JP2015055187A - Compressor and refrigeration cycle device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor, and a refrigeration cycle device capable of reducing costs of a device as a whole, and a weight while keeping performance of a motor.SOLUTION: A compressor includes a rotor iron core 65 fixed to a rotation shaft 31, and provided with a plurality of accommodation holes 66 extended along an axial direction of the rotation shaft 31, and formed at intervals in the circumferential direction, and a plurality of permanent magnets 67 respectively disposed in the accommodation holes 66. The plurality of permanent magnets 67 respectively have a first permanent magnet 67a and a second permanent magnet 67b disposed on positions opposed to each other in the direction along the eccentric direction of eccentric portions 51, 52 of the rotating shaft 31. The second permanent magnet 67b is shifted from the first permanent magnet 67a at least at one end portion of both end portions along the axial direction of the rotating shaft 31, and has an amount of magnetic flux equal to that of the first permanent magnet 67a, and at least one of the first permanent magnet 67a and the second permanent magnet 67b is functioned as a balance weight.

Description

  Embodiments described herein relate generally to a compressor and a refrigeration cycle apparatus.

  Conventionally, as a rotary compressor (compressor) used in a refrigeration cycle apparatus such as an air conditioner, a rotating shaft, an electric motor unit that rotates the rotating shaft, and a compression mechanism unit that compresses fluid by rotating the rotating shaft The thing equipped with these is known.

The electric motor unit includes a stator fixed to the inner wall surface of the hermetic container and a rotor configured to be rotatable inside the stator. The rotor includes a rotor iron core fixed to the rotation shaft and a plurality of permanent magnets arranged on the rotor iron core.
On the other hand, the compression mechanism section includes a cylinder chamber and a roller that is attached to the eccentric portion of the rotating shaft and that rotates eccentrically in the cylinder chamber by the rotation of the rotating shaft, and the roller rotates eccentrically in the cylinder chamber. The fluid in the cylinder chamber is compressed.

  By the way, in the above-described rotary compressor, a moment for tilting the rotating shaft acts on the rotating shaft due to the centrifugal force acting on the eccentric portion of the rotating shaft and the roller. Therefore, there is a problem that vibrations and noises are generated due to the rotation axis being swung around and the rotation balance being lost.

  Therefore, a weight member serving as a balance weight is provided on the rotor iron core, and acts on the rotating shaft due to the eccentric portion of the rotating shaft and the centrifugal force of the roller due to the moment acting on the rotating shaft due to the centrifugal force of the weight member. A configuration that cancels out the moment and reduces vibration and noise is known.

JP 2005-273482 A

  However, in the conventional configuration described above, the provision of the weight member causes a problem that the cost of the apparatus increases and the weight of the entire apparatus increases.

  The problem to be solved by the present invention is to provide a compressor and a refrigeration cycle apparatus capable of reducing the cost and weight of the entire apparatus while maintaining the characteristics of the electric motor.

  In the compressor according to the embodiment, the compressor includes a rotating shaft, an electric motor unit that rotates the rotating shaft, and a compression mechanism unit that compresses a fluid by the rotation of the rotating shaft. A rotor core that is fixed to the shaft and that has a plurality of receiving holes extending along the axial direction of the rotating shaft and spaced apart in the circumferential direction; and a plurality of permanent magnets respectively provided in the receiving hole; The plurality of permanent magnets include a first permanent magnet and a second permanent magnet disposed at positions facing each other in a direction along the eccentric direction of the eccentric portion of the rotating shaft when viewed from the axial direction of the rotating shaft. And among the both ends along the axial direction of the rotating shaft of the second permanent magnet, at least one end portion is shifted with respect to the first permanent magnet and the amount of magnetic flux is the first permanent magnet. Formed equal to the magnet, the first permanent At least one of the magnet and the second permanent magnet is disposed so as to function as a balance weight.

It is a schematic block diagram of the refrigerating-cycle apparatus containing sectional drawing of the rotary compressor in embodiment. It is a disassembled perspective view of a rotor. It is a side view of an end plate. It is sectional drawing which shows the other structure of a rotor. It is sectional drawing which shows the other structure of a rotor.

Next, the compressor and the refrigeration cycle apparatus of the embodiment will be described with reference to the drawings.
[Refrigeration cycle equipment]
As shown in FIG. 1, the refrigeration cycle apparatus 1 of the present embodiment includes a rotary compressor 2, a condenser 3 connected to the rotary compressor 2, an expansion device 4 connected to the condenser 3, An evaporator 5 connected between the expansion device 4 and the rotary compressor 2.

