Multi-cylinder rotary compressor and refrigeration cycle device

Abstract

The multi-cylinder rotary compressor of the present invention comprises: a sealed container forming a shell; a rotary motor housed within the sealed container; a rotating shaft housed within the sealed container, rotating via the rotary motor, and having an eccentric shaft portion; a compression mechanism housed within the sealed container, 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 flow path for drawing low-pressure refrigerant into the cylinder chamber from the outside of the sealed container; 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 fixed to one side of the cylinder body in the height direction. The pressurizing mechanism comprises: a sealing member fixed to the other side of the cylinder body in the height direction, sealing the other side of the cylinder chamber and forming a discharge passage for discharging compressed refrigerant to the compressor chamber; and a discharge valve provided on the sealing member to close the discharge passage and to open the discharge passage when the refrigerant compressed in the compression chamber of the cylinder reaches a preset pressure. The pressurizing mechanism includes: a connecting shaft rotatably supported on the sealing member; a turbine connected to one end of the connecting shaft and rotating 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 refrigerant flowing in the suction passage.

Description

Technical Field

[0001] This disclosure relates to a multi-cylinder rotary compressor and a refrigeration cycle device. 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 comprises a main housing housing the motor, rotating blades, supercharger, and shaft, and a sub-housing housing housing the rotor. The main housing and sub-housing 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 within the motor chamber, and the rotor is housed within the sub-housing housing. An exhaust port provided in the sub-housing housing is connected to a communication hole provided in a manner communicating with the receiving chamber of the main housing via an exhaust pipe. The main housing has an exhaust port communicating with the receiving chamber and discharging compressed gas, and an intake port communicating with the motor chamber and drawing in intake gas from outside the main housing.

[0003] In this turbocharger configuration, the rotation of the motor causes the rotor to rotate. 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 then drives the rotating blades to rotate, and this gas exits from the main housing's exhaust port. Conversely, intake gas flows in from the intake port, is pressurized by the turbocharger rotating with the rotating blades, becomes high-density, 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 then blown onto the rotating blades. Therefore, a problem arises: 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 above-mentioned problems, and its purpose is to provide a multi-cylinder 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 multi-cylinder 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, rotating via the rotary motor, and having an eccentric shaft portion; a compression mechanism housed within the sealed container, 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 flow path for drawing low-pressure refrigerant from outside the sealed container 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 fixed to one side of the cylinder body in the height direction. The pressurizing mechanism includes: a connecting shaft rotatably supported on the sealing member; 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 pressurizing mechanism also includes: a sealing member fixed to the other side of the cylinder body in the height direction, sealing the other side of the cylinder chamber and forming a discharge passage for discharging compressed refrigerant to the outside of the compression chamber; and a discharge valve provided on the sealing member, sealing the discharge passage and opening it when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a predetermined pressure.

[0008] Furthermore, the refrigeration cycle apparatus disclosed herein includes: the aforementioned multi-cylinder rotary compressor; a radiator for dissipating heat from the refrigerant compressed by the aforementioned multi-cylinder rotary compressor; a pressure reducer for reducing the pressure of the refrigerant flowing out of the aforementioned radiator; and an evaporator for evaporating the refrigerant flowing out of the aforementioned pressure reducer.

[0009] According to the multi-cylinder rotary compressor and refrigeration cycle device disclosed herein, the booster mechanism includes: a connecting shaft rotatably supported on a closed component; a turbine connected to one end of the connecting shaft and rotating via refrigerant discharged from an 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. That is, since a booster mechanism driven by refrigerant discharged from the compression mechanism is provided in the compression mechanism, pressure loss as in the past is not generated, and pressure loss can be reduced. Attached Figure Description

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

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

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

[0014] Figure 5 This is a bottom perspective view of the first partition plate, the first cylinder and the first turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0015] Figure 6 This is a longitudinal sectional view showing the first partition plate, the first cylinder, and the first turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0016] Figure 7 This is a bottom view showing the first partition plate, the first cylinder and the first turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0017] Figure 8 This is a bottom perspective view of the first partition plate of the multi-cylinder rotary compressor involved in Embodiment 1.

[0018] Figure 9 This is a top view showing the first partition plate of the multi-cylinder rotary compressor according to Embodiment 1.

[0019] Figure 10 This is a bottom perspective view of the second partition plate, the second cylinder and the second turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0020] Figure 11 This is a longitudinal sectional view showing the second partition plate, the second cylinder, and the second turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0021] Figure 12 This is a top view showing the second partition plate, the second cylinder, and the second turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0022] Figure 13 This is a bottom perspective view of the second partition plate of the multi-cylinder rotary compressor involved in Embodiment 1.

[0023] Figure 14 This is a bottom view showing the second partition plate of the multi-cylinder rotary compressor involved in Embodiment 1.

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

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

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

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

[0028] Figure 19 yes Figure 18 A view of section AA.

[0029] Figure 20 This is a longitudinal sectional view of the second cylinder of the multi-cylinder rotary compressor according to Embodiment 1.

