Rotary compressor and refrigeration cycle device

Abstract

A rotary compressor includes: a sealed container forming the outer shell; a rotary motor housed within the sealed container; a rotating shaft housed within the sealed container and rotated by the rotary motor, having an eccentric shaft portion; a compression mechanism housed within the sealed container and having a cylinder chamber for compressing refrigerant via the eccentric movement of the eccentric shaft portion; and a booster mechanism housed within the sealed container. The compression mechanism includes: a cylinder body forming an intake flow path for drawing low-pressure refrigerant from the outside of the sealed container into the cylinder chamber; a piston fitted into the eccentric shaft portion; vanes dividing the cylinder chamber formed by the inner circumference of the cylinder body and the outer circumference of the piston into an intake chamber and a compression chamber; and a bearing fixed to one side of the cylinder body in the height direction and enclosed. The cylinder chamber has a discharge passage formed on one side, through which the compressed refrigerant is discharged to the outside of the compressor chamber; a sealing member is fixed to the other side in the height direction of the cylinder body and seals the other side of the cylinder chamber; and a discharge valve is provided on the bearing and seals 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 pressurizing mechanism includes: a connecting shaft rotatably supported on the bearing; a turbine connected to one end of the connecting shaft and rotating through 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 refrigerant flowing in the suction passage.

Description

Technical Field

[0001] This disclosure relates to rotary compressors and refrigeration cycle devices. Background Technology

[0002] Conventionally, there exists a turbocharger with a supercharging mechanism (for example, see Patent Document 1). The turbocharger in Patent Document 1 includes a housing, a motor, a rotor, rotating blades, a supercharger, a shaft, and an exhaust pipe. The housing includes: a main housing, in which the motor, rotating blades, supercharger, and shaft are disposed; and a sub-housing, in which the rotor is disposed. The main housing and the sub-housing are fixed to each other, and a partition wall is provided within the main housing. By providing the partition wall within the main housing, a motor chamber and a receiving chamber are formed within the main housing. The shaft is rotatably supported by the partition wall, with rotating blades housed in the receiving chamber fixed to one end of the shaft, and a supercharger housed in the motor chamber fixed to the other end of the shaft. Furthermore, the motor is housed in the motor chamber, and the rotor is housed in the sub-housing. An exhaust port provided in the sub-housing is connected to a communication hole configured to communicate with the receiving chamber of the main housing via an exhaust pipe. The main housing has: an exhaust hole communicating with the receiving chamber and discharging compressed gas, and an intake hole communicating with the motor chamber and drawing in intake gas from outside the main housing.

[0003] In this turbocharger configuration, the rotor rotates due to the rotation of the motor. Gas compressed by the rotor within the secondary housing flows from the secondary housing's outlet through the exhaust pipe and via a connecting hole into the main housing's receiving chamber. The gas flowing into the main housing's receiving chamber via the connecting hole drives the rotating blades to rotate, and this gas is discharged from the main housing's outlet. Conversely, intake gas flows in from the intake port, is pressurized by the turbocharger rotating along with the rotating blades, becomes highly dense, and is drawn into the secondary housing.

[0004] Patent Document 1: Japanese Patent Application Publication No. 51-3445

[0005] However, the turbocharger in Patent Document 1 is configured such that gas compressed by the rotor within the secondary housing is introduced into the housing chamber of the main housing via an exhaust pipe located outside the main housing and blown onto the rotating blades. Therefore, the following problem exists: the gas compressed by the rotor experiences pressure loss as it passes through the exhaust pipe, preventing the rotating blades from rotating efficiently. Summary of the Invention

[0006] This disclosure was made to solve the aforementioned problems, and its object is to provide a rotary compressor and refrigeration cycle device that can reduce pressure loss by providing a booster mechanism driven by refrigerant discharged from the compressor mechanism in the compression mechanism.

[0007] The rotary compressor disclosed herein comprises: a sealed container forming a housing; a rotary motor housed within the sealed container; a rotating shaft housed within the sealed container and rotated by the rotary motor, and having an eccentric shaft portion; a compression mechanism housed within the sealed container and having a cylinder chamber for compressing refrigerant via the eccentric movement of the eccentric shaft portion; and a booster mechanism housed within the sealed container. The compression mechanism comprises: a cylinder body forming an intake passage for drawing low-pressure refrigerant from the outside of the sealed container into the cylinder chamber; a piston fitted with the eccentric shaft portion; a vane dividing the cylinder chamber formed by the inner circumference of the cylinder body and the outer circumference of the piston into an intake chamber and a compression chamber; and a bearing fixed to one side of the cylinder body in the height direction. The pressurizing mechanism includes: a connecting shaft rotatably supported on the bearing; a turbine connected to one end of the connecting shaft and rotating by the refrigerant discharged from the open discharge path; and an impeller connected to the other end of the connecting shaft and rotating with the turbine to promote the flow of refrigerant flowing in the suction path. The turbine is provided with a discharge passage for discharging compressed refrigerant to the outside of the compression chamber; a sealing component fixed to the other side of the cylinder body in the height direction and sealing the other side of the cylinder chamber; and a discharge valve disposed on the bearing and sealing the discharge passage, which opens when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure.

[0008] In addition, the refrigeration cycle apparatus disclosed herein includes: the rotary compressor described above; a radiator for dissipating heat from the refrigerant compressed by the rotary compressor; a pressure reducer for reducing the pressure of the refrigerant flowing out of the radiator; and an evaporator for evaporating the refrigerant flowing out of the pressure reducer.

[0009] According to the rotary compressor and refrigeration cycle apparatus disclosed herein, the booster mechanism comprises: a connecting shaft rotatably supported on a bearing; a turbine connected to one end of the connecting shaft and rotating via refrigerant discharged from an open discharge passage; and an impeller connected to the other end of the connecting shaft and rotating with the turbine to promote the flow of refrigerant flowing in the suction passage. In other words, since the booster mechanism, driven by refrigerant discharged from the compression mechanism, is located within the compression mechanism, pressure loss as in the past is not generated, thus reducing pressure loss. Attached Figure Description

[0010] Figure 1 This is a longitudinal sectional view showing the overall structure of the rotary compressor involved in Embodiment 1.

[0011] Figure 2This is a cross-sectional view of the first cylinder of the compression mechanism of the rotary compressor according to Embodiment 1.

[0012] Figure 3 This is a cross-sectional view of the second cylinder of the compression mechanism of the rotary compressor according to Embodiment 1.

[0013] Figure 4 This is a schematic diagram illustrating a refrigeration cycle apparatus equipped with the rotary compressor described in Embodiment 1.

[0014] Figure 5 This is a top perspective view showing the upper bearing, first cylinder, and first turbine of the rotary compressor according to Embodiment 1.

[0015] Figure 6 This is a longitudinal sectional view showing the upper bearing, first cylinder, and first turbine of the rotary compressor according to Embodiment 1.

[0016] Figure 7 This is a top view showing the upper bearing, first cylinder, and first turbine of the rotary compressor according to Embodiment 1.

[0017] Figure 8 This is a top perspective view of the upper bearing of the rotary compressor according to Embodiment 1.

[0018] Figure 9 This is a bottom view showing the upper bearing of the rotary compressor according to Embodiment 1.

[0019] Figure 10 This is a bottom perspective view showing the lower bearing, second cylinder, and second turbine of the rotary compressor according to Embodiment 1.

[0020] Figure 11 This is a longitudinal sectional view showing the lower bearing, second cylinder, and second turbine of the rotary compressor according to Embodiment 1.

[0021] Figure 12 This is a bottom view showing the lower bearing, second cylinder, and second turbine of the rotary compressor according to Embodiment 1.

[0022] Figure 13 This is a bottom perspective view of the lower bearing of the rotary compressor according to Embodiment 1.

[0023] Figure 14 This is a top view showing the lower bearing of the rotary compressor according to Embodiment 1.

[0024] Figure 15 This is a longitudinal sectional view of the first cylinder of the rotary compressor according to Embodiment 1.

[0025] Figure 16 This is a top view of the first cylinder of the rotary compressor according to Embodiment 1.

[0026] Figure 17 This is a bottom view showing the first cylinder of the rotary compressor according to Embodiment 1.

[0027] Figure 18 This is a top view showing the first cylinder and the first impeller of the rotary compressor according to Embodiment 1.

[0028] Figure 19 This is a longitudinal sectional view of the second cylinder of the rotary compressor according to Embodiment 1.

[0029] Figure 20 This is a bottom view showing the second cylinder of the rotary compressor according to Embodiment 1.

[0030] Figure 21 This is a top view showing the second cylinder of the rotary compressor according to Embodiment 1.

[0031] Figure 22 This is a bottom view showing the second cylinder and second impeller of the rotary compressor according to Embodiment 1.