  The rotary compressor 2 is a so-called rotary compressor, and compresses a low-pressure gas refrigerant (fluid) taken inside to form a high-temperature / high-pressure gas refrigerant. The specific configuration of the rotary compressor 2 will be described later.

The condenser 3 dissipates heat from the high-temperature and high-pressure gas refrigerant sent from the rotary compressor 2, and converts the high-temperature and high-pressure gas refrigerant into a high-pressure liquid refrigerant.
The expansion device 4 lowers the pressure of the high-pressure liquid refrigerant sent from the condenser 3 so that the high-pressure liquid refrigerant becomes a low-temperature / low-pressure liquid refrigerant.
The evaporator 5 vaporizes the low-temperature and low-pressure liquid refrigerant sent from the expansion device 4, and converts the low-temperature and low-pressure liquid refrigerant into a low-pressure gas refrigerant. In the evaporator 5, when the low-pressure liquid refrigerant is vaporized, the vaporization heat is taken from the surroundings, and the surroundings are cooled. The low-pressure gaseous refrigerant that has passed through the evaporator 5 is taken into the rotary compressor 2 described above.

  Thus, in the refrigeration cycle apparatus 1 of the present embodiment, the refrigerant that is the working fluid circulates while changing phase between the gas refrigerant and the liquid refrigerant, and is dissipated in the process of phase change from the gas refrigerant to the liquid refrigerant. The heat is absorbed in the process of phase change from gas to gaseous refrigerant, and heating, cooling, and the like are performed using these heat dissipation and heat absorption.

<Rotary compressor>
The rotary compressor 2 includes a compressor body 11 and an accumulator 12.
The accumulator 12 is a so-called gas-liquid separator and is provided between the evaporator 5 and the compressor body 11 described above. The accumulator 12 is connected to cylinders 41 and 42 (to be described later) of the compressor body 11 through the suction pipe 21. Among the gas refrigerant evaporated by the evaporator 5 and the liquid refrigerant not evaporated by the evaporator 5, the accumulator 12 is a gas. Only the refrigerant is supplied to the compressor body 11.

  The compressor body 11 includes a rotating shaft 31, an electric motor section 32 that rotates the rotating shaft 31, a compression mechanism section 33 that compresses a gaseous refrigerant by the rotation of the rotating shaft 31, and the rotating shaft 31, the electric motor section 32, and the compression mechanism. And a cylindrical sealed container 34 in which the portion 33 is housed. The hermetic container 34 and the rotary shaft 31 are coaxially arranged along the axis O, the motor part 32 is arranged on one end side (upper side in FIG. 1) along the axis O, and the other end side (lower side in FIG. 1). The compression mechanism section 33 is disposed on the front side. In the following description, a direction along the axis O is simply referred to as an axial direction, a direction orthogonal to the axial direction is referred to as a radial direction, and a direction around the axial direction is referred to as a circumferential direction.

<Compression mechanism>
The compression mechanism unit 33 includes a first cylinder 41 and a second cylinder 42 located on the other end side in the axial direction with respect to the first cylinder 41. The cylinders 41 and 42 have a cylindrical shape, and are abutted in the axial direction with the partition plate 43 interposed therebetween. A main bearing 44 that covers the first cylinder 41 from one end side in the axial direction is disposed on one end side in the axial direction with respect to the first cylinder 41, and the other end side in the axial direction with respect to the second cylinder 42. A sub-bearing 45 that covers the second cylinder 42 from the other end side in the axial direction is disposed. The space defined by the first cylinder 41, the partition plate 43, and the main bearing 44 constitutes the first cylinder chamber 46, and the space defined by the second cylinder 42, the partition plate 43, and the auxiliary bearing 45 is the first. A two-cylinder chamber 47 is configured. The suction pipes 21 described above are connected to the cylinders 41 and 42, respectively, so that the gas refrigerant separated by the accumulator 12 is taken into the cylinder chambers 46 and 47.