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

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

[0032] Figure 23 This is a top view showing the second cylinder and the second impeller of the multi-cylinder rotary compressor according to Embodiment 1.

[0033] Figure 24 yes Figure 23 A view of the BB section.

[0034] Figure 25 This is a longitudinal sectional view showing the compression mechanism of the multi-cylinder rotary compressor according to Embodiment 1.

[0035] Figure 26 This is a side view showing the booster mechanism of the multi-cylinder rotary compressor according to Embodiment 1.

[0036] Figure 27 This is a single-unit diagram showing the impeller of the multi-cylinder rotary compressor involved in Embodiment 1.

[0037] Figure 28 This is a single-unit diagram showing the turbine of the multi-cylinder rotary compressor involved in Embodiment 1.

[0038] Figure 29 This is a single-unit diagram showing the connecting shaft of the multi-cylinder rotary compressor involved in Embodiment 1. Detailed Implementation

[0039] 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 sometimes differ from actual dimensions.

[0040] Implementation Method 1

[0041] Figure 1 This is a longitudinal sectional view showing the overall structure of the multi-cylinder 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 multi-cylinder 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 multi-cylinder rotary compressor 1 according to Embodiment 1.

[0042] [Structure of Multi-Cylinder Rotary Compressor 1]

[0043] The multi-cylinder rotary compressor 1 involved in embodiment 1 adopts, as follows: Figure 1 The illustrated multi-cylinder rotary compressor has two cylinders (first cylinder 21A and second cylinder 21B), i.e., a dual-rotary compressor. The overall structure of the multi-cylinder rotary compressor 1, which is a dual-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 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 multi-cylinder rotary compressor 1. The first suction pipe 2A and the second suction pipe 2B are used to supply refrigerant into 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 is used to compress 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 together with the rotor 31. The discharge pipe 4 is used to discharge the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. The detailed structure of the multi-cylinder rotary compressor 1 will be described below.

[0044] (10 sealed containers)

[0045] The sealed container 10, which constitutes the outer shell of the multi-cylinder rotary compressor 1, houses the compression mechanism 20, the rotary motor 30, and the rotary shaft 40, etc. The sealed container 10 has a head 11, a bottom 13, and a main body 12. The head 11 constitutes the upper outer shell of the multi-cylinder rotary compressor 1. The bottom 13 constitutes the lower outer shell of the multi-cylinder rotary compressor 1. The main body 12 constitutes the middle outer shell of the multi-cylinder rotary compressor 1, with the head 11 mounted on its upper part and the bottom 13 mounted on its lower part.

[0046] 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.

[0047] 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.

[0048] like Figure 1 As shown, the bottom 13 forming 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, etc., to reduce friction at sliding parts of the compression mechanism 20, etc.

[0049] (First inhalation tube 2A and second inhalation tube 2B)

[0050] 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 25 The first suction pipe 2A is connected to the second suction flow path 52B of the second cylinder 21B of the compression mechanism 20 (see reference 3). Additionally, the other end of the first suction pipe 2A is connected to the suction muffler 3. Figure 25 The second intake pipe 2B is connected to the intake muffler 3. Additionally, the general terminology that begins with "first" or "second" will sometimes be referred to without "first" or "second". For example, the general terminology for "first cylinder block 21A" and "second cylinder block 21B" is simply "cylinder block".

[0051] (Inhalation silencer 3)

[0052] The intake muffler 3 functions as a muffler to reduce refrigerant noise and other sounds generated when refrigerant flows into the multi-cylinder rotary compressor 1. Furthermore, 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.

[0053] (Compression mechanism 20)

[0054] The compression mechanism 20 is connected to the rotating shaft 40, and compresses the refrigerant drawn in from the outside by means of the power transmitted by the rotating motor 30 through the rotating shaft 40. 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.

[0055] 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, a first partition plate 25A, and a second partition plate 25B. Hereinafter, the first partition plate 25A and the second partition plate 25B are sometimes also referred to as bearings or sealing components.

[0056] The first cylinder body 21A is cylindrical, with a first cylinder chamber 55A formed in its central portion. The first cylinder body 21A has a first suction flow path 52A for drawing refrigerant in through a 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.

[0057] 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, which is formed to extend radially 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.

[0058] 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, communicating 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, sealing the first cylinder chamber 55A. The upper bearing 24A supports the rotating shaft 40 so that it can rotate.

[0059] The second cylinder 21B is cylindrical and positioned below the first cylinder 21A, forming a second cylinder chamber 55B 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.

[0060] 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, which is formed to extend radially 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.

[0061] The second spring hole 54B is formed radially at the outer end of the second slide groove 56B of the second cylinder body 21B and axially extends through the second cylinder body 21B, communicating with the second slide groove 56B. The second spring 51B is received in the second spring hole 54B, pressing the second slide 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.