[0032] Figure 23 This is a longitudinal sectional view showing the compression mechanism of the rotary compressor according to Embodiment 1.

[0033] Figure 24 This is a side view of the booster mechanism of the rotary compressor according to Embodiment 1.

[0034] Figure 25 This is a single impeller diagram of the rotary compressor involved in Embodiment 1.

[0035] Figure 26 This is a diagram of the turbine unit of the rotary compressor involved in Embodiment 1.

[0036] Figure 27 This is a single-unit diagram of the connecting shaft of the rotary compressor according to Embodiment 1.

[0037] Figure 28 yes Figure 18 A view of section AA.

[0038] Figure 29 yes Figure 22 A view of the BB section.

[0039] Figure 30 This is a longitudinal sectional view showing the overall structure of the single-rotary rotary compressor according to Embodiment 2. Detailed Implementation

[0040] Hereinafter, embodiments of the present disclosure will be described based on the accompanying drawings. However, the present disclosure is not limited to the embodiments described below. Additionally, the size relationships of the constituent components in the following drawings may differ from actual dimensions.

[0041] Implementation Method 1

[0042] Figure 1 This is a longitudinal sectional view showing the overall structure of the rotary compressor 1 according to Embodiment 1. Figure 2 This is a cross-sectional view of the first cylinder 21A of the compression mechanism 20 of the rotary compressor 1 according to Embodiment 1. Figure 3 This is a cross-sectional view of the second cylinder 21B of the compression mechanism 20 of the rotary compressor 1 according to Embodiment 1.

[0043] [Structure of rotary compressor 1]

[0044] The rotary compressor 1 according to embodiment 1 uses a... Figure 1 A dual-cylinder rotary compressor, as shown, consists of two cylinders (first cylinder 21A and second cylinder 21B). The overall structure of the rotary compressor 1, which is a dual-cylinder rotary compressor, will be described below. The rotary compressor 1 includes a sealed container 10, a first suction pipe 2A, a second suction pipe 2B, a suction silencer 3, a compression mechanism 20, a rotary motor 30, a rotating shaft 40, and a discharge pipe 4. The sealed container 10 forms the outer casing of the rotary compressor 1. The first suction pipe 2A and the second suction pipe 2B supply refrigerant to the sealed container 10. The suction silencer 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 rotary motor 30 includes a rotor 31 and a stator 32. The rotating shaft 40 is connected to the rotor 31 of the rotary motor 30 and rotates with the rotor 31. The discharge pipe 4 discharges the refrigerant compressed by the compression mechanism 20 out of the sealed container 10. The structure of the rotary compressor 1 will be described in detail below.

[0045] (10 sealed containers)

[0046] The sealed container 10, which constitutes the outer shell of the rotary compressor 1, houses a compression mechanism 20, a rotary motor 30, and a rotating shaft 40. The sealed container 10 has a head 11, a bottom 13, and a main body 12. The head 11 forms the upper outer shell of the rotary compressor 1. The bottom 13 forms the lower outer shell of the rotary compressor 1. The main body 12 forms the middle outer shell of the rotary compressor 1, with the head 11 mounted on its upper part and the bottom 13 mounted on its lower part.

[0047] like Figure 1 As shown, the head 11, which forms the upper part of the sealed container 10, has a generally bowl-shaped shape, for example. A discharge pipe 4, which communicates the inside and outside of the sealed container 10, is connected to the head 11.

[0048] like Figure 1 As shown, the main body 12, which constitutes the middle portion of the sealed container 10, has a generally cylindrical shape, for example. A first suction pipe 2A and a second suction pipe 2B for supplying refrigerant into the sealed container 10 are connected to the main body 12. Furthermore, a stator 32 of a rotary motor 30 is mounted on the inner circumferential surface of the main body 12. Additionally, a compression mechanism 20 is mounted on the inner circumferential surface of the main body 12. In Embodiment 1, a rolling piston type compression mechanism is used as the compression mechanism 20. In this case, the compression mechanism 20 is mostly mounted on the inner circumferential surface of the main body 12 and below the mounting position of the stator 32.

[0049] like Figure 1 As shown, the bottom 13, which forms the lower part of the sealed container 10, has a roughly bowl-shaped structure. Refrigeration oil 6, which serves as a lubricant, is stored in the bottom 13. That is, refrigeration oil 6 is stored inside the sealed container 10. Furthermore, this refrigeration oil 6 is supplied to the compression mechanism 20 and the like to reduce friction in sliding parts of the compression mechanism 20 and the like.

[0050] (First inhalation tube 2A and second inhalation tube 2B)

[0051] As described above, the first suction pipe 2A and the second suction pipe 2B are connected to the main body 12 of the sealed container 10. One end of the first suction pipe 2A is connected to the first suction flow path 52A of the first cylinder 21A of the compression mechanism 20 (see reference 1). Figure 2 The first suction pipe 2A is connected to the second suction flow path 52B of the second cylinder 21B of the compression mechanism 20 (described later). Additionally, the other end of the first suction pipe 2A is connected to the suction muffler 3. One end of the second suction pipe 2B is connected to the second suction flow path 52B of the second cylinder 21B of the compression mechanism 20 (see reference). Figure 3 The second intake pipe 2B is connected to the intake muffler 3. Furthermore, hereinafter, the general term for names beginning with "first" or "second" will sometimes be referred to as the term without "first" or "second". For example, "first cylinder 21A" and "second cylinder 21B" will be collectively referred to as "cylinder".

[0052] (Inhalation silencer 3)

[0053] The intake muffler 3 functions as a muffler to reduce refrigerant noise and other sounds generated when refrigerant flows into the rotary compressor 1. Additionally, the intake muffler 3 also functions as a liquid receiver capable of storing liquid refrigerant. As described above, the intake muffler 3 is connected to the first intake flow path 52A of the first cylinder 21A and the second intake flow path 52B of the second cylinder 21B via the first intake pipe 2A and the second intake pipe 2B.

[0054] (Compression mechanism 20)

[0055] The compression mechanism 20 is connected to the rotating shaft 40 and uses the power of the rotary motor 30 transmitted by the rotating shaft 40 to compress the refrigerant drawn in from the outside. In Embodiment 1, the refrigerant flowing into the intake silencer 3 is supplied to the compression mechanism 20 via the first intake pipe 2A and the second intake pipe 2B. That is, the compression mechanism 20 draws in the external refrigerant via the first intake pipe 2A and the second intake pipe 2B and compresses the refrigerant. The refrigerant compressed by the compression mechanism 20 is released into the interior of the sealed container 10. As described above, in Embodiment 1, a rolling piston type compression mechanism is used as the compression mechanism 20.

[0056] like Figures 1-3 As shown, the rotating shaft 40 according to Embodiment 1 includes a first eccentric shaft portion 40A and a second eccentric shaft portion 40B. The compression mechanism 20 includes a first cylinder 21A, a first piston 22A, a first slide 50A, a first spring 51A, an upper bearing 24A, a second cylinder 21B, a second piston 22B, a second slide 50B, a second spring 51B, a lower bearing 24B, and a partition plate 25. Hereinafter, the upper bearing 24A, the lower bearing 24B, and the partition plate 25 are also referred to as bearings or sealing components.

[0057] The first cylinder body 21A is cylindrical, with a first cylinder chamber 55A formed in the center. The first cylinder body 21A has a first suction flow path 52A for drawing refrigerant from the first suction pipe 2A, and a first discharge flow path 53A for discharging refrigerant through the internal space of the sealed container 10 to the discharge pipe 4. The first suction pipe 2A is pressed into the first suction flow path 52A on the outer circumference of the first cylinder body 21A. The first piston 22A is fitted into the first eccentric shaft portion 40A of the rotating shaft 40, and rotates eccentrically together with the first eccentric shaft portion 40A to compress the refrigerant.

[0058] The first vane 50A is located between the first intake flow path 52A and the first discharge flow path 53A, and is disposed in the first vane groove 56A formed in a radially extending manner along the first cylinder body 21A, dividing 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 flow path 52A, and the first compression chamber 58A communicates with the first discharge flow path 53A.

[0059] A first spring hole 54A is formed radially at the outer end of the first vane groove 56A in the first cylinder body 21A, and axially extends through the first cylinder body 21A and communicates with the first vane groove 56A. A first spring 51A is received in the first spring hole 54A, pressing the first vane 50A, which is mounted at the end of the first spring 51A, against the outer peripheral surface of the first piston 22A. An upper bearing 24A is configured to abut against the upper end face of the first cylinder body 21A and seal the first cylinder chamber 55A. The upper bearing 24A supports the rotating shaft 40 so that it can rotate.

