Compressor and refrigeration cycle device

Abstract

A compressor and a refrigeration cycle device according to the present disclosure comprise: a cylinder that is secured to the inner circumferential side of a sealed vessel, with a radially extending vane groove formed in the inner circumferential surface of the cylinder; a circular piston that rotates eccentrically along the inner circumferential surface of the cylinder; a vane that is accommodated in the vane groove formed in the cylinder so as to be retractable in the radial direction, and that divides the space between the inner circumferential surface of the cylinder and the outer circumferential surface of the piston into a compression chamber and an intake chamber; a spring that is installed in the cylinder so as to expand and contract in the radial direction, and presses the vane against the piston from the outer circumferential side of the vane; and a first magnet and a second magnet that are provided to the vane. The vane has an inner vane and an outer vane disposed on the outer circumferential side of the inner vane. The first magnet and the second magnet are arranged so that the first magnet is disposed on the outer circumferential side of the inner vane, the second magnet is disposed on the inner circumferential side of the outer vane and opposite the first magnet, and the facing surfaces of the magnets are repelled by like magnetic poles thereof.

Description

Compressor and refrigeration cycle device

[0001] The present disclosure relates to a compressor equipped with vanes and a refrigeration cycle device.

[0002] Some compressors include a cylinder, a roller (hereinafter also referred to as a piston) housed in the cylinder so as to be eccentrically rotatable, and a vane housed in a vane groove provided in the cylinder so as to be reciprocable. Among such compressors, there is known one in which magnets are provided in the vane and in the vane groove facing the outer circumferential edge of the vane, and the magnets in the vane groove and the magnets in the vane are arranged so as to repel each other (see, for example, Patent Document 1).

[0003] JP 2007-64110 A

[0004] However, the rotary compressor disclosed in Patent Document 1 is configured so that the tip of the vane is pressed against the roller solely by the repulsive force between the magnets provided in the vane grooves and the magnets provided on the vanes. Therefore, while sufficient repulsive force is obtained when the two magnets are close to each other, sufficient repulsive force is not obtained when the two magnets are far from each other. As a result, the tip of the vane cannot sufficiently follow the eccentric rotation of the roller, and the tip of the vane may separate from the roller. When the tip of the vane separates from the roller, refrigerant leaks from the high-pressure side to the low-pressure side of the compression chamber, resulting in reduced compression performance.

[0005] The present disclosure has been made in light of the above-described problems, and aims to provide a compressor and a refrigeration cycle device that enable the tip ends of vanes to suitably follow the rollers (pistons).

[0006] a vane that is accommodated in the vane groove formed in the cylinder so as to be movable forward and backward in the radial direction, and that separates a space between the inner peripheral surface of the cylinder and the outer peripheral surface of the piston into a compression chamber and a suction chamber; a spring that is provided in the cylinder and expands and contracts in the radial direction, and that presses the vane against the piston from the outer peripheral side of the vane; and a first magnet and a second magnet that are provided in the vane, wherein the vane has an inner vane and an outer vane that is disposed on the outer peripheral side of the inner vane, and the first magnet and the second magnet are disposed such that the first magnet is disposed on the outer peripheral side of the inner vane and the second magnet is disposed on the inner peripheral side of the outer vane so as to face the first magnet, and the opposing surfaces have the same magnetic polarity and repel each other.

[0007] In addition, the refrigeration cycle device according to the present disclosure includes the above-described compressor, a radiator into which the refrigerant compressed by the compressor flows and into which the refrigerant dissipates heat, a pressure reducer that reduces the pressure of the refrigerant that flows out of the radiator, and an evaporator into which the refrigerant that flows out of the pressure reducer flows and into which the refrigerant evaporates.

[0008] The compressor and refrigeration cycle apparatus according to the present disclosure include a spring that presses the vane against the piston, and first and second magnets provided on the vane. The vane has an inner vane and an outer vane disposed on the outer periphery of the inner vane. The first magnet and the second magnet are disposed on the outer periphery of the outer vane so as to face the first magnet, and the second magnet is disposed on the inner periphery of the outer vane so as to face the first magnet, with the opposing surfaces of the magnets having the same magnetic polarity and repelling each other. This configuration allows the tip of the vane to suitably follow the piston by receiving both the biasing force of the spring and the magnetic repulsive force between the first magnet and the second magnet.

[0009] FIG. 1 is a longitudinal sectional view showing the overall configuration of a compressor according to embodiment 1. FIG. 2 is a sectional view of a compression mechanism according to embodiment 1. FIG. 3 is a diagram showing a refrigeration cycle device according to embodiment 1. FIG. 4 is a perspective view showing a state in which a first magnet is provided on an inner vane according to embodiment 1. FIG. 5 is a perspective view showing a state in which a second magnet is provided on an outer vane according to embodiment 1. FIG. 6 is a longitudinal sectional view of a vane according to embodiment 1. FIG. 7 is a schematic explanatory diagram showing the shape of a recessed portion of an inner vane according to embodiment 2. FIG. 8 is a schematic explanatory diagram showing the shape of a protruding portion of an outer vane according to embodiment 2. FIG. 9 is a schematic explanatory diagram showing the shape of a recessed portion of an inner vane according to embodiment 3. FIG. 10 is a schematic explanatory diagram showing the shape of a protruding portion of an outer vane according to embodiment 3. FIG. 11 is a schematic explanatory diagram showing the shape of a recessed portion of an inner vane according to embodiment 4. FIG. 12 is a schematic explanatory diagram showing the shape of a protruding portion of an outer vane according to embodiment 4.

[0010] First Embodiment. FIG. 1 is a longitudinal cross-sectional view showing the overall configuration of a compressor 1 according to the first embodiment. FIG. 2 is a cross-sectional view of a compression mechanism 20 according to the first embodiment. [Configuration of Compressor 1] As shown in FIG. 1, the compressor 1 according to the first embodiment is a rolling piston compressor as an example of a compressor according to the present disclosure. The compressor 1 includes a sealed container 10, a first suction pipe 2A, a second suction pipe 2B, a suction muffler 3, a compression mechanism 20, a rotating electric machine 30, a rotating shaft 40, and a discharge pipe 4. The sealed container 10 forms an outer shell of the compressor 1. The first suction pipe 2A and the second suction pipe 2B supply refrigerant into the sealed container 10. The suction muffler 3 is connected to the first suction pipe 2A and the second suction pipe 2B. The compression mechanism 20 is connected to the first suction pipe 2A and the second suction pipe 2B and compresses the refrigerant. The rotating electric machine 30 includes a rotor 31 and a stator 32, and drives the compression mechanism 20 via a rotating shaft 40. The rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30 and rotates together with the rotor 31. The discharge pipe 4 discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. The configuration of the compressor 1 will be described in detail below.

[0011] (Sealed casing 10) The sealed casing 10, which forms the outer casing of the compressor 1, houses the compression mechanism 20, the rotating electric machine 30, the rotating shaft 40, etc. The sealed casing 10 has a lid 11, a bottom 13, and a body 12. The lid 11 forms the outer casing of the upper part of the compressor 1. The bottom 13 forms the outer casing of the lower part of the compressor 1. The body 12 forms the outer casing of the middle part of the compressor 1, and the lid 11 is attached to the upper part of the body 12, and the bottom 13 is attached to the lower part of the body 12.