[0062] The first partition plate 25A is configured to abut against the lower end face of the first cylinder block 21A and close the first cylinder chamber 55A. The second partition plate 25B is configured to abut against the upper end face of the second cylinder block 21B and close the second cylinder chamber 55B. Furthermore, the lower end face of the first partition plate 25A and the upper end face of the second partition plate 25B are configured to abut against each other.

[0063] 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.

[0064] Furthermore, the first piston 22A is connected to the rotating shaft 40 in a manner that its rotational phase relative to the second piston 22B within the second cylinder 21B is offset by 180 degrees. In other words, the second piston 22B is connected to the rotating shaft 40 in a manner that its rotational phase relative to the first piston 22A within the first cylinder 21A is offset by -180 degrees.

[0065] Additionally, a first discharge valve 26A (described later) is provided in the upper bearing 24A (see reference). Figure 6 The first discharge valve 26A releases the refrigerant compressed by the first cylinder 21A and the first piston 22A. Opening the first discharge valve 26A allows the first discharge path 53A to connect with the first discharge muffler 23A, described later. Furthermore, a second discharge valve 26B, described later, is provided on the lower bearing 24B (see [reference]). Figure 11 The second discharge valve 26B releases the refrigerant compressed by the second cylinder 21B and the second piston 22B. By opening the second discharge valve 26B, the second discharge flow path 53B can be connected to the second discharge muffler 23B, which will be described later.

[0066] (Rotary motor 30 and rotating shaft 40)

[0067] 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.

[0068] 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 together with the rotor 31. Additionally, Figure 1 The rotating shaft 40 shown rotates around an axis extending vertically along the plane of the paper. Furthermore, 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 compresses the refrigerant drawn in from the outside by means of the power of the rotary motor 30 transmitted by the rotary shaft 40.

[0069] (Drain pipe 4)

[0070] 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.

[0071] (Centrifugal pump 45)

[0072] 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. Furthermore, 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 position on the outer circumferential surface of the rotating shaft 40 opposite to the compression mechanism 20. In Embodiment 1, the other end of the first oil supply port 43 opens at a position 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 position opposite to the lower bearing 24B of the compression mechanism 20.

[0073] 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 into the oil supply port 42 by the centrifugal pump 45 is supplied to the sliding part of the compression mechanism 20. Specifically, a portion of the refrigerant oil 6 drawn into the oil supply port 42 is supplied to the sliding part between the upper bearing 24A of the compression mechanism 20 and the rotating shaft 40 through the first oil supply port 43. In addition, a portion of the refrigerant oil 6 drawn into the oil supply port 42 is supplied to the sliding part between the lower bearing 24B of the compression mechanism 20 and the rotating shaft 40 through the second oil supply port 44. As the refrigerant oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, and polyol ester-based lubricants are used.

[0074] [Operation of the rotary motor 30]

[0075] 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, thereby forming a rotating magnetic field on the stator 32. This rotating magnetic field of the stator 32 acts on the permanent magnet disposed on 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.

[0076] [Refrigerant flow]

[0077] Refrigerant is drawn into the multi-cylinder rotary compressor 1 through the eccentric rotation of the first piston 22A and the second piston 22B. Specifically, low-pressure refrigerant outside the multi-cylinder rotary compressor 1 flows into the suction muffler 3 through the eccentric rotation of the first piston 22A and the second piston 22B. Then, the low-pressure gaseous refrigerant flowing into the suction muffler 3 flows into the compression mechanism 20 of the multi-cylinder rotary compressor 1 through 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 into a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant flows through the first discharge path 53A, the first outlet hole 151 (described later), the second outlet hole 152, and the third outlet hole 153 (see reference). Figure 25 The high-temperature and high-pressure gaseous refrigerant flowing into the first discharge muffler 23A flows out from the discharge port 23Aa (described later) of the first discharge muffler 23A. Figure 25The high-temperature and high-pressure gaseous refrigerant released into the space inside the sealed container 10 is then moved to the upper part of the space inside the sealed container 10 through gaps in the rotary motor 30 and other parts, and discharged from the discharge pipe 4.

[0078] 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, becoming a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant flows through the second discharge path 53B, the first outlet port 151 (described later), the second outlet port 152, and the third outlet port 153 (see reference). Figure 25 The high-temperature and high-pressure gaseous refrigerant fed into the first discharge muffler 23A then flows into the first discharge muffler 23A through the discharge port 23Aa (described later) located in the first discharge muffler 23A. Figure 25 The high-temperature and high-pressure gaseous refrigerant released into the space inside the sealed container 10 is then moved to the upper part of the space inside the sealed container 10 through gaps in the rotary motor 30 and other parts, and discharged from the discharge pipe 4.

[0079] Furthermore, 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. In addition, 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. Through the flow of refrigerant oil 6 between these parts, the rotating shaft 40 can smoothly transmit the rotational driving force to the first piston 22A and the second piston 22B.

[0080] Furthermore, 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. Additionally, the refrigerant oil 6 is used to facilitate the 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.