[0060] The second cylinder 21B is cylindrical and positioned below the first cylinder 21A, with a second cylinder chamber 55B formed in its central portion. The second cylinder 21B has a second suction flow path 52B for drawing refrigerant from the second suction pipe 2B, and a second discharge flow path 53B for discharging refrigerant through the internal space of the sealed container 10 to the discharge pipe 4. The second suction pipe 2B is pressed into the second suction flow path 52B on the outer circumference of the second cylinder 21B. The second piston 22B is fitted into the second eccentric shaft portion 40B of the rotating shaft 40, and rotates eccentrically together with the second eccentric shaft portion 40B to compress the refrigerant.

[0061] The second vane 50B is located between the second intake flow path 52B and the second discharge flow path 53B, and is disposed in the second vane groove 56B formed in a radially extending manner along the second cylinder body 21B, dividing 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 flow path 52B, and the second compression chamber 58B communicates with the second discharge flow path 53B.

[0062] The second spring hole 54B is formed radially at the outer end of the second vane groove 56B of the second cylinder body 21B, and axially extends through the second cylinder body 21B and communicates with the second vane groove 56B. The second spring 51B is received in the second spring hole 54B, pressing the second vane 50B, which is mounted at the end of the second spring 51B, against the outer peripheral surface of the second piston 22B. The lower bearing 24B is configured to abut against the lower end face of the second cylinder body 21B, sealing the second cylinder chamber 55B. The lower bearing 24B supports the rotating shaft 40 so that it can rotate.

[0063] The partition plate 25 is configured to abut against the lower end face of the first cylinder 21A and to abut against the upper end face of the second cylinder 21B, thereby sealing the first cylinder chamber 55A and the second cylinder chamber 55B.

[0064] The first piston 22A is slidably rotatable within the first cylinder 21A. This first piston 22A is configured to rotate eccentrically within the first cylinder 21A relative to the rotation center of the rotation axis 40. Hereinafter, this eccentric rotational motion relative to the rotation center of the rotation axis 40 will be referred to as eccentric rotational motion. Furthermore, the second piston 22B is slidably rotatable within the second cylinder 21B. This second piston 22B is configured to rotate eccentrically within the second cylinder 21B.

[0065] Furthermore, the first piston 22A is connected to the rotating shaft 40 in a manner that allows it to rotate within the first cylinder 21A with a rotational phase offset of 180 degrees relative to the second piston 22B when rotating within the second cylinder 21B. In other words, the second piston 22B is connected to the rotating shaft 40 in a manner that allows it to rotate within the second cylinder 21B with a rotational phase offset of -180 degrees relative to the first piston 22A when rotating within the first cylinder 21A.

[0066] Furthermore, a first discharge valve 26A (described later) is provided on the upper bearing 24A to discharge the refrigerant compressed by the first cylinder 21A and the first piston 22A. Figure 6 By opening the first discharge valve 26A, the first discharge flow path 53A can be connected to the first discharge muffler 23A described later. Additionally, a second discharge valve 26B (described later) is provided in the lower bearing 24B to discharge the refrigerant compressed by the second cylinder 21B and the second piston 22B. Figure 11 By opening the second discharge valve 26B, the second discharge flow path 53B can be connected to the second discharge silencer 23B, which will be described later.

[0067] (Rotary motor 30 and rotating shaft 40)

[0068] like Figure 1 As shown, the rotary motor 30 has a rotor 31 that transmits its own rotation to the rotating shaft 40, and a stator 32 formed by mounting multiphase windings on a laminated iron core.

[0069] The rotating shaft 40 is connected to the rotary motor 30 and rotates under the power of the rotary motor 30. Furthermore, the rotating shaft 40 transmits the power of the rotary motor 30 to the compression mechanism 20. In Embodiment 1, the upper end of the rotating shaft 40 is connected to the rotor 31 of the rotary motor 30. Therefore, the rotating shaft 40 rotates along with the rotor 31. Furthermore, Figure 1The rotating shaft 40 shown rotates around an axis extending vertically along the plane of the paper. The lower end of the rotating shaft 40 is connected to the compression mechanism 20. More specifically, the lower end of the rotating shaft 40 is rotatably supported by the upper bearing 24A and the lower bearing 24B of the compression mechanism 20. Furthermore, a first eccentric shaft portion 40A and a second eccentric shaft portion 40B are provided between the portion of the rotating shaft 40 rotatably supported by the upper bearing 24A and the portion rotatably supported by the lower bearing 24B. The rotating shaft 40 is connected in such a way that a first piston 22A fitted into the first eccentric shaft portion 40A and a second piston 22B fitted into the second eccentric shaft portion 40B can perform eccentric rotational movement. Thus, as the rotor 31 rotates, the rotating shaft 40 also rotates, and the first piston 22A and the second piston 22B perform eccentric rotational movement. Therefore, the refrigerant is compressed by the first cylinder 21A and the first piston 22A, and by the second cylinder 21B and the second piston 22B. That is, the compression mechanism 20 uses the power of the rotary motor 30 transmitted by the rotary shaft 40 to compress the refrigerant drawn in from the outside.

[0070] (Drain pipe 4)

[0071] Discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. That is, discharge pipe 4 is a pipe that discharges the high-temperature and high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10.

[0072] (Centrifugal pump 45)

[0073] An oil supply hole 42 is formed on the rotating shaft 40, opening at its lower end 41. The oil supply hole 42 extends along the rotation center of the rotating shaft 40. Additionally, a first oil supply port 43 and a second oil supply port 44 are formed on the rotating shaft 40. The first oil supply port 43 and the second oil supply port 44 form flow paths for supplying refrigerant oil 6 drawn into the oil supply hole 42 to the sliding portion of the compression mechanism 20. One end of the first oil supply port 43 and the second oil supply port 44 communicates with the oil supply hole 42. Furthermore, the other end of the first oil supply port 43 and the second oil supply port 44 opens at a location on the outer circumferential surface of the rotating shaft 40 opposite to the compression mechanism 20. Moreover, in Embodiment 1, the other end of the first oil supply port 43 opens at a location opposite to the upper bearing 24A of the compression mechanism 20. Furthermore, the other end of the second oil supply port 44 opens at a location opposite to the lower bearing 24B of the compression mechanism 20.

[0074] A centrifugal pump 45 is installed inside the oil supply port 42 of the rotating shaft 40. The centrifugal pump 45 is formed by twisting a plate-shaped component. The centrifugal pump 45 is a fluid machine that uses the centrifugal force generated by the rotational motion of the rotating shaft 40 to draw up the refrigerant oil 6 stored at the bottom 13 of the sealed container 10 as lubricating oil. The refrigerant oil 6 drawn up by the centrifugal pump 45 to the oil supply port 42 is supplied to the sliding part of the compression mechanism 20. Specifically, a portion of the refrigerant oil 6 drawn up to the oil supply port 42 is supplied through the first oil supply port 43 to the sliding part between the upper bearing 24A of the compression mechanism 20 and the rotating shaft 40. In addition, a portion of the refrigerant oil 6 drawn up to the oil supply port 42 is supplied through the second oil supply port 44 to the sliding part between the lower bearing 24B of the compression mechanism 20 and the rotating shaft 40. As the refrigerant oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, and polyol ester-based lubricants can be used.

[0075] [Operation of the rotary motor 30]

[0076] A current is supplied to the windings of the laminated iron core disposed on the stator 32 by a power source not shown in the figure, causing the stator 32 to generate a rotating magnetic field. This rotating magnetic field of the stator 32 then acts on the permanent magnet disposed on the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted via the rotating shaft 40 to the first piston 22A and the second piston 22B, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.

[0077] [Refrigerant flow]

[0078] Refrigerant is introduced into the rotary compressor 1 through the eccentric rotation of the first piston 22A and the second piston 22B. Specifically, low-pressure refrigerant outside the rotary compressor 1 flows into the suction muffler 3 through the eccentric rotation of the first piston 22A and the second piston 22B. Furthermore, the low-pressure gaseous refrigerant flowing into the suction muffler 3 flows into the compression mechanism 20 of the rotary compressor 1 via the first suction pipe 2A and the second suction pipe 2B. A portion of the gaseous refrigerant flowing into the compression mechanism 20 is compressed by the first cylinder 21A and the first piston 22A, becoming a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant flows into the first discharge muffler 23A via the first discharge valve 26A of the upper bearing 24A. The high-temperature and high-pressure gaseous refrigerant flowing into the first discharge muffler 23A exits from the discharge port 23Aa (described later) provided in the first discharge muffler 23A. Figure 23 The high-temperature and high-pressure gaseous refrigerant released into the sealed container 10 is then moved to the upper part of the sealed container 10 through gaps in the rotary motor 30 and other parts, and discharged from the discharge pipe 4.