[0012] The lid 11 constituting the upper part of the sealed container 10 has, for example, a substantially bowl shape as shown in Fig. 1. A discharge pipe 4 that connects the inside and outside of the sealed container 10 is connected to the lid 11. Here, the outside of the sealed container 10 is, for example, a flow path in a refrigerant pipe that connects the compressor 1 and a flow path switching device 201 in a refrigerant circuit shown in Fig. 3, which will be described later.

[0013] As shown in Fig. 1 , the body portion 12 constituting the middle portion of the sealed container 10 has, for example, a substantially cylindrical shape. A first suction pipe 2A and a second suction pipe 2B for supplying refrigerant into the sealed container 10 are connected to the body portion 12. A stator 32 of a rotating electric machine 30 is attached to the inner circumferential surface of the body portion 12. A compression mechanism 20 is also attached to the inner circumferential surface of the body portion 12. In the first embodiment, a rolling piston type compression mechanism is used as the compression mechanism 20. In this case, the compression mechanism 20 is generally attached to the inner circumferential surface of the body portion 12 below the position where the stator 32 is attached.

[0014] The bottom 13 constituting the lower part of the sealed container 10 has, for example, a substantially bowl shape, as shown in Fig. 1. Refrigerating machine oil 6, which is a lubricating oil, is stored in the bottom 13. That is, the refrigerating machine oil 6 is stored inside the sealed container 10. This refrigerating machine oil 6 is supplied to the compression mechanism 20 and the like, and has the function of reducing friction at sliding parts of the compression mechanism 20 and the like.

[0015] (First suction pipe 2A and second suction pipe 2B) As described above, the first suction pipe 2A and the second suction pipe 2B are connected to the body 12 of the sealed container 10. One end of the first suction pipe 2A is connected to a first cylinder 21A of the compression mechanism 20, which will be described later. 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 a second cylinder 21B of the compression mechanism 20, which will be described later. The other end of the second suction pipe 2B is connected to the suction muffler 3.

[0016] (Suction muffler 3) The suction muffler 3 functions as a muffler that reduces refrigerant noise and other noise generated when the refrigerant flows into the compressor 1. The suction muffler 3 also functions as an accumulator that can store liquid refrigerant. As described above, the suction muffler 3 communicates with the first suction pipe 2A and the second suction pipe 2B.

[0017] (Compression mechanism 20) The compression mechanism 20 is connected to the rotating shaft 40 and compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40. In the first embodiment, the refrigerant that flows into the suction muffler 3 is supplied to the compression mechanism 20 via the first suction pipe 2A and the second suction pipe 2B. That is, the compression mechanism 20 draws in the external refrigerant via the first suction pipe 2A and the second suction pipe 2B and compresses this refrigerant. The refrigerant compressed by the compression mechanism 20 is released to the outside of the compression mechanism 20 within the sealed container 10.

[0018] In the first embodiment, the rotating shaft 40 includes a first eccentric shaft portion 40A and a second eccentric shaft portion 40B. As shown in Fig. 1 , the compression mechanism 20 includes a first cylinder 21A, a first piston 22A, an upper bearing 24A, a second cylinder 21B, a second piston 22B, a lower bearing 24B, a partition plate 25, and the like.

[0019] 2, the compression mechanism 20 includes a plate-shaped vane 50 provided in each cylinder (the first cylinder 21A and the second cylinder 21B shown in FIG. 1) and a spring 51. Each vane 50 is provided with two magnets (a first magnet 505 and a second magnet 506 shown in FIGS. 4 and 5, which will be described later).

[0020] Hereinafter, the first cylinder 21A and the second cylinder 21B may be referred to as cylinders 21 without distinction. The first piston 22A and the second piston 22B may be referred to as pistons 22 without distinction. The first eccentric shaft portion 40A and the second eccentric shaft portion 40B may be referred to as eccentric shaft portion 40X without distinction.

[0021] In addition, the vane 50 and spring 51 provided in the first cylinder 21A may be referred to as the first vane 50A and the first spring 51A, and the vane 50 and spring 51 provided in the second cylinder 21B may be referred to as the second vane 50B and the second spring 51B to distinguish them from the first vane 50A and the first spring 51A.

[0022] In the following description, structural parts of the first cylinder 21A are designated by the suffix A, and structural parts of the second cylinder 21B are designated by the suffix B. The first cylinder 21A and the second cylinder 21B are defined as having the same structure, and in Figure 2, the suffix A and B are omitted from the reference numerals of the structural parts of each cylinder 21 (for example, the intake passage 52, the discharge passage 53, and the spring hole 54).

[0023] 1 and 2 , the first cylinder 21A is cylindrical and defines a first cylinder chamber 55A. The first cylinder 21A is fixed to the inner periphery of the sealed container 10. The first cylinder 21A includes a first intake passage 52A through which refrigerant is drawn from the first intake pipe 2A and a first discharge passage 53A through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. The first intake pipe 2A is press-fitted into the first intake passage 52A on the outer periphery of the first cylinder 21A. The first piston 22A is annular and fitted to the first eccentric shaft portion 40A of the rotary shaft 40. The first piston 22A eccentrically rotates together with the first eccentric shaft portion 40A to compress the refrigerant.

[0024] The first cylinder 21A has a first vane groove 56A formed on its inner circumferential surface so as to extend radially. The first cylinder 21A also has a first spring 51A attached thereto and a first spring hole 54A formed therein to accommodate the first spring 51A.

[0025] The first vane 50A is located between the first intake passage 52A and the first discharge passage 53A and is disposed in a first vane groove 56A formed to extend radially of the first cylinder 21A. The first vane 50A divides the first cylinder chamber 55A, particularly the space between the inner circumferential surface of the first cylinder 21A and the outer circumferential surface of the first piston 22A, into a first intake chamber 57A and a first compression chamber 58A. The first intake chamber 57A communicates with the first intake passage 52A, and the first compression chamber 58A communicates with the first discharge passage 53A.

[0026] The first spring hole 54A is formed at the radially outer end of the first vane groove 56A of the first cylinder 21A, penetrates the first cylinder 21A in the axial direction (arrow Z direction), and communicates with the first vane groove 56A. The first spring 51A is housed in the first spring hole 54A and expands and contracts radially. The first spring 51A presses the first vane 50A attached to the tip of the first spring 51A against the outer peripheral surface of the first piston 22A. The first vane 50A is housed in the first vane groove 56A so as to be movable radially forward and backward. As will be described later, the first vane 50A is divided radially into two parts, an inner vane 501 and an outer vane 502 disposed radially outward of the inner vane 501.

[0027] The upper bearing 24A is disposed so as to abut against the upper end surface of the first cylinder 21A, and closes the first cylinder chamber 55A. The upper bearing 24A supports the rotary shaft 40 so as to be able to rotate freely.

[0028] The second cylinder 21B is cylindrical and disposed below the first cylinder 21A, forming a second cylinder chamber 55B. The second cylinder 21B is fixed to the inner periphery of the sealed container 10. The second cylinder 21B is formed with a second suction passage 52B through which refrigerant is drawn from the second suction pipe 2B and a second discharge passage 53B through which refrigerant is discharged to the discharge pipe 4 via the internal space of the sealed container 10. The second suction pipe 2B is press-fitted into the second suction passage 52B on the outer periphery of the second cylinder 21B. The second piston 22B is annular and fitted to the second eccentric shaft portion 40B of the rotary shaft 40, rotating eccentrically together with the second eccentric shaft portion 40B to compress the refrigerant.