[0081] [Structure and operation of refrigeration cycle unit 200]

[0082] Figure 4 This is a schematic diagram illustrating a refrigeration cycle device 200 equipped with the multi-cylinder rotary compressor 1 according to Embodiment 1. Next, using... Figure 4A refrigeration cycle unit 200 equipped with a multi-cylinder 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 4 An example of a refrigeration cycle unit 200 used as an air conditioning unit is shown. 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. Furthermore, Figure 4 The refrigeration cycle unit 200 shown can also operate in a refrigeration manner. Therefore, the refrigeration cycle unit 200 is equipped with a flow path switching valve 201. The refrigeration cycle unit 200 includes: a multi-cylinder rotary compressor 1 having 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 for refrigerant circulation.

[0083] Examples of refrigerants circulating in the refrigerant circuit include fluorinated or hydrocarbon refrigerants with low Global Warming Potential (GWP). Furthermore, examples of such refrigerants include any single refrigerant from R1234yf, R1234ze, R32, and R290, or mixtures of any two or more of these refrigerants, or mixtures of any one of these refrigerants with other refrigerants. 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.

[0084] 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 reducer 203 reduces the pressure of the refrigerant, causing it to expand. The pressure reducer 203 is, for example, an electronic expansion valve capable of adjusting the throttling opening. 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 air and 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 an evaporator or radiator, exchanging heat between air and refrigerant, causing the refrigerant to evaporate or condense. The indoor heat exchanger 204 functions as a radiator during heating operation and as an evaporator during cooling operation.

[0085] 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.

[0086] 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 flow path is shown by the solid line. Thus, 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 the high-temperature and high-pressure gaseous refrigerant compressed by the multi-cylinder rotary compressor 1 is discharged from the multi-cylinder 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 that flows out of the indoor heat exchanger 204. At this time, the indoor air is heated. In addition, depending on the type of refrigerant, there are also refrigerants such as carbon dioxide refrigerant that do not condense when dissipating heat. When using a refrigerant that condenses when dissipating heat, the radiator is sometimes also called a condenser.

[0087] 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, which flows out of pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing from 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 the suction muffler 3 of multi-cylinder rotary compressor 1. Then, the low-pressure gaseous 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 into a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant is then discharged from the multi-cylinder rotary compressor 1. That is, when the refrigeration cycle unit 200 is in heating operation, the refrigerant... Figure 4 The loop repeats as shown by the solid arrow.

[0088] 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 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 the high-temperature and high-pressure gaseous refrigerant compressed by the multi-cylinder rotary compressor 1 is discharged from the multi-cylinder 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.

[0089] 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, which flows out of pressure reducer 203. The low-temperature, low-pressure gas-liquid two-phase refrigerant flowing from 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 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 muffler 3 of multi-cylinder rotary compressor 1. Then, the low-pressure gaseous 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, becoming a high-temperature and high-pressure gaseous refrigerant. This high-temperature and high-pressure gaseous refrigerant is then discharged from the multi-cylinder rotary compressor 1. That is, when the refrigeration cycle device 200 is operating in refrigeration mode, the refrigerant... Figure 4 The loop repeats as shown by the dashed arrow.

[0090] Figure 5 This is a bottom perspective view of the first partition plate 25A, the first cylinder 21A, and the first turbine 28A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 6 This is a longitudinal 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 Embodiment 1. Figure 7 This is a bottom 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 Embodiment 1. Figure 8 This is a bottom perspective view of the first partition plate 25A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 9 This is a top view showing the first partition plate 25A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 10 This is a bottom perspective 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 Embodiment 1. Figure 11 This is a longitudinal sectional 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 Embodiment 1. Figure 12 This 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 Embodiment 1. Figure 13 This is a bottom perspective view of the second partition plate 25B of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 14This is a bottom view showing the second partition plate 25B of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 15 This is a longitudinal sectional view of the first cylinder 21A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 16 This is a bottom view showing the first cylinder 21A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 17 This is a top view showing the first cylinder 21A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 18 This is a bottom view showing the first cylinder 21A and the first impeller 29A of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 19 yes Figure 18 A view of section AA. Figure 20 This is a longitudinal sectional view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 21 This is a top view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 22 This is a bottom view showing the second cylinder 21B of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 23 This 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. Figure 24 yes Figure 23 A view of the BB section. Additionally... Figure 6 and Figure 24 Shown upside down.

[0091] (Boosting mechanisms T1, T2)

[0092] Next, the pressurization mechanisms T1 and T2 involved in Embodiment 1 will be described. Figures 5-9 As shown, a first through hole 25Ab extending axially is formed in the first partition plate 25A. A first connecting shaft 27A is rotatably mounted in the first through hole 25Ab formed in the first partition plate 25A. Furthermore, 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 mounted at one end of the first connecting shaft 27A and disposed below the first cylinder block 21A. Furthermore, a first impeller 29A is mounted at the other end of the first connecting shaft 27A and disposed above the first partition plate 25A. Additionally, as... Figure 6 , Figures 15-19As shown, a first impeller 29A is disposed in a first connecting chamber 21Ab, which is part of a first suction flow path 52A. Refrigerant discharged into the space separated by a first partition plate 25A is then blown onto a first turbine 28A mounted at one end of a first connecting shaft 27A, causing the first turbine 28A to rotate. The first connecting shaft 27A is rotatably mounted in a first through hole 25Ab of the first partition plate 25A. 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 first suction chamber 57A. The first turbine 28A, the first connecting shaft 27A, and the first impeller 29A constitute the pressurization mechanism T1.