[0079] The remaining portion of the gaseous refrigerant flowing into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B into a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant flows into the second discharge muffler 23B via the second discharge valve 26B of the lower bearing 24B. The high-temperature and high-pressure gaseous refrigerant flowing into the second discharge muffler 23B passes through the inter-muffler refrigerant flow path 59 (described later) from the second discharge muffler 23B. Figure 23 The high-temperature and high-pressure gaseous refrigerant is then fed into the first discharge muffler 23A. The refrigerant, which is then fed into the first discharge muffler 23A, exits through the discharge port 23Aa (described later) located in the first discharge muffler 23A. Figure 23 The high-temperature and high-pressure gaseous refrigerant released into the sealed container 10 then moves to the upper part of the space inside the sealed container 10 through gaps in the rotary motor 30 and other parts, and is discharged from the discharge pipe 4.

[0080] Additionally, the refrigerant oil 6 stored in the bottom 13 of the sealed container 10 is drawn up from the lower end 41 of the oil supply port 42 by a centrifugal pump 45 that rotates together with the rotating shaft 40. The refrigerant oil 6 drawn up from the lower end 41 of the oil supply port 42 flows as lubricant from the first oil supply port 43 between the upper bearing 24A and the rotating shaft 40. Furthermore, the aforementioned refrigerant oil 6 flows as lubricant from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40. By allowing the refrigerant oil 6 to flow between them, the rotating shaft 40 can smoothly transmit rotational driving force to the first piston 22A and the second piston 22B.

[0081] Additionally, a portion of the refrigerant oil 6 flowing from the first oil inlet 43 between the upper bearing 24A and the rotating shaft 40 flows into the space between the upper bearing 24A and the upper surface of the first piston 22A. Similarly, a portion of the refrigerant oil 6 flowing from the second oil inlet 44 between the lower bearing 24B and the rotating shaft 40 flows into the space between the lower bearing 24B and the lower surface of the second piston 22B. Furthermore, the refrigerant oil 6 is used to ensure smooth rotation of the first piston 22A and the second piston 22B, but a portion of the refrigerant oil 6 is compressed along with the low-pressure gaseous refrigerant and discharged as a component of the high-temperature, high-pressure gaseous refrigerant.

[0082] [Structure and operation of refrigeration cycle unit 200]

[0083] Figure 4 This is a schematic diagram illustrating a refrigeration cycle apparatus 200 equipped with the rotary compressor 1 according to Embodiment 1. Next, using... Figure 4 A refrigeration cycle unit 200 equipped with a rotary compressor 1 will be described. The refrigeration cycle unit 200 is used in various applications such as air conditioning units, hot water supply units, and refrigeration units. Figure 4The image shows an example of a refrigeration cycle unit 200 being used as an air conditioning unit. Therefore, Figure 4 The refrigeration cycle unit 200 shown 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. Additionally, Figure 4 The refrigeration cycle device 200 shown can also perform refrigeration operation. Therefore, the refrigeration cycle device 200 is equipped with a flow path switching valve 201. The refrigeration cycle device 200 includes: a rotary compressor 1, and an intake silencer 3 connected to the intake side of the rotary compressor 1; a flow path switching valve 201 connected to the discharge side of the 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 for refrigerant circulation.

[0084] Examples of refrigerants circulating in the refrigerant circuit include fluorinated or hydrocarbon refrigerants with low Global Warming Potential (GWP). Other examples of such refrigerants include any single refrigerant from R1234yf, R1234ze, R32, and R290, or a mixture of two or more of these refrigerants, or a mixture of one of these refrigerants with another refrigerant. Additionally, examples of such refrigerants include mixtures containing R1132(E) or mixtures containing R1123. In addition, examples of the aforementioned refrigerants include mixed refrigerants such as R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, R459A, and R410A.

[0085] The flow path switching valve 201 is, for example, a four-way valve, which switches between cooling and heating operation by changing the direction of refrigerant flow. Alternatively, a combination of two-way and three-way valves can be used instead of the four-way valve as the flow path switching valve 201. The pressure regulator 203 reduces the pressure of the refrigerant, causing it to expand. The pressure regulator 203 is, for example, an electronic expansion valve capable of adjusting the opening of a throttle valve. By adjusting the opening, it controls the refrigerant pressure flowing into the indoor heat exchanger 204 during cooling operation and controls the refrigerant pressure flowing into the outdoor heat exchanger 202 during heating operation. The outdoor heat exchanger 202 functions as an evaporator or radiator, exchanging heat between the air and the refrigerant, causing the refrigerant to evaporate or condense. 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 either an evaporator or a radiator, facilitating heat exchange between the air and the refrigerant, causing the refrigerant to evaporate or condense. During heating operation, the indoor heat exchanger 204 functions as a radiator; during cooling operation, it functions as an evaporator.

[0086] When the refrigeration cycle unit 200 is used as an air conditioning unit, for example, an indoor heat exchanger 204 is installed indoors. Alternatively, for example, a flow path switching valve 201, an outdoor heat exchanger 202, and a pressure reducer 203 are installed outdoors.

[0087] Next, the operation of the refrigeration cycle unit 200 during heating and cooling operations will be explained. When the refrigeration cycle unit 200 is in heating operation, the flow path switching valve 201 switches to... Figure 4 The solid line indicates the flow path. Thus, the discharge pipe 4 of the rotary compressor 1 is connected to the indoor heat exchanger 204, and the suction muffler 3 of the 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 the high-temperature and high-pressure gaseous refrigerant compressed by the rotary compressor 1 is discharged from the rotary compressor 1, this high-temperature and high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature and high-pressure gaseous refrigerant flowing into the indoor heat exchanger 204 condenses while dissipating heat to the indoor air, becoming a high-pressure liquid refrigerant and flowing out of the indoor heat exchanger 204. At this time, the indoor air is heated. Furthermore, depending on the type of refrigerant, there are also refrigerants that do not condense when dissipating heat, such as carbon dioxide refrigerant. When using refrigerants that condense when dissipating heat, the radiator is sometimes also called a condenser.

[0088] High-pressure liquid refrigerant flowing from indoor heat exchanger 204 flows into pressure reducer 203. Then, the high-pressure liquid refrigerant flowing into pressure reducer 203 is depressurized, becoming a low-temperature, low-pressure gas-liquid two-phase refrigerant, and flows out of pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing out of pressure reducer 203 flows into outdoor heat exchanger 202. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing into outdoor heat exchanger 202 absorbs heat from outdoor air and evaporates, flowing out of outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant. The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out of outdoor heat exchanger 202 is drawn into suction silencer 3 of rotary compressor 1. Then, the low-pressure gaseous refrigerant drawn into suction silencer 3 of rotary compressor 1 is compressed by compression mechanism 20 of rotary compressor 1, becoming a high-temperature, high-pressure gaseous refrigerant. The high-temperature and high-pressure gaseous refrigerant is discharged again from the rotary compressor 1. That is, when the refrigeration cycle unit 200 is in heating operation, the refrigerant... Figure 4 The solid arrows indicate a loop.

[0089] When the refrigeration cycle unit 200 is in refrigeration operation, the flow path switching valve 201 switches to... Figure 4 The flow path is shown by the dashed line. Thus, the discharge pipe 4 of the rotary compressor 1 is connected to the outdoor heat exchanger 202, and the suction silencer 3 of the 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 the high-temperature and high-pressure gaseous refrigerant compressed by the rotary compressor 1 is discharged from the rotary compressor 1, this high-temperature and high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature and high-pressure gaseous refrigerant flowing into the outdoor heat exchanger 202 condenses while dissipating heat to the outdoor air, becoming a high-pressure liquid refrigerant that flows out from the outdoor heat exchanger 202.

[0090] High-pressure liquid refrigerant flowing from outdoor heat exchanger 202 flows into pressure reducer 203. Then, the high-pressure liquid refrigerant flowing into pressure reducer 203 is depressurized, becoming a low-temperature, low-pressure gas-liquid two-phase refrigerant, and flows out of pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing out of pressure reducer 203 flows into indoor heat exchanger 204. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing into indoor heat exchanger 204 absorbs heat from the indoor air and evaporates, flowing out of indoor heat exchanger 204 as a low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant. At this time, the indoor air is cooled. The low-pressure gaseous refrigerant or gas-liquid two-phase refrigerant flowing out of indoor heat exchanger 204 is drawn into the suction silencer 3 of rotary compressor 1. Then, the low-pressure gaseous refrigerant drawn into the suction silencer 3 of the rotary compressor 1 is compressed by the compression mechanism 20 of the rotary compressor 1, becoming a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant is then discharged from the rotary compressor 1 again. That is, when the refrigeration cycle device 200 is operating in refrigeration mode, the refrigerant... Figure 4 The loop is as shown by the dashed arrow.