[0029] The second cylinder 21B has a second vane groove 56B formed on its inner circumferential surface so as to extend radially. The second cylinder 21B also has a second spring hole 54B formed therein, and a second spring 51B is attached to the second cylinder 21B. The second spring 51B is accommodated in the second spring hole 54B.

[0030] The second vane 50B is located between the second intake passage 52B and the second discharge passage 53B and is disposed in a second vane groove 56B formed to extend radially of the second cylinder 21B. The second vane 50B divides the second cylinder chamber 55B, particularly the space between the inner peripheral surface of the second cylinder 21B and the outer peripheral surface of the second piston 22B, into a second intake chamber 57B and a second compression chamber 58B. The second intake chamber 57B communicates with the second intake passage 52B, and the second compression chamber 58B communicates with the second discharge passage 53B.

[0031] The second spring hole 54B is formed at the radially outer end of the second vane groove 56B of the second cylinder 21B, penetrates the second cylinder 21B in the axial direction (arrow Z direction), and communicates with the second vane groove 56B. The second spring 51B is housed in the second spring hole 54B and expands and contracts radially. The second spring 51B presses the second vane 50B attached to the tip of the second spring 51B against the outer peripheral surface of the second piston 22B. The second vane 50B is housed in the second vane groove 56B so as to be movable radially forward and backward. As will be described later, the second vane 50B is divided into two radially, and includes an inner vane 501 and an outer vane 502 disposed radially outward of the inner vane 501.

[0032] The lower bearing 24B is disposed so as to abut against the lower end surface of the second cylinder 21B, and closes the second cylinder chamber 55B. The lower bearing 24B supports the rotary shaft 40 so as to be able to rotate freely.

[0033] The partition plate 25 is disposed so as to abut against the lower end surface of the first cylinder 21A and the upper end surface of the second cylinder 21B, and closes the first cylinder chamber 55A and the second cylinder chamber 55B.

[0034] The first piston 22A rotates slidably within the first cylinder 21A. This first piston 22A is configured to be able to rotate eccentrically within the first cylinder 21A with respect to the center of rotation Ax of the rotary shaft 40. Hereinafter, rotation eccentrically with respect to the center of rotation Ax of the rotary shaft 40 will be referred to as "eccentric rotation." Furthermore, the second piston 22B rotates slidably within the second cylinder 21B. This second piston 22B is configured to be able to rotate eccentrically within the second cylinder 21B.

[0035] Furthermore, the first piston 22A is connected to the rotary shaft 40 so as to be able to rotate within the first cylinder 21A with a phase shift of 180 degrees relative to the rotational phase of the second piston 22B when it rotates within the second cylinder 21B. In other words, the second piston 22B is connected to the rotary shaft 40 so as to be able to rotate within the second cylinder 21B with a phase shift of −180 degrees relative to the rotational phase of the first piston 22A when it rotates within the first cylinder 21A.

[0036] The upper bearing 24A is provided with a valve (not shown) that discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A. When this valve is opened, the space formed by the first cylinder 21A and the first piston 22A can be connected to a first muffler 23A (described later). The lower bearing 24B is provided with a valve (not shown) that discharges the refrigerant compressed by the second cylinder 21B and the second piston 22B. When this valve is opened, the space formed by the second cylinder 21B and the second piston 22B can be connected to a second muffler 23B (described later).

[0037] The upper bearing 24A is provided with a first muffler 23A that discharges the refrigerant compressed by the first cylinder 21A and the first piston 22A. The first muffler 23A is provided with a refrigerant discharge portion (not shown). As a result, the refrigerant compressed by the first cylinder 21A and the first piston 22A is discharged into the first muffler 23A, and then released from the refrigerant discharge portion into the sealed container 10 and outside the compression mechanism 20.

[0038] A second muffler 23B is provided on the lower bearing 24B, from which the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged. The second muffler 23B is connected to the first muffler 23A via a refrigerant flow path (not shown). Thus, the refrigerant compressed by the second cylinder 21B and the second piston 22B is discharged into the second muffler 23B and then flows into the first muffler 23A via the refrigerant flow path (not shown). The refrigerant that flows into the first muffler 23A is then discharged from a refrigerant discharge port of the first muffler 23A into the interior of the sealed container 10 and outside the compression mechanism 20.

[0039] (Rotating Electric Machine 30 and Rotating Shaft 40) The rotating electric machine 30 has a rotor 31 that transmits its own rotation to the rotating shaft 40, and a stator 32 configured by mounting a multi-phase winding on a laminated core.

[0040] The rotating shaft 40 is connected to the rotating electric machine 30 and rotates by the power of the rotating electric machine 30. The rotating shaft 40 also transmits the power of the rotating electric machine 30 to the compression mechanism 20. In the first embodiment, the upper end side of the rotating shaft 40 is connected to the rotor 31 of the rotating electric machine 30. As a result, the rotating shaft 40 rotates together with the rotation of the rotor 31. The rotating shaft 40 shown in FIG. 1 rotates around a rotation center Ax that extends in the vertical direction (direction of arrow Z) on the page.

[0041] The lower end of the rotary shaft 40 is connected to the compression mechanism 20. More specifically, the lower end of the rotary shaft 40 is rotatably supported by an upper bearing 24A and a lower bearing 24B of the compression mechanism 20. The first piston 22A and the second piston 22B are connected to the rotary shaft 40 between a portion rotatably supported by the upper bearing 24A and a portion rotatably supported by the lower bearing 24B so that they can rotate eccentrically.

[0042] As a result, the rotating shaft 40 rotates in conjunction with the rotation of the rotor 31, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion. The refrigerant is compressed by the first cylinder 21A and the first piston 22A, and the refrigerant is compressed by the second cylinder 21B and the second piston 22B. In other words, the compression mechanism 20 compresses the refrigerant drawn in from the outside using the power of the rotating electric machine 30 transmitted by the rotating shaft 40.

[0043] (Discharge Pipe 4) The discharge pipe 4 is a pipe that discharges the refrigerant compressed by the compression mechanism 20 to the outside of the sealed container 10. In other words, the discharge pipe 4 is a pipe that discharges the high-temperature, high-pressure refrigerant inside the sealed container 10 to the outside of the sealed container 10.

[0044] (Centrifugal pump 45) The rotating shaft 40 has an oil supply hole 42 formed therein, which opens at one end 41 of the rotating shaft 40. The end 41 corresponds to a first end. In the first embodiment, the end 41 is the lower end of the rotating shaft 40. The oil supply hole 42 extends along the rotation center Ax of the rotating shaft 40. The rotating shaft 40 also has a first oil supply port 43 and a second oil supply port 44 formed therein. The first oil supply port 43 and the second oil supply port 44 serve as flow paths for supplying the refrigeration oil 6 sucked into the oil supply port 42 to the sliding parts of the compression mechanism 20. One end of each of the first oil supply port 43 and the second oil supply port 44 communicates with the oil supply hole 42. The other end of each 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 that faces the compression mechanism 20. In the first embodiment, the other end of first oil filler port 43 opens at a position facing upper bearing 24A of compression mechanism 20. The other end of second oil filler port 44 opens at a position facing lower bearing 24B of compression mechanism 20.