  The rotating shaft 31 described above is provided through the cylinder chambers 46 and 47 and is rotatably supported by the main bearing 44 and the sub bearing 45. A first eccentric portion 51 is formed in a portion of the rotating shaft 31 located in the first cylinder chamber 46, and a second eccentric portion 52 is formed in a portion located in the second cylinder chamber 47. Yes. Each of the eccentric portions 51 and 52 has the same shape and size in a plan view as viewed from the axial direction, and is eccentric by the same amount in the radial direction with respect to the axis O with a phase difference of 180 ° in the circumferential direction. That is, each eccentric part 51 and 52 is each eccentric toward the both sides along one direction (henceforth an eccentric direction) among radial directions.

  A first roller 53 is fitted to the first eccentric portion 51, and a second roller 54 is fitted to the second eccentric portion 52. Each of the rollers 53 and 54 is configured to be capable of eccentric movement (eccentric rotation) while the outer peripheral surface of each of the rollers 53 and 54 is in sliding contact with the inner peripheral surface of each of the cylinders 41 and 42 as the rotary shaft 31 rotates. .

  Each cylinder 41, 42 is provided with a blade (not shown) that is slidable along the radial direction. These blades are urged inward in the radial direction by an urging means (not shown), and their tips are in contact with the outer peripheral surfaces of the rollers 53 and 54 in the cylinder chambers 46 and 47, respectively. Thus, the blade is configured to be able to advance and retract in the cylinder chambers 46 and 47 in accordance with the rotation operation of the rollers 53 and 54. The cylinder chambers 46 and 47 are divided into a suction chamber side and a compression chamber side by rollers 53 and 54 and blades. Then, the compression operation is performed in the cylinder chambers 46 and 47 by the rotation operation of the rollers 53 and 54 and the advance and retreat operation of the blade.

The main bearing 44 is provided with a first discharge valve mechanism 56 capable of opening and closing a first discharge hole 44 a for discharging the refrigerant in the first cylinder chamber 46 according to the pressure in the first cylinder chamber 46. On the other hand, the secondary bearing 45 is provided with a second discharge valve mechanism 57 that can open and close a second discharge hole 45 a for discharging the refrigerant in the second cylinder chamber 47 according to the pressure in the second cylinder chamber 47. Yes.
Further, a muffler (first muffler 58 and second muffler 59) from which high-temperature and high-pressure gaseous refrigerant is discharged through the discharge valve mechanisms 56 and 57 is provided in the bearings 44 and 45 in the axial direction. It covers from the outside. The first muffler 58 is formed with a communication hole 50 that allows the inside and outside of the first muffler 58 to communicate with each other, and high-temperature and high-pressure gaseous refrigerant is discharged into the sealed container 34 through the communication hole 50. On the other hand, the inside of the second muffler 59 and the inside of the first muffler 58 communicate with each other through a gas refrigerant guide passage (not shown), and the high-temperature and high-pressure gas refrigerant discharged into the second muffler 59 communicates with the first muffler 58. It is discharged into the sealed container 34 through the hole 50. The sealed container 34 contains lubricating oil, and a portion of the compression mechanism 33 that is located on the other end side in the axial direction from the first muffler 58 is immersed in the lubricating oil.

<Motor section>
As shown in FIGS. 1 and 2, the electric motor unit 32 is a so-called inner rotor type motor, and includes a cylindrical stator 61 fixed to the inner wall surface of the hermetic container 34 by shrink fitting, and a stator 61. , And a cylindrical rotor 62 disposed at a radial interval inside.
The stator 61 is formed by, for example, laminating a plurality of magnetic steel plates in the axial direction, and a coil is wound through an insulator (not shown).

  The rotor 62 includes a rotor core 65 that is press-fitted and fixed to one end of the rotating shaft 31 in the axial direction. The rotor core 65 is formed by, for example, magnetic steel plates laminated in the axial direction, and an accommodation hole 66 that penetrates the rotor core 65 in the axial direction is formed in the outer peripheral portion thereof. The housing holes 66 are, for example, rectangular in a plan view when the rotor core 65 is viewed from the axial direction, and a plurality (four in this embodiment) are arranged at equal intervals in the circumferential direction. Specifically, the receiving hole 66 of the present embodiment has a first receiving hole 66a and a second receiving hole 66b that are arranged at positions facing each other in the direction along the eccentric direction described above in the radial direction, and in the eccentric direction. And a pair of third accommodation holes 66c arranged at positions facing each other in a direction orthogonal to the direction along. The first accommodation hole 66a is located on the first roller 53 (first eccentric portion 51) side along the eccentric direction, and the second accommodation hole 66b is the second roller 54 (second eccentric portion 52) along the eccentric direction. Located on the side.