[0091] Figure 5 This is a top perspective view showing the upper bearing 24A, the first cylinder 21A, and the first turbine 28A of the rotary compressor 1 according to Embodiment 1. Figure 6 This is a longitudinal sectional view showing the upper bearing 24A, the first cylinder 21A, and the first turbine 28A of the rotary compressor 1 according to Embodiment 1. Figure 7 This is a top view showing the upper bearing 24A, the first cylinder 21A, and the first turbine 28A of the rotary compressor 1 according to Embodiment 1. Figure 8 This is a top perspective view showing the upper bearing 24A of the rotary compressor 1 according to Embodiment 1. Figure 9 This is a bottom view showing the upper bearing 24A of the rotary compressor 1 according to Embodiment 1. Figure 10 This is a bottom perspective view showing the lower bearing 24B, the second cylinder 21B, and the second turbine 28B of the rotary compressor 1 according to Embodiment 1. Figure 11 This is a longitudinal sectional view showing the lower bearing 24B, the second cylinder 21B, and the second turbine 28B of the rotary compressor 1 according to Embodiment 1. Figure 12 This is a bottom view showing the lower bearing 24B, the second cylinder 21B, and the second turbine 28B of the rotary compressor 1 according to Embodiment 1. Figure 13 This is a bottom perspective view showing the lower bearing 24B of the rotary compressor 1 according to Embodiment 1. Figure 14 This is a top view showing the lower bearing 24B of the rotary compressor 1 according to Embodiment 1. Figure 15This is a longitudinal sectional view of the first cylinder 21A of the rotary compressor 1 according to Embodiment 1. Figure 16 This is a top view showing the first cylinder 21A of the rotary compressor 1 according to Embodiment 1. Figure 17 This is a bottom view showing the first cylinder 21A of the rotary compressor 1 according to Embodiment 1. Figure 18 This is a top view showing the first cylinder 21A and the first impeller 29A of the rotary compressor 1 according to Embodiment 1. Figure 19 This is a longitudinal sectional view showing the second cylinder 21B of the rotary compressor 1 according to Embodiment 1. Figure 20 This is a bottom view showing the second cylinder 21B of the rotary compressor 1 according to Embodiment 1. Figure 21 This is a top view showing the second cylinder 21B of the rotary compressor 1 according to Embodiment 1. Figure 22 This is a bottom view showing the second cylinder 21B and the second impeller 29B of the rotary compressor 1 according to Embodiment 1. Furthermore, Figure 11 Represented upside down.

[0092] (Boosting mechanisms T1, T2)

[0093] Next, the pressurization mechanisms T1 and T2 involved in Embodiment 1 will be described. For example... Figures 5-9 As shown, a first recess 124A recessed in the height direction is provided on the upper surface of the upper bearing 24A, and a first through hole 24Ab extending axially through the first bottom surface 124Aa is formed in the first bottom surface 124Aa of the first recess 124A. A first connecting shaft 27A is rotatably mounted in the first through hole 24Ab formed in the first bottom surface 124Aa of the first recess 124A. Furthermore, one end of the first connecting shaft 27A protrudes upward toward the first bottom surface 124Aa, and the other end protrudes downward toward the first bottom surface 124Aa. A first turbine 28A is mounted at one end of the first connecting shaft 27A and disposed above the first bottom surface 124Aa. Furthermore, a first impeller 29A is mounted at the other end of the first connecting shaft 27A and disposed below the first bottom surface 124Aa. Additionally, as... Figure 6 , Figures 15-18As shown, the first impeller 29A is disposed in the first connecting chamber 21Ab, which is part of the first suction flow path 52A. Refrigerant discharged into the first discharge muffler 23A is then blown towards the first turbine 28A, which rotates. The first turbine 28A is mounted at one end of a first connecting shaft 27A rotatably mounted in the first through hole 24Ab. As the first turbine 28A rotates, the first impeller 29A, mounted at the other end of the first connecting shaft 27A, rotates, thereby promoting the flow of refrigerant in the first suction flow path 52A and pressurizing the refrigerant in the first suction chamber 57A. The first turbine 28A, the first connecting shaft 27A, and the first impeller 29A constitute the pressurization mechanism T1.

[0094] like Figures 10-14 As shown, a second recess 124B recessed in the height direction is provided on the lower surface of the lower bearing 24B, and a second through hole 24Bb extending axially through the second bottom surface 124Ba of the second recess 124B is formed therein. A second connecting shaft 27B is rotatably mounted in the second through hole 24Bb formed in the second bottom surface 124Ba of the second recess 124B. Furthermore, one end of the second connecting shaft 27B protrudes downwards from the second bottom surface 124Ba, and the other end protrudes upwards from the second bottom surface 124Ba. A second turbine 28B is mounted at one end of the second connecting shaft 27B and disposed below the second bottom surface 124Ba. A second impeller 29B is mounted at the other end of the second connecting shaft 27B and disposed above the second bottom surface 124Ba. Additionally, as... Figure 11 , Figures 19-22 As shown, the second impeller 29B is disposed in the second connecting chamber 21Bb, which is part of the second suction flow path 52B. Refrigerant discharged into the second discharge muffler 23B is then blown towards the second turbine 28B, which rotates. The second turbine 28B is mounted at one end of the second connecting shaft 27B, which is rotatably mounted on the second through hole 24Bb. As the second turbine 28B rotates, the second impeller 29B, mounted at the other end of the second connecting shaft 27B, rotates, thereby promoting the flow of refrigerant in the second suction flow path 52B and pressurizing the refrigerant in the second suction chamber 57B. The pressurization mechanism T2 is constituted by the second turbine 28B, the second connecting shaft 27B, and the second impeller 29B.

[0095] like Figures 5-9As shown, a first discharge valve 26A, a first valve press member 15A, and a first turbine 28A are disposed in the first recess 124A of the upper bearing 24A. Furthermore, a first discharge flow path 53A is formed on the first bottom surface 124Aa of the first recess 124A. That is, the first discharge flow path 53A is formed in both the first cylinder block 21A and the upper bearing 24A. Additionally, 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 towards the first turbine 28A.

[0096] like Figures 10-14 As shown, a second discharge valve 26B, a second valve press member 15B, and a second turbine 28B are disposed in the second recess 124B of the lower bearing 24B. Furthermore, a second discharge flow path 53B is formed on the second bottom surface 124Ba of the second recess 124B. That is, the second discharge flow path 53B is formed in both the second cylinder block 21B and the lower bearing 24B. Additionally, 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 towards the second turbine 28B.

[0097] By employing this structure, refrigerant discharged from the first discharge path 53A to the outside of the first compression chamber 58A can be guided along the first guide surface 124Ab to the first turbine 28A, thus enabling the first turbine 28A to rotate efficiently. Similarly, refrigerant discharged from the second discharge path 53B to the outside of the second compression chamber 58B can be guided along the second guide surface 124Bb to the second turbine 28B, thus enabling the second turbine 28B to rotate efficiently.

[0098] In addition, such as Figures 5-9 As shown, two first guide surfaces 124Ab are formed by the side surfaces of the first recess 124A, 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 towards the first turbine 28A, the density of the refrigerant guided from the first discharge passage 53A towards the first turbine 28A can be increased, enabling the first turbine 28A to rotate efficiently. Similarly, as Figures 10-14 As shown, two second guide surfaces 124Bb are formed by the side surfaces of the second recess 124B, and the two second guide surfaces 124Bb are configured to move closer to each other as they approach the second turbine 28B. Therefore, when the refrigerant discharged from the second discharge passage 53B to the outside of the second compression chamber 58B is guided along the second guide surfaces 124Bb towards the second turbine 28B, the density of the refrigerant guided from the second discharge passage 53B towards the second turbine 28B can be increased, enabling the second turbine 28B to rotate efficiently.

[0099] like Figure 6As shown, the first discharge valve 26A includes: a first end portion 26Aa, movable in a cantilever beam shape, which closes or opens the first discharge flow path 53A at the end side; and a first base end portion 26Ab, fixed to the upper bearing 24A at the base end side. The first discharge valve 26A is supported by a first valve pressing member 15A. The first valve pressing member 15A is an elongated plate-shaped member with a thickness greater than that of the first discharge valve 26A, which limits the movable range of the first discharge valve 26A and protects the first discharge valve 26A from deformation. The first turbine 28A is positioned on the side opposite to the first base end portion 26Ab of the first discharge valve 26A, with reference to the first end portion 26Aa of the first discharge valve 26A. Figure 11 As shown, the second discharge valve 26B includes: a second end portion 26Ba, which moves in a cantilever beam shape and closes or opens the second discharge passage 53B at its end; and a second base end portion 26Bb, which is fixed to the lower bearing 24B at its base end. The second discharge valve 26B is supported by a second valve pressing member 15B. The second valve pressing member 15B is an elongated plate-shaped member with a thickness greater than that of the second discharge valve 26B, which limits the movable range of the second discharge valve 26B and protects the second discharge valve 26B from deformation. The second turbine 28B is positioned on the side opposite to the second base end portion 26Bb of the second discharge valve 26B, with reference to the second end portion 26Ba of the second discharge valve 26B.