[0045] The centrifugal pump 45 is provided inside the oil supply hole 42 of the rotating shaft 40. The centrifugal pump 45 is formed by twisting a plate-like member. The centrifugal pump 45 is a fluid machine that uses centrifugal force generated by the rotational motion of the rotating shaft 40 to suck up refrigeration oil 6 as lubricant stored in the bottom 13 of the sealed container 10.

[0046] Refrigerant oil 6 pumped up into oil feed hole 42 by centrifugal pump 45 is supplied to the sliding parts of compression mechanism 20. Specifically, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through first oil feed port 43 and is supplied to the sliding part between upper bearing 24A of compression mechanism 20 and rotating shaft 40. Furthermore, a portion of refrigerant oil 6 pumped up into oil feed hole 42 passes through second oil feed port 44 and is supplied to the sliding part between lower bearing 24B of compression mechanism 20 and rotating shaft 40.

[0047] As the refrigeration oil 6, for example, mineral oil-based, alkylbenzene-based, polyalkylene glycol-based, polyvinyl ether-based, polyol ester-based lubricating oil or the like is used.

[0048] [Operation of the rotating electric machine 30] A current is supplied from a power source (not shown) to windings provided on the laminated core of the stator 32, generating a rotating magnetic field in the stator 32. This causes the rotating magnetic field of the stator 32 to act on the permanent magnets provided in the rotor 31, causing the rotor 31 to rotate. The rotation of the rotor 31 is transmitted to the first piston 22A and the second piston 22B via the rotating shaft 40, causing the first piston 22A and the second piston 22B to perform eccentric rotational motion.

[0049] [Refrigerant Flow] The eccentric rotation of the first piston 22A and the second piston 22B draws refrigerant into the compressor 1. Specifically, the eccentric rotation of the first piston 22A and the second piston 22B causes low-pressure refrigerant outside the compressor 1 to flow into the suction muffler 3. Then, of the low-pressure refrigerant that has flowed into the suction muffler 3, low-pressure gaseous refrigerant flows into the compression mechanism 20 of the compressor 1 via the first suction pipe 2A and the second suction pipe 2B. A portion of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the first cylinder 21A and the first piston 22A to become high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the first muffler 23A via the valve of the upper bearing 24A. The high-temperature, high-pressure gaseous refrigerant that has flowed into the first muffler 23A is discharged from a refrigerant discharge port (not shown) provided in the first muffler 23A into the space within the sealed container 10. Then, the high-temperature, high-pressure gaseous refrigerant that has been discharged into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., of the rotating electrical machine 30, and is discharged from the discharge pipe 4.

[0050] The remainder of the gaseous refrigerant that has flowed into the compression mechanism 20 is compressed by the second cylinder 21B and the second piston 22B to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant flows into the second muffler 23B through a valve in the lower bearing 24B. The high-temperature, high-pressure gaseous refrigerant that has flowed into the second muffler 23B passes through a refrigerant flow path (not shown) from the second muffler 23B and is sent to the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant sent to the first muffler 23A is then discharged into the space within the sealed container 10 from a refrigerant discharge port (not shown) provided in the first muffler 23A. The high-temperature, high-pressure gaseous refrigerant discharged into the space within the sealed container 10 moves to the upper part of the space within the sealed container 10 through gaps, etc., between the rotating electrical machine 30 and the like, and is discharged from the discharge pipe 4.

[0051] Furthermore, refrigeration oil 6 stored in bottom 13 within sealed container 10 is sucked up from the lower end of oil feed hole 42 by centrifugal pump 45, which rotates together with rotating shaft 40. Refrigeration oil 6 sucked up from the lower end of oil feed hole 42 flows as lubricating oil between upper bearing 24A and rotating shaft 40 from first oil feed port 43. Refrigeration oil 6 also flows from second oil feed port 44 between lower bearing 24B and rotating shaft 40. By refrigeration oil 6 flowing between these, rotating shaft 40 can smoothly transmit rotational driving force to first piston 22A and second piston 22B.

[0052] Furthermore, a portion of the refrigeration oil 6 that flows from the first oil supply port 43 between the upper bearing 24A and the rotating shaft 40 flows between the upper bearing 24A and the upper surface of the first piston 22A. A portion of the refrigeration oil 6 that flows from the second oil supply port 44 between the lower bearing 24B and the rotating shaft 40 flows between the lower bearing 24B and the lower surface of the second piston 22B. The refrigeration oil 6 is used to smoothly rotate the first piston 22A and the second piston 22B, but a portion of the refrigeration oil 6 is compressed together with the low-pressure gaseous refrigerant and is discharged in a state contained in the high-temperature, high-pressure gaseous refrigerant.

[0053] 3 is a diagram showing the refrigeration cycle apparatus 200 according to Embodiment 1. The refrigeration cycle apparatus 200 includes the compressor 1 according to Embodiment 1, a radiator in which the refrigerant compressed by the compressor 1 radiates heat, a pressure reducer 203 such as an electric expansion valve that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator in which the refrigerant flowing out from the pressure reducer 203 evaporates.

[0054] The refrigeration cycle apparatus 200 is used for various purposes, such as a hot water supply apparatus and a freezing apparatus. FIG. 3 shows an example in which the refrigeration cycle apparatus 200 is used as an air conditioner. Therefore, the refrigeration cycle apparatus 200 shown in FIG. 3 includes an indoor heat exchanger 204 that functions as a radiator during heating operation and an outdoor heat exchanger 202 that functions as an evaporator during heating operation. The refrigeration cycle apparatus 200 shown in FIG. 3 is also capable of cooling operation. Therefore, the refrigeration cycle apparatus 200 includes a flow path switching device 201 that switches the flow path of the refrigerant. The flow path switching device 201 is, for example, a four-way valve, and switches the heat exchanger connected to the discharge pipe 4, which is the refrigerant discharge port of the compressor 1, and the heat exchanger connected to the suction muffler 3, which is the refrigerant intake port of the compressor 1. During cooling operation, the indoor heat exchanger 204 functions as an evaporator, and the outdoor heat exchanger 202 functions as a radiator. The flow path switching device 201 may be configured as, for example, a two-way valve or a three-way valve.

[0055] When the refrigeration cycle apparatus 200 is used as an air conditioner, for example, the indoor heat exchanger 204 is mounted in an indoor device (i.e., an indoor unit), and the flow path switching device 201, the outdoor heat exchanger 202, and the pressure reducer 203 are mounted in an outdoor device (i.e., an outdoor unit).

[0056] Examples of the refrigerant include a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential (GWP). Examples of the refrigerant include a single refrigerant such as R1234yf, R1234ze, R32, or R290, a mixed refrigerant of two or more of these, or a mixed refrigerant of one or more of these with other refrigerants. Examples of the refrigerant include a mixed refrigerant containing R1132(E) or a mixed refrigerant containing R1123. Examples of the refrigerant include a mixed refrigerant of two or more of R516A, R410A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0057] When the refrigeration cycle apparatus 200 performs heating operation, the flow path switching device 201 switches to the flow path shown by the solid line in FIG. 3 . As a result, the discharge pipe 4 of the compressor 1 is connected to the indoor heat exchanger 204, and the suction muffler 3 of the compressor 1 is connected to the outdoor heat exchanger 202. That is, the indoor heat exchanger 204 functions as a radiator, and the outdoor heat exchanger 202 functions as an evaporator. In this state, when high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the indoor heat exchanger 204. The high-temperature, high-pressure gaseous refrigerant that has flowed into the indoor heat exchanger 204 condenses while releasing heat to the indoor air, and then flows out of the indoor heat exchanger 204 as high-pressure liquid refrigerant. At this time, the indoor air is heated. Note that some types of refrigerants, such as carbon dioxide refrigerant, do not condense when radiating heat. When a refrigerant that condenses when radiating heat is used, the radiator may also be called a condenser.