  Each accommodation hole 66 accommodates a flat permanent magnet 67 made of a rare earth such as neodymium. The permanent magnet 67 is housed in each of the third housing holes 66c, the first permanent magnet 67a housed in the first housing hole 66a, the second permanent magnet 67b housed in the second housing hole 66b, and the third housing hole 66c. And a third permanent magnet 67c.

  Here, in the present embodiment, the first permanent magnet 67a and the second permanent magnet 67b described above are arranged so that the second permanent magnet 67b functions as a balance weight by shifting the position of one end in the axial direction. Has been. In this case, in the present embodiment, the first permanent magnet 67a and the second permanent magnet 67a and the second permanent magnet 67a are arranged so that the second roller 54 side along the eccentric direction described above becomes heavy and the first roller 53 side lightens at one end portion in the axial direction of the rotor 62. A permanent magnet 67b is disposed.

  Specifically, the first permanent magnet 67a has a shorter axial length than the second and third permanent magnets 67b and 67c, and is lighter in weight than the second and third permanent magnets 67b and 67c. It has become. The first permanent magnet 67a is shorter in the axial direction than the rotor core 65, and is arranged in a state of being brought closer to the other end side in the axial direction in the first accommodation hole 66a. Therefore, a gap is provided at one end portion in the axial direction in the first accommodation hole 66a.

  On the other hand, the second and third permanent magnets 67b and 67c have an axial length equivalent to that of the rotor core 65, and are disposed almost entirely along the axial direction in the housing holes 66b and 66c. Yes. Accordingly, the second permanent magnet 67b is arranged with the position of one end portion in the axial direction shifted with respect to the first permanent magnet 67a, and one end of the second permanent magnet 67b in the axial direction with respect to the first permanent magnet 67a. The portion protruding to the side constitutes a weight region (balance weight) 70. Therefore, at one end portion of the rotor 62 in the axial direction, the second roller 54 side along the eccentric direction is heavy, and the first roller 53 side is light. In addition, the position of the other end part of the axial direction in each permanent magnet 67, the thickness along a radial direction, and the width | variety along the circumferential direction are respectively equal.

Further, the first permanent magnet 67a is made of a material having a higher magnetic flux density (residual magnetic flux density: Br) than the second and third permanent magnets 67b and 67c, and the amount of magnetic flux is the second and third permanent magnets 67b and 67c. It is equivalent to.
Further, the first permanent magnet 67a has a smaller coercive force than the second and third permanent magnets 67b and 67c. That is, since the permanent magnet 67 tends to have a higher magnetic flux density as the coercive force is smaller, the coercive force of the first permanent magnet 67a is set smaller than that of the second and third permanent magnets 67b and 67c. It becomes easier to set the magnetic flux density of the first permanent magnet 67a higher than that of the second and third permanent magnets 67b and 67c.

  The rotor core 65 is sandwiched between a pair of end plates (a first end plate 71 and a second end plate 72) provided on both axial ends thereof. Each of the end plates 71 and 72 has an annular shape made of a nonmagnetic material and covers the above-described accommodation hole 66 from both sides in the axial direction.

Of the end plates 71 and 72, the first end plate 71 positioned on the other end side in the axial direction with respect to the rotor core 65 is in contact with the other end surface along the axial direction of each permanent magnet 67.
On the other hand, as shown in FIG. 3, among the end plates 71, 72, the second end plate 72 located on one end side in the axial direction with respect to the rotor core 65 is permanently accommodated in each accommodation hole 66. A plurality of magnet pressers 73 for positioning the magnets 67 in the axial direction are formed.

  Each magnet presser 73 has a plate spring shape in which the portion of the second end plate 72 that overlaps each accommodation hole 66 in the axial direction is cut and raised toward the inside of the accommodation hole 66. Each magnet presser 73 has a tip abutted against one end surface in the axial direction of each permanent magnet 67 and presses each permanent magnet 67 toward the other end side in the axial direction (first end plate 71 side). . In this case, among the magnet holders 73, the magnet holder 73a located in the first accommodation hole 66a has an axial length longer than the magnet holders 73b located in the second and third accommodation holes 66b and 66c. It is getting longer.