[0093] like Figures 10-14 As shown, a second through hole 25Bb extending axially is formed in the second partition plate 25B. A second connecting shaft 27B is rotatably mounted in the second through hole 25Bb formed in the second partition plate 25B. Furthermore, 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 mounted at one end of the second connecting shaft 27B and disposed above the second cylinder block 21B. Furthermore, a second impeller 29B is mounted at the other end of the second connecting shaft 27B and disposed below the second partition plate 25B. Additionally, as... Figure 11 , Figures 20-24 As shown, the second impeller 29B is disposed in the second connecting chamber 21Bb, which is part of the second suction flow path 52B. The refrigerant discharged into the space separated by the second partition plate 25B is then blown onto the second turbine 28B mounted at one end of the second connecting shaft 27B, causing the second turbine 28B to rotate. The second connecting shaft 27B is rotatably mounted in the second through hole 25Bb of the second partition plate 25B. 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 second turbine 28B, the second connecting shaft 27B, and the second impeller 29B constitute the pressurization mechanism T2.

[0094] like Figures 5-9As shown, a first recess 124A, recessed in the height direction, is provided on the surface of the first partition plate 25A opposite to the first cylinder block 21A. 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 first partition plate 25A. 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 on both the first cylinder block 21A and the first partition plate 25A. 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 to the first turbine 28A.

[0095] like Figures 10-14 As shown, a second recess 124B, recessed in the height direction, is provided on the surface of the second partition plate 25B opposite to the second cylinder 21B. 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 second partition plate 25B. 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 on both the second cylinder 21B and the second partition plate 25B. 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 to the second turbine 28B.

[0096] 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.

[0097] 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 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, enabling the first turbine 28A to rotate efficiently. Similarly, as Figures 10-14As 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 to the second turbine 28B, the density of the refrigerant guided from the second discharge passage 53B toward the second turbine 28B can be increased, enabling the second turbine 28B to rotate efficiently.

[0098] like Figure 6 As shown, the first discharge valve 26A includes: a first end portion 26Aa that is movable in a cantilever beam shape, closing or opening the first discharge flow path 53A at its end side; and a first base end portion 26Ab fixed to the first partition plate 25A at its base end side. The first discharge valve 26A is supported by a first valve pressing member 15A. The first valve pressing member 15A is a long plate-shaped member thicker than the first discharge valve 26A, which limits the movable range of the first discharge valve 26A while protecting 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 that is movable in a cantilever beam shape, closing or opening the second discharge flow path 53B at its end side; and a second base end portion 26Bb fixed to the second partition plate 25B at its base end side. The second discharge valve 26B is supported by a second valve pressing member 15B. The second valve pressing member 15B is a long plate-shaped member that is thicker than the second discharge valve 26B, which limits the movable range of the second discharge valve 26B while protecting 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.

[0099] As described above, the first discharge valve 26A is movable 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. The refrigerant discharged from the opened first discharge passage 53A is then blown towards the first turbine 28A, utilizing the pressure energy of the blown refrigerant to efficiently rotate the first turbine 28A. Similarly, the second discharge valve 26B is movable 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. The refrigerant discharged from the opened second discharge passage 53B is then blown towards the second turbine 28B, utilizing the pressure energy of the blown refrigerant to efficiently rotate the second turbine 28B.

[0100] Figure 25 This is a longitudinal sectional view showing the compression mechanism 20 of the multi-cylinder rotary compressor 1 according to Embodiment 1. (Example) Figure 25 As shown, a first exhaust muffler 23A is fixed to the side of the upper bearing 24A opposite to the first cylinder 21A. An exhaust port 23Aa is formed in the first exhaust muffler 23A. Furthermore, a second exhaust muffler 23B is fixed to the side of the lower bearing 24B opposite to the second cylinder 21B.

[0101] Conventionally, a known structure exists where, in a rotary compressor, a discharge muffler covering the discharge valve is provided to mitigate the noise generated by the refrigerant discharged from the discharge path, which is open due to the discharge valve opening. Noise reduction is achieved by ensuring that the refrigerant discharged from the discharge path collides with the discharge muffler instead of the sealed container. However, pressure loss occurs when the refrigerant from the discharge path collides with the discharge muffler. 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 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.