[0058] The high-pressure liquid refrigerant that flows out of the indoor heat exchanger 204 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flows into the pressure reducer 203 is reduced in pressure by the pressure reducer 203 to become a low-temperature, low-pressure two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the outdoor heat exchanger 202. The low-temperature, low-pressure two-phase gas-liquid refrigerant that flows into the outdoor heat exchanger 202 absorbs heat from the outdoor air in the outdoor heat exchanger 202 and evaporates, and flows out of the outdoor heat exchanger 202 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant that flows out of the outdoor heat exchanger 202 is drawn into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerant drawn into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs heating operation, the refrigerant circulates as shown by the solid arrows in FIG. 3 .

[0059] When the refrigeration cycle apparatus 200 performs cooling operation, the flow path switching device 201 switches to the flow path shown by the dashed line in FIG. 3 . As a result, the discharge pipe 4 of the compressor 1 is connected to the outdoor heat exchanger 202, and the suction muffler 3 of the compressor 1 is connected to the indoor heat exchanger 204. That is, the outdoor heat exchanger 202 functions as a radiator, and the indoor heat exchanger 204 functions as an evaporator. In this state, when high-temperature, high-pressure gaseous refrigerant compressed by the compressor 1 is discharged from the compressor 1, this high-temperature, high-pressure gaseous refrigerant flows into the outdoor heat exchanger 202. The high-temperature, high-pressure gaseous refrigerant that has flowed into the outdoor heat exchanger 202 condenses while releasing heat to the outdoor air, and then flows out of the outdoor heat exchanger 202 as a high-pressure liquid refrigerant.

[0060] The high-pressure liquid refrigerant flowing out of the outdoor heat exchanger 202 flows into the pressure reducer 203. The high-pressure liquid refrigerant that flowed into the pressure reducer 203 is then decompressed by the pressure reducer 203 to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant, which flows out of the pressure reducer 203. The low-temperature, low-pressure, two-phase gas-liquid refrigerant that flows out of the pressure reducer 203 flows into the indoor heat exchanger 204. The low-temperature, low-pressure, two-phase gas-liquid refrigerant that flowed into the indoor heat exchanger 204 absorbs heat from the indoor air in the indoor heat exchanger 204 and evaporates, flowing out of the indoor heat exchanger 204 as a low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant. At this time, the indoor air is cooled. The low-pressure gaseous refrigerant or a two-phase gas-liquid refrigerant that flows out of the indoor heat exchanger 204 is drawn into the suction muffler 3 of the compressor 1. Then, the low-pressure gaseous refrigerant among the refrigerants drawn into the suction muffler 3 of the compressor 1 is compressed by the compression mechanism 20 of the compressor 1 to become a high-temperature, high-pressure gaseous refrigerant. This high-temperature, high-pressure gaseous refrigerant is discharged again from the compressor 1. That is, when the refrigeration cycle apparatus 200 performs cooling operation, the refrigerant circulates as shown by the dashed arrows in FIG. 3 .

[0061] Figure 4 is a perspective view showing a state in which a first magnet 505 is provided on an inner vane 501 according to embodiment 1. Figure 5 is a perspective view showing a state in which a second magnet 506 is provided on an outer vane 502 according to embodiment 1. Figure 6 is a vertical cross-sectional view of vane 50 according to embodiment 1. The configuration of vane 50 will be described in detail below with reference to Figures 2 and 4 to 6.

[0062] 2 and 6, the vane 50 is configured as a substantially rectangular plate-like member extending in the radial direction, divided into two halves in the radial direction. The vane 50 has a concave / convex portion at the boundary between the inner vane 501 and the outer vane 502, which allows the inner vane 501 and the outer vane 502 to engage with each other. The inner vane 501 and the outer vane 502 are configured to engage with each other through the concave / convex portion, changing the distance between them at the boundary, thereby expanding or contracting the radial length of the vane 50. The configuration of the inner vane 501 and the outer vane 502 will be described below.

[0063] As shown in FIGS. 2, 4, and 6, the inner vane 501 has a rectangular plate shape extending radially and axially (in the direction of the arrow Z). An inner peripheral tip 507 of the inner vane 501 contacts the outer peripheral surface of the piston 22, and an outer peripheral end face 501o of the inner vane 501 faces the outer vane 502. As shown in FIGS. 4 and 6, a recess 503 extending toward the tip 507 is formed in the outer peripheral end face 501o of the inner vane 501. In FIGS. 4 and 6, the recess 503 is formed in the central portion of the outer peripheral end face 501o of the inner vane 501 in the axial direction (in the direction of the arrow Z). A first magnet 505 is fixed to a bottom 503w1 of the recess 503. Note that in FIG. 4, the recess 503 formed in the inner vane 501 is represented by a solid line to facilitate explanation of the recess 503.

[0064] As shown in Figures 2, 5, and 6, outer vane 502 has a base portion 509 having a rectangular plate shape extending radially and axially (in the direction of arrow Z). An inner peripheral end face 502i of outer vane 502 (inner peripheral end face 502i of base portion 509) faces outer peripheral end face 501o of inner vane 501, and outer peripheral end face 502o of outer vane 502 faces spring 51. As shown in Figures 5 and 6, inner peripheral end face 502i of base portion 509 is formed with a protrusion 504 that is disposed within recess 503 of inner vane 501. In Figures 5 and 6, protrusion 504 is formed in the center of inner peripheral end face 502i of outer vane 502 in the axial direction (in the direction of arrow Z). A second magnet 506 is fixed to the tip of protrusion 504.

[0065] Furthermore, a spring disposition hole 508 in which spring 51 is disposed is formed in outer peripheral end face 502o of outer vane 502 (i.e., the outer peripheral end face of base portion 509). Spring 51 is attached to the bottom of spring disposition hole 508. In Figures 5 and 6, spring disposition hole 508 is formed in the center of outer peripheral end face 502o of outer vane 502 in the axial direction (direction of arrow Z). In other words, spring 51 presses convex portion 504 radially inward from the radially outer side via base portion 509.

[0066] The inner vane 501 and the outer vane 502 are connected to each other by a recess 503 and a protrusion 504 that slidably fit together. Hereinafter, the recess 503 and the protrusion 504 provided on the inner vane 501 and the outer vane 502 may be referred to as a connecting portion 50c. In Figures 4 and 5, the recess 503 and the protrusion 504 are formed so that the cross section perpendicular to the radial direction has a circular shape. The recess 503 can be formed, for example, by a machining drill, and the protrusion 504 can be formed, for example, by a lathe while rotating a workpiece.

