member opposite to the cylinder is provided with a recess in which the discharge valve and the turbine are arranged. The aforementioned recess is The discharge channel formed on the bottom surface, It has a guide surface formed on the side that guides the refrigerant discharged from the discharge channel to the turbine. Multi-cylinder rotary compressor.

4. The aforementioned turbine, It is equipped with a turbine blade group consisting of multiple blades that allow refrigerant to flow in from the radially outer side and to flow out in the axial direction, The impeller is, It is equipped with an impeller blade group consisting of multiple blades that allow refrigerant to flow in from the axial direction and discharge outwards in the radial direction. A multi-cylinder rotary compressor according to claim 1.

5. A wall portion of the closing member is formed around the entire outer circumference of the side of the closing member opposite to the cylinder. The blocking member has a first discharge hole that communicates with the discharge passage and penetrates from the opposite side of the cylinder toward the cylinder side. The cylinder has a second outlet hole that communicates with the first outlet hole and penetrates from the closing member side toward the bearing side. The bearing has a third outlet hole that communicates with the second outlet hole and penetrates from the cylinder side toward the side opposite to the cylinder. The multi-cylinder rotary compressor according to claim 4.

6. The recess has two guide surfaces, The two guide surfaces are configured to move closer to each other as they approach the turbine. A multi-cylinder rotary compressor according to claim 3.

7. A multi-cylinder rotary compressor according to claim 1, A heat exchanger from which the refrigerant compressed by the aforementioned multi-cylinder rotary compressor dissipates heat, A pressure reducer for reducing the pressure of the refrigerant that has flowed out from the heat sink, The system comprises an evaporator from which the refrigerant discharged from the pressure reducer evaporates. Refrigeration cycle device.

8. A single refrigerant of R1234yf, R1234ze, R32, or R290, or a mixture of two or more of these, or a mixture of one of these with another refrigerant, or a mixture containing R1132(E), or a mixture containing R1123 is used. The refrigeration cycle apparatus according to claim 7.