[0102] Furthermore, the first discharge muffler 23A and the second discharge muffler 23B can reduce noise by ensuring that the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B does not collide with the sealed container 10, but instead collides with the first discharge muffler 23A and the second discharge muffler 23B respectively. In this way, the first discharge muffler 23A and the second discharge muffler 23B can mitigate the discharge noise of the refrigerant discharged from the first discharge flow path 53A and the second discharge flow path 53B. Moreover, since 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, the pressure energy of the refrigerant can be used to efficiently rotate the first turbine 28A and the second turbine 28B.

[0103] like Figures 5-9 As shown, a first sealing member wall portion 25Aa is formed around the entire circumference of the outer periphery of the surface of the first partition plate 25A opposite to the first cylinder body 21A. Furthermore, as... Figures 10-14 As shown, a second sealing member wall portion 25Ba is formed around the entire circumference of the outer periphery of the surface of the second partition plate 25B opposite to the second cylinder body 21B. The entire circumference of the first sealing member wall portion 25Aa of the first partition plate 25A and the entire circumference of the second sealing member wall portion 25Ba of the second partition plate 25B are configured to abut against each other.

[0104] like Figure 25 As shown, a first outlet hole 151 is formed in the first partition plate 25A, extending from the side opposite to the first cylinder 21A towards the first cylinder 21A side and discharging refrigerant. A second outlet hole 152 is formed in the first cylinder 21A, communicating with the first outlet hole 151 and extending from the first partition plate 25A side towards the upper bearing 24A side. A third outlet hole 153 is formed in the upper bearing 24A, communicating with the second outlet hole 152 and extending from the first cylinder 21A side towards the side opposite to the first cylinder 21A side. Therefore, refrigerant discharged from the first discharge passage 53A and the second discharge passage 53B can be discharged from the first sealing member wall 25Aa and the second sealing member wall 25Ba via the first outlet hole 151, the second outlet hole 152, and the third outlet hole 153.

[0105] like Figure 25As 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 through the discharge port 23Aa into the interior of the sealed container 10. Furthermore, the refrigerant compressed by the second cylinder 21B and the second piston 22B flows into the first discharge muffler 23A via the first outlet port 151, the second outlet port 152, and the third outlet port 153. Then, the refrigerant flowing into the first discharge muffler 23A is released through the discharge port 23Aa into the interior of the sealed container 10.

[0106] The rotating shaft 40 is rotated by the rotating motor 30, and the first eccentric shaft portion 40A and the second eccentric shaft portion 40B of the rotating shaft 40 perform eccentric movements in the first cylinder chamber 55A and the second cylinder chamber 55B, respectively. Therefore, 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 preset 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 opened. As a result, the first discharge passage 53A and the second discharge passage 53B open, and the refrigerant is discharged from the first discharge passage 53A and the second discharge passage 53B to the outside of the first compression chamber 58A and the second compression chamber 58B, respectively. The refrigerant discharged to the outside of 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.

[0107] 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 flowing 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 multi-cylinder rotary compressor 1. Furthermore, by pressurizing the first suction chamber 57A and the second suction chamber 57B, the work done per revolution of the multi-cylinder rotary compressor 1 can be reduced.

[0108] 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 multi-cylinder rotary compressor 1 according to Embodiment 1, 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 booster mechanisms T1 and T2 provided in the first partition plate 25A and the second partition plate 25B for power recovery. Therefore, pressure loss as in the past is not generated, and power recovery is performed efficiently. Thus, by providing booster mechanisms T1 and T2 driven by refrigerant discharged from the compression mechanism 20 in the compression mechanism 20, pressure loss can be reduced.

[0109] Figure 26 This is a side view of the booster mechanisms T1 and T2 of the multi-cylinder rotary compressor 1 according to Embodiment 1. Figure 27 This is a single impeller diagram of the multi-cylinder rotary compressor 1 involved in Embodiment 1. Figure 28 This is a turbine unit diagram of the multi-cylinder rotary compressor 1 involved in Embodiment 1. Figure 29 This is a single-unit diagram of the connecting shaft of the multi-cylinder rotary compressor 1 according to Embodiment 1. Additionally, Figure 26 (a) shows a side view of the booster mechanism T1, and (b) shows a side view of the booster mechanism T2. Furthermore, Figure 27 and Figure 28 (a) represents a top view, (b) represents a side view, (c) represents a bottom view, and (d) represents a perspective view. Furthermore, Figure 29 (a) represents a top view, (b) represents a side view, and (c) represents a perspective view. Furthermore, Figure 27 The first impeller 29A is shown, but the second impeller 29B has the same shape and is therefore omitted from the illustration. Furthermore, Figure 28 The first turbine 28A is shown, but the second turbine 28B has the same shape and is therefore omitted from the illustration. Furthermore, Figure 29 The first connecting shaft 27A is shown, but the second connecting shaft 27B has the same shape, so it is omitted from the illustration.

[0110] like Figures 26-29As 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.

[0111] Thus, by having a first turbine blade set 28Aa and a second turbine blade set 28Ba, the first discharge valve 26A and the 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, the first suction chamber 57A and the second suction chamber 57B can be arranged radially outside the first impeller 29A and the second impeller 29B.