[0067] The configurations of inner vane 501 and outer vane 502 are not limited to those described above. It is sufficient that a recess is formed on one of outer peripheral end face 501o of inner vane 501 and inner peripheral end face 502i of outer vane 502, and a protrusion that slides radially within the recess is formed on the other. For example, inner vane 501 may be provided with a protrusion, and outer vane 502 may be provided with a recess.

[0068] 6 , a protrusion 504 of an outer vane 502 fits into a recess 503 of an inner vane 501, and the protrusion 504 slides radially within the recess 503 during operation of the compressor 1. Specifically, the protrusion 504 is in sliding contact with an inner portion 503w2 of the recess 503. The inner vane 501 and the outer vane 502 are configured so that the length L1 of the inner vane 501 in the advancing / retracting direction is longer than the length L2 of the base portion 509 of the outer vane 502 in the advancing / retracting direction. In other words, the length from the inner peripheral end face 501i to the outer peripheral end face 501o of the inner vane 501 is longer than the length from the inner peripheral end face 502i to the outer peripheral end face 502o of the outer vane 502, excluding the protrusion 504.

[0069] In this way, of the inner vane 501 and outer vane 502 that make up vane 50, the inner vane 501 that comes into contact with piston 22, i.e., the side that enters cylinder chamber 55 (see FIG. 2), is made radially longer than the base portion 509 of the outer vane 502, so that the entire inner vane 501 does not enter cylinder chamber 55. As a result, as shown in FIG. 2, the outer peripheral end face 501o (see FIG. 6) of the inner vane 501 is always positioned within the vane groove 56 during operation of the compressor 1, preventing the peripheral edge of the outer peripheral end face 501o from getting caught on the inner peripheral surface of the cylinder 21.

[0070] As shown in Figures 2 and 4 to 6, the first magnet 505 at the bottom 503w1 of the recess 503 and the second magnet 506 at the tip of the protrusion 504 are arranged so that their opposing surfaces have the same magnetic poles and repel each other.

[0071] The locations of the first magnet 505 on the inner vane 501 and the second magnet 506 on the outer vane 502 are not limited to the above locations. The first magnet 505 and the second magnet 506 may be arranged such that the first magnet 505 is disposed on the outer periphery of the inner vane 501 and the second magnet 506 is disposed on the inner periphery of the outer vane 502 so as to face the first magnet 505, and the opposing surfaces of the first magnet 505 and the second magnet 506 have the same magnetic polarity and repel each other. For example, the first magnet 505 may be arranged on the outer periphery end face 501o of the inner vane 501 except for the recessed portion 503, and the second magnet 506 may be arranged on the inner periphery end face 502i of the outer vane 502 except for the protruding portion 504 so as to face the first magnet 505.

[0072] The operation of vane 50 will be described with reference to Figures 1 and 2 and 4 to 6. Vane 50 is divided into an inner vane 501 and an outer vane 502, with a first magnet 505 and a second magnet 506 interposed between them, and outer vane 502 is biased inward by a spring 51.

[0073] That is, outer vane 502 is biased toward piston 22 by spring 51, and therefore outer vane 502 presses inner vane 501 against piston 22 by the magnetic repulsive force between first magnet 505 at bottom 503w1 of recess 503 and second magnet 506 at the tip of protrusion 504. Here, the spring force maintains the separation distance between first magnet 505 and second magnet 506 within a certain distance that is shorter than the maximum distance in the conventional case (i.e., the maximum movement distance of vane 50), so the magnetic repulsive force acts effectively.

[0074] Therefore, the tip 507 of the inner vane 501 is subjected to both the spring force of the spring 51 and the magnetic repulsive force between the first magnet 505 at the bottom 503w1 of the recess 503 and the second magnet 506 at the tip of the protrusion 504, and follows the eccentrically rotating piston 22.

[0075] Generally, in a rolling piston type compression mechanism 20, a decrease in compression performance can occur due to separation between the tip 507 of the vane 50 and the piston 22. On the other hand, in the compression mechanism 20 of the present disclosure, the configuration combining the spring force and the magnetic repulsive force as described above allows the tip 507 of the vane 50 to suitably follow the eccentrically rotating piston 22. As a result, a decrease in compression performance can be suppressed.

[0076] In the conventional configuration, magnets are provided on the vane 50 and on the inner surface of the vane groove 56 facing the outer circumferential edge of the vane 50, and the vane 50 is brought into contact with the piston 22 by the force of the magnets alone. Here, the magnitude of the repulsive force acting between the magnets is inversely proportional to the square of the distance between the magnets. Therefore, in the conventional configuration, when the piston 22 is farthest from the vane groove 56 and the vane 50 is most exposed from the vane groove 56 to the interior of the cylinder 21 (see FIG. 2), that is, when the distance between the magnets is greatest, the magnetic force acting on the vane 50 becomes extremely weak. Therefore, it is conceivable that the tip 507 of the vane 50 will separate from the piston 22.

[0077] On the other hand, in the configuration of the present disclosure, the vane 50 is divided and a magnet is placed between the two to suppress attenuation of the repulsive force due to distance, and by using a spring 51 together with such a vane 50 configuration, tracking ability in the sliding direction can be ensured.

[0078] It is desirable that the inner vane 501 and the outer vane 502 are made of a non-magnetic material to prevent the magnetic properties of the first magnet 505 at the bottom 503w1 of the recess 503 and the second magnet 506 at the tip of the protrusion 504 from affecting surrounding metal parts and impeding sliding.

[0079] As described above, the compressor 1 according to the first embodiment includes a cylinder 21 fixed to the inner periphery of the sealed container 10 and having a radially extending vane groove 56 formed on its inner periphery, and an annular piston 22 that rotates eccentrically along the inner periphery of the cylinder 21. The compressor 1 also includes a vane 50 that is accommodated in the vane groove 56 formed in the cylinder 21 so as to be movable forward and backward in the radial direction and that divides the space between the inner periphery of the cylinder 21 and the outer periphery of the piston 22 into a compression chamber 58 and a suction chamber 57. The compressor 1 also includes a spring 51 that is provided in the cylinder 21, expands and contracts in the radial direction, and presses the vane 50 against the piston 22 from the outer periphery of the vane 50, and a first magnet 505 and a second magnet 506 that are provided on the vane 50. The vane 50 includes an inner vane 501 and an outer vane 502 that is disposed on the outer periphery of the inner vane 501. The first magnet 505 and the second magnet 506 are arranged such that the first magnet 505 is positioned on the outer periphery of the inner vane 501, and the second magnet 506 is positioned on the inner periphery of the outer vane 502 so as to face the first magnet 505, and the opposing surfaces have the same magnetic poles and repel each other.

[0080] By having such a configuration, the tip 507 of the vane 50 can suitably follow the piston 22 by receiving both the force of the spring 51 and the magnetic repulsive force between the first magnet 505 and the second magnet 506.

[0081] In addition, the inner vane 501 and the outer vane 502 have a recess 503 formed on one of the outer peripheral end face 501o of the inner vane 501 and the inner peripheral end face 502i of the outer vane 502, and a protrusion 504 that slides radially within the recess 503 formed on the other, and are connected to each other by the recess 503 and the protrusion 504.

[0082] As a result, even if vane 50 is configured to be divided into inner vane 501 and outer vane 502 and the distance between inner vane 501 and outer vane 502 is changed by first magnet 505 and second magnet 506, tilting of one vane relative to the other in the circumferential direction is restricted. This improves the ability of tip end 507 of vane 50 to follow piston 22.