[0100] As described above, the first discharge valve 26A moves in a cantilever beam shape. Therefore, when the refrigerant compressed in the first compression chamber 58A of the first cylinder chamber 55A reaches a preset pressure, the cantilever beam-shaped first end portion 26Aa of the first discharge valve 26A is lifted, opening the first discharge passage 53A. Then, the refrigerant discharged from the opened first discharge passage 53A is blown towards the first turbine 28A, and the pressure energy of the blown refrigerant causes the first turbine 28A to rotate efficiently. Similarly, the second discharge valve 26B moves in a cantilever beam shape. Therefore, when the refrigerant compressed in the second compression chamber 58B of the second cylinder chamber 55B reaches a preset pressure, the cantilever beam-shaped second end portion 26Ba of the second discharge valve 26B is lifted, opening the second discharge passage 53B. Then, the refrigerant discharged from the opened second discharge passage 53B is blown towards the second turbine 28B, and the pressure energy of the blown refrigerant causes the second turbine 28B to rotate efficiently.

[0101] Figure 23 This is a longitudinal sectional view showing the compression mechanism 20 of the rotary compressor 1 according to Embodiment 1. (See attached image.) Figure 23As shown, a first exhaust muffler 23A covering the first exhaust valve 26A and the first turbine 28A is provided on the side of the upper bearing 24A opposite to the first cylinder 21A. Similarly, a second exhaust muffler 23B covering the second exhaust valve 26B and the second turbine 28B is provided on the side of the lower bearing 24B opposite to the second cylinder 21B.

[0102] Conventionally, in rotary compressors, to mitigate the noise from refrigerant discharged through an open discharge path (due to the opening of the discharge valve), a known structure involves providing a discharge muffler covering the discharge valve. Noise reduction is achieved by ensuring the refrigerant discharged from the discharge path collides with the muffler instead of the sealed container. However, this collision results in pressure loss. In Embodiment 1, the refrigerant discharged from the first discharge path 53A and the second discharge path 53B is configured to collide with the first turbine 28A and the second turbine 28B respectively before colliding with the first and second discharge mufflers 23A and 23B. Therefore, the pressure energy of the refrigerant can be used to efficiently rotate the first turbine 28A and the second turbine 28B.

[0103] Furthermore, the first discharge muffler 23A and the second discharge muffler 23B respectively cover the first discharge valve 26A and the first turbine 28A, as well as the second discharge valve 26B and the second turbine 28B. Therefore, the refrigerant discharged from the first discharge path 53A and the second discharge path 53B can collide with the first discharge muffler 23A and the second discharge muffler 23B respectively, instead of colliding with the sealed container 10, thereby achieving noise reduction. In this way, the discharge noise of the refrigerant discharged from the first discharge path 53A and the second discharge path 53B can be mitigated by the first discharge muffler 23A and the second discharge muffler 23B. Additionally, the refrigerant discharged from the first discharge path 53A and the second discharge path 53B is configured such that it collides 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 used to efficiently rotate the first turbine 28A and the second turbine 28B.

[0104] like Figure 23As shown, a discharge port 23Aa is formed in the first discharge muffler 23A. 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 through the discharge port 23Aa. Furthermore, an axially extending refrigerant flow path 59 is formed between the upper bearing 24A, the first cylinder 21A, the partition plate 25, the second cylinder 21B, and the lower bearing 24B. The second discharge muffler 23B is connected to the first discharge muffler 23A via the refrigerant flow path 59. Thus, the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged into the second discharge muffler 23B and then flows into the first discharge muffler 23A via the refrigerant flow path 59. Then, the refrigerant flowing into the first discharge muffler 23A is released from the discharge port 23Aa of the first discharge muffler 23A into the interior of the sealed container 10.

[0105] The rotating shaft 40 is rotated by the rotating motor 30, causing the first eccentric shaft portion 40A and the second eccentric shaft portion 40B of the rotating shaft 40 to move eccentrically 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 a predetermined pressure, the first end portion 26Aa of the first discharge valve 26A and the second end portion 26Ba of the second discharge valve 26B are lifted. This opens the first discharge passage 53A and the second discharge passage 53B, allowing refrigerant to be discharged from the first discharge passage 53A and the second discharge passage 53B, respectively, to the outside of the first compression chamber 58A and the second compression chamber 58B. The refrigerant discharged from the first compression chamber 58A and the second compression chamber 58B respectively causes the first turbine 28A and the second turbine 28B to rotate. Then, as the first turbine 28A and the second turbine 28B rotate, the first impeller 29A and the second impeller 29B also rotate. The rotation of the first impeller 29A and the second impeller 29B promotes the flow of refrigerant flowing in the first suction flow path 52A and the second suction flow path 52B.

[0106] In this way, the pressure energy of the refrigerant 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 second compression chamber 58B is used to rotate the first impeller 29A and the second impeller 29B. This promotes the flow of refrigerant in the first suction flow path 52A and the second suction flow path 52B, respectively. As a result, the refrigerant in the first suction chamber 57A and the second suction chamber 57B is pressurized, increasing the capacity of the rotary compressor 1. Furthermore, by pressurizing the first suction chamber 57A and the second suction chamber 57B, the work done by the rotary compressor 1 per revolution can be reduced.

[0107] In more detail, in the turbocharger of the prior art, gas is guided from the outlet in the auxiliary housing to the rotating blades via a discharge pipe provided outside the main housing for power recovery. In contrast, in the rotary compressor 1 according to Embodiment 1, refrigerant is guided from the first discharge passage 53A and the second discharge passage 53B provided in the upper bearing 24A and the lower bearing 24B to the first turbine 28A and the second turbine 28B of the booster mechanisms T1 and T2 provided in the upper bearing 24A and the lower bearing 24B for power recovery. Therefore, pressure loss as in the past is not generated, and power recovery is highly efficient. Thus, by providing the booster mechanisms T1 and T2 driven by the refrigerant discharged from the compression mechanism 20 in the compression mechanism 20, pressure loss can be reduced.

[0108] Figure 24 This is a side view of the booster mechanisms T1 and T2 of the rotary compressor 1 according to Embodiment 1. Figure 25 This is a single impeller diagram of the rotary compressor 1 according to Embodiment 1. Figure 26 This is a diagram of the turbine unit of the rotary compressor 1 according to Embodiment 1. Figure 27 This is a single-unit diagram of the connecting shaft of the rotary compressor 1 according to Embodiment 1. Furthermore, Figure 24 (a) shows a side view of the supercharger T1, and (b) shows a side view of the supercharger T2. Additionally, Figure 25 and Figure 26 (a) represents a top view, (b) represents a side view, (c) represents a bottom view, and (d) represents a perspective view. Additionally, Figure 27 (a) represents a top view, (b) represents a side view, and (c) represents a perspective view. Additionally, Figure 25 The first impeller 29A is shown, but since the second impeller 29B has the same shape, it is omitted from the illustration. Additionally, Figure 26 The first turbine 28A is shown, but since the second turbine 28B has the same shape, it is omitted from the illustration. Additionally, Figure 27 The first connecting shaft 27A is shown, but since the second connecting shaft 27B has the same shape, it is omitted from the illustration.

[0109] like Figures 24-27As shown, the first turbine 28A is circular when viewed from above. Furthermore, the first turbine 28A includes a first turbine blade assembly 28Aa consisting of multiple blades that allow refrigerant to flow in radially outward and outward toward the axis. The first impeller 29A includes a first impeller blade assembly 29Aa consisting of multiple blades that allow refrigerant to flow in radially outward and outward toward the axis. Similarly, the second turbine 28B is circular when viewed from above. Furthermore, the second turbine 28B includes a second turbine blade assembly 28Ba consisting of multiple blades that allow refrigerant to flow in radially outward and outward toward the axis. The second impeller 29B includes a second impeller blade assembly 29Ba consisting of multiple blades that allow refrigerant to flow in radially outward and outward toward the axis.

[0110] Thus, by having a first turbine blade set 28Aa and a second turbine blade set 28Ba, a first discharge valve 26A and a second discharge valve 26B can be arranged radially outside the first turbine 28A and the second turbine 28B. Furthermore, by having a first impeller blade set 29Aa and a second impeller blade set 29Ba, a first suction chamber 57A and a second suction chamber 57B can be arranged radially outside the first impeller 29A and the second impeller 29B.