[0112] The compression mechanism 20 of the multi-cylinder rotary compressor 1 according to Embodiment 1 includes two cylinder chambers: a first cylinder chamber 55A and a second cylinder chamber 55B. These chambers share a first partition plate 25A and a second partition plate 25B constituting the first cylinder chamber 55A, and a first partition plate 25A and a second partition plate 25B constituting the second cylinder chamber 55B. That is, the multi-cylinder rotary compressor 1 according to Embodiment 1 is a dual-cylinder rotary compressor. Therefore, compared to a single-cylinder rotary compressor with one cylinder chamber, the multi-cylinder rotary compressor 1 according to Embodiment 1 can improve refrigerant compression capacity.

[0113] Furthermore, the multi-cylinder rotary compressor 1 involved in Embodiment 1 uses a dual rotary compressor, but it is not limited to this and may also be a three-rotary compressor, etc.

[0114] The multi-cylinder 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 rotary shaft 40 housed within the sealed container 10, rotating via the rotary motor 30, and having an eccentric shaft portion; a compression mechanism 20 housed within the sealed container 10, having a cylinder chamber for compressing refrigerant via 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 into the cylinder chamber from the outside of the sealed container 10; a piston fitted to an eccentric shaft; 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; a bearing fixed to one side of the cylinder body in the height direction, closing the side of the cylinder chamber; a sealing member fixed to the other side of the cylinder body in the height direction, closing the other side of the cylinder chamber, and forming a discharge flow path for discharging the compressed refrigerant to the outside of the compression chamber; and a discharge valve provided on the sealing member, closing the discharge flow path, and opening the discharge flow path when the refrigerant compressed in the compression chamber of the cylinder chamber reaches a preset pressure. The booster mechanisms T1 and T2 include: a connecting shaft rotatably supported on the sealing member; a turbine connected to one end of the connecting shaft, rotating through the refrigerant discharged from the open discharge flow path; and an impeller connected to the other end of the connecting shaft, rotating with the rotation of the turbine to promote the flow of refrigerant flowing in the intake flow path.

[0115] According to the multi-cylinder rotary compressor 1 of Embodiment 1, the booster mechanisms T1 and T2 include: a connecting shaft rotatably supported on a closed component; a turbine connected to one end of the connecting shaft, which rotates through refrigerant discharged from the open discharge path; and an impeller connected to the other end of the connecting shaft, which rotates with the rotation of the turbine to promote the flow of refrigerant flowing in the suction path. That is, since the compression mechanism 20 is equipped with booster mechanisms T1 and T2 driven by refrigerant discharged from the compression mechanism 20, pressure loss as in the past is not generated, and pressure loss can be reduced.

[0116] Furthermore, in the multi-cylinder 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; 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.

[0117] According to the multi-cylinder rotary compressor 1 of embodiment 1, since the turbine has a turbine blade assembly, the discharge valve can be arranged radially outside the turbine. Furthermore, since the impeller has an impeller blade assembly, the suction chamber can be arranged radially outside the impeller.

[0118] Furthermore, in the multi-cylinder rotary compressor 1 according to Embodiment 1, a sealing member wall is formed around the entire circumference of the outer periphery of the side of the sealing member opposite to the cylinder body. A first outlet hole 151 is formed in the sealing member that communicates with the discharge flow path and extends from the side opposite to the cylinder body towards the cylinder body side. A second outlet hole 152 is formed in the cylinder body that communicates with the first outlet hole 151 and extends from the sealing member side towards the bearing side. A third outlet hole 153 is formed in the bearing that communicates with the second outlet hole 152 and extends from the cylinder body side towards the side opposite to the cylinder body side.

[0119] According to Embodiment 1, the multi-cylinder rotary compressor 1 can discharge refrigerant from the discharge path through the wall of the closed component via the first discharge hole 151, the second discharge hole 152 and the third discharge hole 153.

[0120] Furthermore, in the multi-cylinder rotary compressor 1 according to Embodiment 1, a recess is provided on the side of the closed component opposite to the cylinder body 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.

[0121] According to the multi-cylinder rotary compressor 1 of embodiment 1, since the refrigerant discharged from the discharge flow path to the compressor room can be guided to the turbine along the guide surface, the turbine can be rotated efficiently.

[0122] Furthermore, in the multi-cylinder 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.

[0123] According to the multi-cylinder rotary compressor 1 of embodiment 1, when the refrigerant discharged from the discharge path to the compressor room is guided to the turbine along the guide surface, the density of the refrigerant guided from the discharge path to the turbine can be increased, and the turbine can be rotated efficiently.

[0124] Furthermore, in the multi-cylinder rotary compressor 1 according to Embodiment 1, the discharge valve has an end portion that can move in a cantilever beam shape and close or open the discharge flow path, and a base end portion fixed to the closing member. The turbine is provided on the side opposite to the base end portion of the discharge valve, with the end portion of the discharge valve as a reference.