[0083] Further, recess 503 is formed in outer peripheral end face 501o of inner vane 501, protrusion 504 is formed in inner peripheral end face 502i of outer vane 502, and spring arrangement hole 508 for arranging spring 51 is formed in outer peripheral end face 502o of outer vane 502. Inner vane 501 and outer vane 502 are configured so that the length from inner peripheral end face 501i of inner vane 501 to the part of outer peripheral end face 501o other than recess 503 (length L1 of inner vane 501 in the forward / backward direction) is longer than the length from the part of inner peripheral end face 502i of outer vane 502 other than protrusion 504 to the part of outer peripheral end face 502o other than spring arrangement hole 508 (length L2 of base portion 509 of outer vane 502 in the forward / backward direction).

[0084] In this way, when the length L1 of the inner vane 501 in the forward / backward direction is longer than the length L2 of the base portion 509 of the outer vane 502 in the forward / backward direction, the peripheral portion of the outer end face 501o of the inner vane 501 can be prevented from getting caught on the inner surface of the cylinder 21, compared to when the length L1 is shorter than the length L2 of the base portion 509 in the forward / backward direction.

[0085] The first magnet 505 and the second magnet 506 are disposed at the bottom 503 w 1 of the recess 503 and the tip of the protrusion 504 .

[0086] As a result, even if the distance between first magnet 505 and second magnet 506 changes, the faces of the same magnetic poles can remain facing each other, and the magnetic repulsive force is effectively converted into radial movement of inner vane 501 and outer vane 502. As a result, the ability of tip end 507 of vane 50 to follow piston 22 is improved.

[0087] The refrigerant used may be, for example, a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixed refrigerant of two or more of these, a mixed refrigerant of one or more of these with another refrigerant, a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123.

[0088] The refrigeration cycle apparatus 200 according to the present disclosure includes the compressor 1 described above and a radiator (e.g., indoor heat exchanger 204) into which the refrigerant compressed by the compressor 1 flows and into which the refrigerant dissipates heat. The refrigeration cycle apparatus 200 also includes a pressure reducer 203 that reduces the pressure of the refrigerant flowing out from the radiator, and an evaporator (e.g., outdoor heat exchanger 202) into which the refrigerant flowing out from the pressure reducer 203 flows and into which the refrigerant evaporates.

[0089] As a result, the performance of the refrigeration cycle device 200 can be improved by using the compressor 1 described above.

[0090] Embodiment 2. Figure 7 is a schematic diagram illustrating the shape of a recess 503 of an inner vane 501 according to Embodiment 2. Figure 8 is a schematic diagram illustrating the shape of a protrusion 504 of an outer vane 502 according to Embodiment 2. Embodiment 2 will be described with reference to Figures 7 and 8. In Embodiment 2, items that are not specifically described are the same as in Embodiment 1, and the same functions and configurations as in Embodiment 1 will be described using the same reference numerals.

[0091] Vane 50 in the second embodiment has a rotation suppression mechanism that suppresses rotation between inner vane 501 and outer vane 502. The rotation suppression mechanism is provided at connecting portion 50c between inner vane 501 and outer vane 502, which are slidably fitted together, and in the second embodiment, the shape of connecting portion 50c is different from that in the first embodiment.

[0092] Because the convex portion 504 of the outer vane 502 slides within the concave portion 503 of the inner vane 501, it is possible that the inner vane 501 may tilt about the axis of the convex portion 504 of the outer vane 502. Therefore, in the second embodiment, rotation is suppressed by the shape of the connecting portion 50c between the inner vane 501 and the outer vane 502, and contact between the vane 50 and the inner surface of the vane groove 56 is suppressed.

[0093] 8, the convex portion 504 has a cylindrical portion 80a that extends radially and has a circular cross section perpendicular to the radial direction, and a key portion 81a that is formed to protrude from the outer circumferential surface of the cylindrical portion 80a and extends radially. As shown in FIGS. 7 and 8, the concave portion 503 has a circular hole portion 70a that accommodates the cylindrical portion 80a, and a key groove portion 71a that accommodates the key portion 81a.

[0094] In this way, by accommodating the key portion 81a in the key groove portion 71a, the convex portion 504 can be prevented from rotating relative to the concave portion 503, and sliding within the vane groove 56 can be achieved in the same way as when the vane 50 is made of a single plate.

[0095] The key portions 81a and the key grooves 71a are formed so that the cross section perpendicular to the radial direction has a crescent shape. In other words, the key portions 81a and the key grooves 71a are formed so that the outer ring shape in the cross section perpendicular to the radial direction has an arc shape. Note that the shapes of the key portions 81a and the key grooves 71a are not limited to the above shapes and may be any shape as long as the convex portion 504 can be prevented from rotating relative to the concave portion 503.

[0096] It is preferable to provide the key grooves 71a in the recessed portions 503 and the keys 81a in the protruding portions 504 on the upper or lower side rather than on the side, in order to avoid the occurrence of portions in the vane 50 where the wall thickness in the lateral direction (i.e., the circumferential direction) is extremely thin.

[0097] Instead of providing the outer vane 502 with the convex portion 504 and the inner vane 501 with the concave portion 503, the inner vane 501 may be provided with the convex portion and the outer vane 502 may be provided with the concave portion.

[0098] Embodiment 3. Figure 9 is a schematic explanatory diagram showing the shape of a recess 503 of an inner vane 501 according to Embodiment 3. Figure 10 is a schematic explanatory diagram showing the shape of a protrusion 504 of an outer vane 502 according to Embodiment 3. Embodiment 3 will be described with reference to Figures 9 and 10. In Embodiment 3, items that are not specifically described are the same as in Embodiment 1, and the same functions and configurations as in Embodiment 1 will be described using the same reference numerals.

[0099] Similar to the second embodiment, the vane 50 of the third embodiment has a rotation suppression mechanism that suppresses rotation between the inner vane 501 and the outer vane 502. In the third embodiment, the shapes of the key portion 81b and the key groove portion 71b that function as the rotation suppression mechanism are different from those in the second embodiment.

[0100] 10, the convex portion 504 has a cylindrical portion 80a that extends radially and has a circular cross section perpendicular to the radial direction, and a key portion 81b that is formed to protrude from the outer circumferential surface of the cylindrical portion 80a and extends radially. As shown in FIGS. 9 and 10, the concave portion 503 has a circular hole portion 70a that accommodates the cylindrical portion 80a, and a key groove portion 71b that accommodates the key portion 81b.

[0101] The key portions 81b and the key grooves 71b are formed so that the cross section perpendicular to the radial direction has a rectangular shape. In other words, the outer ring contour of the key portions 81b and the key grooves 71b in the cross section perpendicular to the radial direction is formed by a plurality of straight lines. In this case, the key portions 81b and the key grooves 71b can be easily formed using, for example, an end mill.

[0102] Instead of providing the outer vane 502 with the convex portion 504 and the inner vane 501 with the concave portion 503, the inner vane 501 may be provided with the convex portion and the outer vane 502 may be provided with the concave portion.