[0111] Figure 28 yes Figure 18 A view of section AA. Figure 29 yes Figure 22 A view of the BB section. Furthermore... Figure 28 Represented upside down. For example... Figure 28 As shown, the first impeller blade group 29Aa includes a first impeller blade base end group 29Aaa as the base end side in the axial direction and a first impeller blade end portion group 29Aab as the end side in the axial direction. The diameter of the first impeller blade base end group 29Aaa is configured to be larger than the diameter of the first impeller blade end portion group 29Aab. A first step portion 21Aa is formed in the first cylinder body 21A. The first step portion 21Aa has an opening on one side of the first cylinder body 21A in the height direction and communicates with the first suction flow path 52A (first communicating chamber 21Ab), accommodating the outer periphery of the first impeller blade base end group 29Aaa. The second impeller blade group 29Ba includes a second impeller blade base end group 29Baa as the base end side in the axial direction and a second impeller blade end portion group 29Bab as the end side in the axial direction. The diameter of the second impeller blade base end group 29Baa is configured to be larger than the diameter of the second impeller blade end portion group 29Bab. A second step portion 21Ba is formed in the second cylinder body 21B. The second step portion 21Ba opens on one side of the second cylinder body 21B in the height direction and communicates with the second suction flow path 52B (second communication chamber 21Bb), and accommodates the outer periphery of the second impeller blade base end group 29Baa.

[0112] In this configuration, the outer periphery of the first impeller blade base end group 29Aaa and the outer periphery of the second impeller blade base end group 29Baa are respectively housed in the first stepped portion 21Aa formed in the first cylinder body 21A and the second stepped portion 21Ba formed in the second cylinder body 21B. Therefore, the first impeller blade end group 29Aab and the first impeller blade base end group 29Aaa can be arranged along the inner surface of the first stepped portion 21Aa, which communicates with the first suction flow path 52A of the first cylinder body 21A. As a result, refrigerant can flow into and out of the first impeller blade group 29Aa efficiently. Similarly, the second impeller blade end group 29Bab and the second impeller blade base end group 29Baa can be arranged along the inner surface of the second stepped portion 21Ba, which communicates with the second suction flow path 52B of the second cylinder body 21B. As a result, the refrigerant can flow into the second impeller blade group 29Ba efficiently and flow out of the second impeller blade group 29Ba efficiently.

[0113] In this way, since the outer periphery of the first impeller blade base end group 29Aaa and the outer periphery of the second impeller blade base end group 29Baa are respectively housed in the first step portion 21Aa and the second step portion 21Ba formed in the first cylinder body 21A and the second cylinder body 21B, the refrigerant can flow into the first impeller blade group 29Aa and the second impeller blade group 29Ba efficiently, and the refrigerant can flow out from the first impeller blade group 29Aa and the second impeller blade group 29Ba efficiently.

[0114] The compression mechanism 20 of the rotary compressor 1 according to Embodiment 1 includes two cylinder chambers, a first cylinder chamber 55A and a second cylinder chamber 55B, which share a partition plate 25 constituting the first cylinder chamber 55A and a partition plate 25 constituting the second cylinder chamber 55B. That is, the rotary compressor 1 according to Embodiment 1 is a dual-rotation rotary compressor. Therefore, compared with a single-rotation rotary compressor having one cylinder chamber, the rotary compressor 1 according to Embodiment 1 can improve the refrigerant compression capacity.

[0115] The rotary compressor 1 according to Embodiment 1 includes: a sealed container 10 forming a housing; a rotary motor 30 housed within the sealed container 10; a rotating shaft 40 housed within the sealed container 10 and rotated by the rotary motor 30, and having an eccentric shaft portion; a compression mechanism 20 housed within the sealed container 10 and having a cylinder chamber for compressing refrigerant by the eccentric movement of the eccentric shaft portion; and booster mechanisms T1 and T2 housed within the sealed container 10. The compression mechanism 20 includes: a cylinder body forming an intake flow path for drawing low-pressure refrigerant from the outside of the sealed container 10 into the cylinder chamber; a piston fitted into the eccentric shaft portion; a vane dividing the cylinder chamber formed by the inner circumference of the cylinder body and the outer circumference of the piston into an intake chamber and a compression chamber; and a bearing. The pressurizing mechanisms T1 and T2 include: a connecting shaft rotatably supported on a bearing; a turbine connected to one end of the connecting shaft and rotating by the refrigerant discharged from the open discharge path; and an impeller connected to the other end of the connecting shaft and rotating with the turbine to promote the flow of refrigerant flowing in the suction path. The turbine is fixed to one side of the cylinder body in the height direction, sealing one side of the cylinder chamber and forming a discharge flow path for discharging compressed refrigerant to the outside of the compressor chamber; a sealing component fixed to the other side of the cylinder body in the height direction and sealing the other side of the cylinder chamber; and a discharge valve disposed on a bearing, sealing the discharge flow path, and opening the discharge flow path when the refrigerant compressed in the cylinder chamber reaches a preset pressure.

[0116] According to the rotary compressor 1 of Embodiment 1, the booster mechanisms T1 and T2 include: a connecting shaft rotatably supported on a bearing; a turbine connected to one end of the connecting shaft and rotating via refrigerant discharged from the open discharge passage; and an impeller connected to the other end of the connecting shaft and rotating with the turbine to promote the flow of refrigerant flowing in the suction passage. In other words, since the booster mechanisms T1 and T2, driven by refrigerant discharged from the compression mechanism 20, are provided in the compression mechanism 20, pressure loss as in the past is not generated, and pressure loss can be reduced.

[0117] Furthermore, in the rotary compressor 1 according to Embodiment 1, the turbine has a turbine blade assembly consisting of a plurality of blades that allow refrigerant to flow in from the radially outer side and to flow out of the refrigerant in the axial direction, and the impeller has an impeller blade assembly consisting of a plurality of blades that allow refrigerant to flow in from the axial direction and to flow out of the refrigerant in the radially outer side.

[0118] According to Embodiment 1, the rotary compressor 1 has a turbine with a turbine blade assembly, allowing a discharge valve to be disposed radially outside the turbine. Additionally, the impeller has an impeller blade assembly, allowing a suction chamber to be disposed radially outside the impeller.

[0119] Furthermore, in the rotary compressor 1 according to Embodiment 1, the impeller blade assembly includes an impeller blade base end assembly as the base end side in the axial direction and an impeller blade end portion assembly as the end side in the axial direction. The diameter of the impeller blade base end assembly is configured to be larger than the diameter of the impeller blade end portion assembly. A stepped portion is formed in the cylinder body. The stepped portion opens on one side of the cylinder body in the height direction and communicates with the suction flow path, and accommodates the outer periphery of the impeller blade base end assembly.

[0120] According to Embodiment 1, the rotary compressor 1 is configured such that the outer periphery of the impeller blade base end group is housed in the stepped portion of the cylinder, thereby enabling the refrigerant to flow into the impeller blade group efficiently and to flow out of the impeller blade group efficiently.

[0121] In addition, in the rotary compressor 1 according to Embodiment 1, a recess is provided on the bearing side opposite to the cylinder for arranging a discharge valve and a turbine. The recess has a discharge flow path formed on the bottom surface and a guide surface formed on the side surface to guide the refrigerant discharged from the discharge flow path to the turbine.

[0122] According to Embodiment 1, the rotary compressor 1 can guide the refrigerant discharged from the discharge path to the compressor room along the guide surface to the turbine, thus enabling the turbine to rotate efficiently.

[0123] Furthermore, in the rotary compressor 1 according to Embodiment 1, the recess has two guide surfaces, which are configured to move closer to each other as they approach the turbine.

[0124] According to Embodiment 1, the rotary compressor 1 can increase the density of the refrigerant being guided from the discharge path toward the turbine when the refrigerant discharged from the discharge path toward the compressor room is guided along the guide surface toward the turbine, thereby enabling the turbine to rotate efficiently.

[0125] Furthermore, in the rotary compressor 1 according to Embodiment 1, the discharge valve moves in a cantilever beam shape and has an end portion that closes or opens the discharge flow path and a base end portion that is fixed to the bearing. The turbine is provided on the side opposite to the base end portion of the discharge valve with reference to the end portion of the discharge valve.

[0126] According to the rotary compressor 1 of Embodiment 1, the discharge valve moves in a cantilever beam shape. Therefore, when the refrigerant compressed in the compression chamber of the cylinder reaches a preset pressure, the cantilever beam end of the discharge valve is lifted, opening the discharge flow path. The refrigerant discharged from the opened discharge flow path is blown toward the turbine side. The pressure energy of the blown refrigerant enables the turbine to rotate efficiently.