[0125] According to the multi-cylinder rotary compressor 1 of Embodiment 1, since the discharge valve can move in a cantilever beam shape, 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 towards the turbine side. The pressure energy of the blown refrigerant can be used to make the turbine rotate efficiently.

[0126] Furthermore, in the multi-cylinder rotary compressor 1 according to Embodiment 1, a discharge muffler is provided on the side of the bearing opposite to the cylinder body, and a discharge hole 23Aa is formed in the discharge muffler.

[0127] According to Embodiment 1, the multi-cylinder rotary compressor 1 can mitigate the discharge noise of the refrigerant discharged from the discharge path by means of the discharge muffler. Furthermore, since it is configured such that the refrigerant discharged from the discharge path collides with the impeller before colliding with the discharge muffler, the pressure energy of the refrigerant can be used to make the impeller rotate efficiently.

[0128] Furthermore, the refrigeration cycle apparatus 200 according to Embodiment 1 includes: the multi-cylinder rotary compressor 1 described above; a radiator for dissipating heat from the refrigerant compressed by the multi-cylinder 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.

[0129] Furthermore, the refrigeration cycle device 200 according to Embodiment 1 uses any single refrigerant from R1234yf, R1234ze, R32, R290, or a mixture of any two or more of them, or a mixture of any one of them with other refrigerants, or a mixture containing R1132(E), or a mixture containing R1123.

[0130] According to the refrigeration cycle device 200 of Embodiment 1, the same effect as the multi-cylinder rotary compressor 1 described above can be obtained.

[0131] Explanation of reference numerals in the attached figures

[0132] 1... Multi-cylinder 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; 21Ab... First connecting chamber; 21B... Second cylinder; 21Bb... Second connecting chamber; 22A... First piston; 22B... Second piston; 23A... First discharge silencer; 23Aa... Discharge port; 23B... Second discharge silencer; 24A... 24B... Lower bearing; 25A... First partition plate; 25Aa... First sealing component wall; 25Ab... First through hole; 25B... Second partition plate; 25Ba... Second sealing component wall; 25Bb... Second through hole; 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; 29B...Second impeller; 29Ba...Second impeller blade 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; 53 B...Second discharge 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; 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 unit; 201...flow path switching valve; 202...outdoor heat exchanger; 203...pressure regulator; 204...indoor heat exchanger; T1...pressurization mechanism; T2...pressurization mechanism.

Claims

1. A multi-cylinder 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, housed within the sealed container, rotates via 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 that draws 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 seals one side of the cylinder chamber; A sealing component, fixed to the other side of the cylinder body in the height direction, seals off the other side of the cylinder chamber and forms a discharge path for discharging the compressed refrigerant to the outside of the compressor; and A discharge valve, disposed on the sealing component, closes the discharge path and opens the discharge path when the refrigerant compressed in the compression chamber of the cylinder reaches a preset pressure. The pressurization mechanism includes: The connecting shaft is rotatably supported on the enclosed component; The turbine, connected to one end of the connecting shaft, rotates through the refrigerant discharged from the open discharge passage; as well as The impeller, connected to the other end of the connecting shaft, rotates as the turbine rotates to facilitate the flow of refrigerant in the suction flow path.

2. The multi-cylinder 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 to flow out radially outward.

3. The multi-cylinder rotary compressor according to claim 2, characterized in that, A sealing member wall is formed around the entire circumference of the outer periphery of the surface of the sealing member opposite to the cylinder body. The sealing component has a first outlet hole that communicates with the discharge flow path and extends from the side opposite to the cylinder block side toward the cylinder block side. A second outlet hole is formed in the cylinder body, which communicates with the first outlet hole and extends from the side of the closed component toward the side of the bearing. The bearing has a third outlet hole that communicates with the second outlet hole and extends from the cylinder side toward a surface opposite to the cylinder.

4. The multi-cylinder rotary compressor according to any one of claims 1 to 3, characterized in that, The sealing component 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 to the turbine.

5. The multi-cylinder 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 multi-cylinder rotary compressor according to any one of claims 1 to 5, characterized in that, The discharge valve includes: The end portion is capable of moving in a cantilever beam shape, and can close or open the discharge flow path; and Fixed to the base end of the closed component, 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 multi-cylinder rotary compressor according to any one of claims 1 to 6, characterized in that, An exhaust muffler is provided on the side of the bearing opposite to the cylinder body. The exhaust muffler has an exhaust port.

8. A refrigeration cycle device, characterized in that, have: The multi-cylinder rotary compressor according to any one of claims 1 to 7; A radiator for dissipating heat from the refrigerant compressed by the multi-cylinder 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.

9. The refrigeration cycle device according to claim 8, characterized in that, Use any single refrigerant from R1234yf, R1234ze, R32, R290, or a mixture of any two or more of them, or a mixture of any one of them with other refrigerants, or a mixture containing R1132(E), or a mixture containing R1123.

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