[0103] Fourth Embodiment Figure 11 is a schematic diagram illustrating the shape of a recess 503 of an inner vane 501 according to a fourth embodiment. Figure 12 is a schematic diagram illustrating the shape of a protrusion 504 of an outer vane 502 according to the fourth embodiment. The fourth embodiment will be described with reference to Figures 11 and 12. In the fourth embodiment, items that are not specifically described are the same as those in the first embodiment, and the same functions and configurations as those in the first embodiment will be described using the same reference numerals.

[0104] Similarly to the second and third embodiments, the vane 50 of the fourth embodiment has a rotation suppression mechanism that suppresses rotation between the inner vane 501 and the outer vane 502. In the fourth embodiment, the shape of the connecting portion 50c (the recessed portion 503 and the protruding portion 504) that functions as the rotation suppression mechanism is different from that in the second and third embodiments.

[0105] In the fourth embodiment, the convex portion 504 and the concave portion 503 have a rectangular cross section perpendicular to the radial direction. That is, the convex portion 504 and the concave portion 503 have a cross section with corners 81c and 71c. In this case, the corners 81c and 71c of the convex portion 504 and the concave portion 503 function as a rotation suppression return mechanism. In the example shown in FIGS. 11 and 12, the corners 81c and 71c of the convex portion 504 and the concave portion 503 are curved.

[0106] In the fourth embodiment, the corners 81c, 71c function as a rotation suppression return mechanism, eliminating the need for the keys 81a, 81b and key grooves 71a, 71b used in the second and third embodiments. This allows the cross-sectional shapes of the convex portion 504 and the concave portion 503 to be simplified, facilitating fabrication. The convex portion 504 and the concave portion 503 shown in Figures 11 and 12 have a cross-sectional shape perpendicular to the radial direction that is rectangular with the corners 81c, 71c curved, as described above. Such convex portion 504 and concave portion 503 can be easily formed, for example, by an end mill.

[0107] Instead of providing the outer vane 502 with the convex portion 504 and the inner vane 501 with the concave portion 503, the inner vane 501 may be provided with the convex portion and the outer vane 502 may be provided with the concave portion.

[0108] REFRIGERATION SYSTEM, 1 Compressor, 2A First suction pipe, 2B Second suction pipe, 3 Suction muffler, 4 Discharge piping, 6 Refrigerating machine oil, 10 Sealed container, 11 Lid, 12 Body, 13 Bottom, 20 Compression mechanism, 21 Cylinder, 21A First cylinder, 21B Second cylinder, 22 Piston, 22A First piston, 22B Second piston, 23A First muffler, 23B Second muffler, 24A Upper bearing, 24B Lower bearing, 25 Partition plate, 30 Rotating electric machine, 31 Rotor, 32 Stator, 40 Rotating shaft, 40A First eccentric shaft portion, 40B Second eccentric shaft portion, 40X Eccentric shaft portion, 41 End, 42 Oil supply hole, 43 First oil supply port, 44 Second oil supply port, 45 Centrifugal pump, 50 Vane, 50A First vane, 50B Second vane, 50c Connecting portion, 51 Spring, 51A First spring, 51B Second spring, 52 Intake passage, 52A First intake passage, 52B Second intake passage, 53 Discharge passage, 53A First discharge passage, 53B Second discharge passage, 54 Spring hole, 54A First spring hole, 54B Second spring hole, 55 Cylinder chamber, 55A First cylinder chamber, 55B Second cylinder chamber, 56 Vane groove, 56A First vane groove, 56B Second vane groove, 57 Intake chamber, 57A First intake chamber, 57B Second intake chamber, 58 Compression chamber, 58A First compression chamber, 58B Second compression chamber, 70a Circular hole portion, 71a Key groove portion, 71b Key groove portion, 71c Corner portion, 80a Cylindrical portion, 81a Key portion, 81b Key portion, 81c corner portion, 200 refrigeration cycle device, 201 flow path switching device, 202 outdoor heat exchanger, 203 pressure reducer, 204 indoor heat exchanger, 501 inner vane, 501i inner peripheral end surface, 501o outer peripheral end surface, 502 outer vane, 502i inner peripheral end surface, 502o outer peripheral end surface, 503 recessed portion, 503w1 bottom portion, 503w2 inner portion, 504 convex portion, 505 first magnet, 506 second magnet, 507 tip portion, 508 spring arrangement hole, 509 base portion, Ax rotation center.

Claims

1. A compressor comprising: a cylinder fixed to the inner periphery of a sealed container, the inner periphery having a vane groove formed on it that extends radially; an annular piston that rotates eccentrically along the inner periphery of the cylinder; a vane that is accommodated in the vane groove formed in the cylinder so as to be able to move forward and backward in the radial direction, and that separates the space between the inner periphery of the cylinder and the outer periphery of the piston into a compression chamber and a suction chamber; a spring that is provided in the cylinder and expands and contracts radially, pressing the vane against the piston from the outer periphery of the vane; and first and second magnets that are provided on the vane, the vane having an inner vane and an outer vane arranged on the outer periphery of the inner vane, the first magnet and the second magnet being arranged so that the first magnet is arranged on the outer periphery of the inner vane and the second magnet is arranged on the inner periphery of the outer vane so as to face the first magnet, the opposing surfaces having the same magnetic polarity and repelling each other.

2. The compressor according to claim 1, wherein the inner vane and the outer vane have a recess formed on one of the outer peripheral end face of the inner vane and the inner peripheral end face of the outer vane, and a protrusion formed on the other that slides radially within the recess, and the inner vane and the outer vane are connected to each other by the recess and the protrusion.

3. The compressor according to claim 2, wherein the convex portion has a cylindrical portion that extends in the radial direction and has a circular cross section perpendicular to the radial direction, and a key portion that is formed to protrude from the outer circumferential surface of the cylindrical portion and extends in the radial direction, and the concave portion has a circular hole portion that houses the cylindrical portion and a key groove portion that houses the key portion.

4. The compressor according to claim 3, wherein the outer ring contour of the key portion and the key groove portion in a cross section perpendicular to the radial direction is formed in an arc shape.

5. The compressor according to claim 2, wherein the cross section of the convex portion and the concave portion perpendicular to the radial direction is formed in a rectangular shape.

6. A compressor as claimed in any one of claims 2 to 5, wherein the recess is formed on the outer peripheral end face of the inner vane, the protrusion is formed on the inner peripheral end face of the outer vane, a spring arrangement hole in which the spring is arranged is formed in the outer peripheral end face of the outer vane, and the inner vane and the outer vane are configured so that the length from the inner peripheral end face of the inner vane to the part of the outer peripheral end face other than the recess is longer than the length from the part of the inner peripheral end face of the outer vane other than the protrusion to the outer peripheral end face.

7. A compressor according to any one of claims 2 to 6, wherein the first magnet and the second magnet are arranged at the bottom of the recess and the tip of the protrusion.

8. The compressor according to any one of claims 1 to 7, wherein the refrigerant used is any one of R1234yf, R1234ze, R32, and R290, or a mixture of two or more of these, or a mixture of any one of these with another refrigerant, or a mixed refrigerant containing R1132(E), or a mixed refrigerant containing R1123.

9. A refrigeration cycle device comprising: a compressor according to any one of claims 1 to 8; a radiator into which refrigerant compressed by the compressor flows and into which the refrigerant dissipates heat; a pressure reducer that reduces the pressure of the refrigerant flowing out of the radiator; and an evaporator into which the refrigerant flowing out of the pressure reducer flows and into which the refrigerant evaporates.

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