[0127] In addition, in the rotary compressor 1 according to embodiment 1, a discharge muffler covering the discharge valve and the turbine is provided on the side of the bearing opposite to the cylinder, and a discharge hole 23Aa is formed in the discharge muffler.

[0128] According to Embodiment 1, the rotary compressor 1 can mitigate the discharge noise of refrigerant discharged from the discharge path by using a discharge muffler. Furthermore, the compressor is configured such that the refrigerant discharged from the discharge path collides with the impeller before colliding with the discharge muffler, thus enabling efficient impeller rotation using the pressure energy of the refrigerant.

[0129] Furthermore, in the rotary compressor 1 according to Embodiment 1, the compression mechanism 20 has multiple cylinder chambers.

[0130] According to Embodiment 1, the rotary compressor 1 is a multi-cylinder rotary compressor with multiple cylinder chambers, which improves the refrigerant compression capacity compared to a single-cylinder rotary compressor with one cylinder chamber.

[0131] In addition, the refrigeration cycle apparatus 200 according to Embodiment 1 includes: the rotary compressor 1 described above; a radiator for dissipating heat from the refrigerant compressed by the rotary compressor 1; a pressure reducer 203 for reducing the pressure of the refrigerant flowing out of the radiator; and an evaporator for evaporating the refrigerant flowing out of the pressure reducer 203.

[0132] In addition, the refrigeration cycle device 200 according to Embodiment 1 uses any single refrigerant from R1234yf, R1234ze, R32, R290, or any two or more of them mixed refrigerants, or any one of them mixed with other refrigerants, or a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123.

[0133] According to the refrigeration cycle device 200 of Embodiment 1, the same effect as the rotary compressor 1 described above can be obtained.

[0134] Implementation Method 2

[0135] In Embodiment 1 described above, a booster mechanism T1 and T2 are configured in the dual-rotary rotary compressor 1. However, Embodiment 2, in which a booster mechanism T1 and T2 are configured in the single-rotary rotary compressor 301, will be described next.

[0136] Figure 30 This is a longitudinal sectional view showing the overall structure of the single-rotary rotary compressor 301 according to Embodiment 2. Figure 30The single-rotary rotary compressor 301 shown may also be configured to include booster mechanisms T1 and T2. Furthermore, although not shown, multi-cylinder rotary compressors, such as three-rotary rotary compressors, may also be configured to include booster mechanisms T1 and T2.

[0137] Explanation of reference numerals in the attached figures

[0138] 1… Rotary compressor; 2A… First suction pipe; 2B… Second suction pipe; 3… Suction silencer; 4… Discharge pipe; 6… Refrigeration oil; 10… Sealed container; 11… Head; 12… Main body; 13… Bottom; 15A… First valve press; 15B… Second valve press; 20… Compression mechanism; 21A… First cylinder; 21Aa… First step; 21Ab… First connecting chamber; 21B… Second cylinder; 21Ba… Second step; 21Bb… Second connecting chamber; 22A… First piston; 22B… Second piston; 23A… First discharge silencer; 23Aa… Discharge port; 23B… Second discharge silencer; 24A… Upper bearing; 24Ab… First through hole; 24B…lower bearing; 24Bb…second through hole; 25…partition plate; 26A…first discharge valve; 26Aa…first end portion; 26Ab…first base end portion; 26B…second discharge valve; 26Ba…second end portion; 26Bb…second base end portion; 27A…first connecting shaft; 27B…second connecting shaft; 28A…first turbine; 28Aa…first turbine blade assembly; 28B…second turbine; 28Ba…second turbine blade assembly; 29A…first impeller; 29Aa…first impeller blade assembly; 29Aaa…first impeller blade base end assembly; 29Aab…first impeller blade end portion assembly; 29B…second impeller; 29Ba…second… Impeller blade assembly; 29Baa…Second impeller blade base end assembly; 29Bab…Second impeller blade tip assembly; 30…Rotating motor; 31…Rotor; 32…Stator; 40…Rotating shaft; 40A…First eccentric shaft; 40B…Second eccentric shaft; 41…Lower end; 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 flow path; 52B…Second suction flow path; 53A…First discharge flow path; 53B…Second discharge flow path; 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; 59…Refrigerant flow path between mufflers; 124A…First recess; 124Aa…First bottom surface; 124Ab…First guide surface; 124B…Second recess; 124Ba…Second bottom surface; 124Bb…Second guide surface; 200…Refrigeration cycle device; 201…Flow path switching valve; 202…Outdoor heat exchanger; 203…Pressure reducer; 204…Indoor heat exchanger; 301…Rotary compressor; T1…Boosting mechanism; T2…Boosting mechanism.

Claims

1. A rotary compressor, characterized in that, have: A sealed container, forming the outer shell; A rotary motor is housed within the sealed container; A rotating shaft is housed within the sealed container and rotated by the rotating motor, and has an eccentric shaft portion; A compression mechanism, housed within the sealed container, and having a cylinder chamber for compressing the refrigerant via the eccentric movement of the eccentric shaft; and The pressurization mechanism is housed within the sealed container. The compression mechanism comprises: The cylinder body has an intake flow path for drawing low-pressure refrigerant from the outside of the sealed container into the cylinder chamber; The piston is fitted into the eccentric shaft portion; A sliding vane divides the cylinder chamber, formed by the inner circumference of the cylinder body and the outer circumference of the piston, into an intake chamber and a compression chamber. The bearing is fixed to one side of the cylinder body in the height direction and closes one side of the cylinder chamber, and forms a discharge flow path for discharging the compressed refrigerant to the outside of the compressor. A sealing component, fixed to the other side of the cylinder block in the height direction, and sealing the other side of the cylinder chamber; and A discharge valve is disposed on the bearing and closes the discharge passage. When the refrigerant compressed in the compression chamber of the cylinder reaches a preset pressure, the discharge passage is opened. The pressurization mechanism includes: The connecting shaft is rotatably supported by the bearing; A turbine is connected to one end of the connecting shaft and rotates through the refrigerant discharged from the open discharge passage; as well as An impeller, connected to the other end of the connecting shaft, rotates as the turbine rotates to facilitate the flow of refrigerant in the suction path.

2. The rotary compressor according to claim 1, characterized in that, The turbine has a turbine blade assembly consisting of multiple blades that allow refrigerant to flow in radially outward and outward towards the axis. The impeller has an impeller blade assembly consisting of multiple blades that allow refrigerant to flow in from the axial direction and flow out radially outward.

3. The rotary compressor according to claim 2, characterized in that, The impeller blade assembly includes: As the base end group of the impeller blades on the base end side in the axial direction; and As the end-side impeller blade end assembly in the axial direction, The diameter of the base end group of the impeller blades is larger than the diameter of the tip end group of the impeller blades. A stepped portion is formed in the cylinder body, which opens on one side of the cylinder body in the height direction and communicates with the suction flow path, and accommodates the outer periphery of the impeller blade base end assembly.

4. The rotary compressor according to any one of claims 1 to 3, characterized in that, The bearing has a recess on the side opposite to the cylinder block where the discharge valve and the turbine are disposed. The recess has: The discharge path is formed on the bottom surface; and A guide surface, formed on the side, guides the refrigerant discharged from the discharge path toward the turbine.

5. The rotary compressor according to claim 4, characterized in that, The recess has two guide surfaces. The two guide surfaces are configured to move closer to each other as they approach the turbine.

6. The rotary compressor according to any one of claims 1 to 5, characterized in that, The discharge valve includes: The end portion moves in a cantilever beam shape, and closes or opens the discharge path; and The base end is fixed to the bearing. The turbine is positioned on the side opposite to the base end of the discharge valve, with the end portion of the discharge valve as a reference.

7. The rotary compressor according to any one of claims 1 to 6, characterized in that, A discharge muffler covering the discharge valve and the turbine is provided on the side of the bearing opposite to the cylinder block. The exhaust muffler has an exhaust port.

8. The rotary compressor according to any one of claims 1 to 7, characterized in that, The compression mechanism has multiple cylinder chambers.

9. A refrigeration cycle device, characterized in that, have: The rotary compressor according to any one of claims 1 to 8; A radiator for dissipating heat from the refrigerant compressed by the rotary compressor; A pressure reducer is used to reduce the pressure of the refrigerant flowing out of the radiator; as well as An evaporator that causes the refrigerant flowing out of the pressure reducer to evaporate.

10. The refrigeration cycle device according to claim 9, characterized in that, Use any single refrigerant from R1234yf, R1234ze, R32, R290, or any combination of two or more of them, or any combination of them with other refrigerants, or a combination of refrigerants containing R1132(E), or a combination of refrigerants containing R1123.

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