  Further, as shown in FIG. 1, a weight member 74 serving as a balance weight is disposed on the other end side in the axial direction with respect to the first end plate 71. The weight member 74 is a plate material that has an arc shape in a plan view when viewed from the axial direction, and is disposed on the first roller 53 side along the eccentric direction described above on the other end side in the axial direction of the rotor 62. . In the present embodiment, the weight member 74 is disposed at a position equivalent to the first accommodation hole 66a in the circumferential direction, and two pieces are overlapped in the axial direction. The weight member 74, the end plates 71 and 72, and the rotor iron core 65 are fixed in a state where they are stacked in the axial direction by caulking pins 75 (see FIG. 2) that pass through them in the axial direction.

The weight member 74 and the weight region 70 of the second permanent magnet 67b described above are opposed to each other in the eccentric direction across the axis O in a plan view as viewed from the axial direction. Due to this, the moment acting on the rotating shaft 31 is offset.
Specifically, when the rotating shaft 31 rotates, the centrifugal force by the first roller 53 is F1, the centrifugal force by the second roller 54 is F2, the centrifugal force by the weight member 74 is F3, and the centrifugal force by the weight region 70 is F4. L1 is the distance to the axial center of the first roller 53 with reference to the other axial end of the rotary shaft 31, and L2 is the distance to the axial center of the second roller 54. Assuming that the distance to the axial center is L3 and the distance to the axial center of the weight region 70 is L4, the moments M1 to M4 acting on the rotating shaft 31 due to F1 to F4 are F1 × L1, respectively. It is represented by F2 × L2, F3 × L3, and F4 × L4.

  In this case, the moment M1 acting on the rotating shaft 31 due to the centrifugal force F1 of the first roller 53 and the moment M4 acting on the rotating shaft due to the centrifugal force F4 of the weight region 70 act in the same direction. doing. On the other hand, the moment M2 acting on the rotating shaft 31 due to the centrifugal force F2 of the second roller 54 and the moment M3 acting on the rotating shaft 31 due to the centrifugal force F3 of the weight member 74 act in the same direction. doing.

  In this embodiment, the mass of the weight member 74 and the weight region 70 is adjusted so that the sum of the moment M1 and the moment M4 described above is equal to the sum of the moment M2 and the moment M3. Note that the mass of the weight member 74 can be adjusted, for example, by changing the material, the number, etc., of the weight member 74. Further, the weight region 70 maintains the same amount of magnetic flux between the first permanent magnet 67a and the second permanent magnet 67b, and the material of the permanent magnets 67a and 67b and the length of the weight region 70 (first permanent magnet). The mass can be adjusted by changing the displacement amount of the 67a and the second permanent magnet 67b along the axial direction).

  In the rotary compressor 2 of this embodiment, the rotor 62 rotates together with the rotating shaft 31 by supplying electric power from a power source (not shown) to the coil of the stator 61. The rollers 53 and 54 are eccentrically rotated in the cylinder chambers 46 and 47 by the rotation of the rotating shaft 31, whereby the low-pressure gaseous refrigerant taken into the cylinder chambers 46 and 47 is compressed.

As described above, in the present embodiment, the first permanent magnet 67a and the second permanent magnet 67b having the same amount of magnetic flux while being arranged with the position of one end in the axial direction being shifted with respect to the first permanent magnet 67a. And the second permanent magnet 67b is arranged so as to function as a balance weight.
According to this configuration, the number of weight members 74 provided separately and the mass of the weight members 74 can be reduced by causing the second permanent magnet 67b itself to function as a balance weight. As a result, the cost of the rotary compressor 2 as a whole is reduced and the weight is reduced, and the moment acting on the rotary shaft 31 due to the eccentric force 51, 52 of the rotary shaft 31 and the centrifugal force of the rollers 53, 54 is achieved. The influence of M1 and M2 can be reduced and the rotation balance can be stabilized. As a result, since vibration and noise can be reduced, the high-quality and highly reliable rotary compressor 2 can be provided.
In particular, in the present embodiment, by setting the magnetic flux amounts of the first permanent magnet 67a and the second permanent magnet 67b to be equal, the magnetic flux in the circumferential direction (between each permanent magnet 67) is maintained uniformly, and torque ripple is increased. Can be suppressed. As a result, it is possible to stabilize the rotation balance while maintaining the characteristics of the electric motor unit 32.

  Further, by forming the first permanent magnet 67a shorter than the second permanent magnet 67b, a portion protruding from the first permanent magnet 67a within the length range of the second permanent magnet 67b (a portion shifted in the axial direction) ) Can function as the weight region 70. Thereby, the rotation balance can be adjusted while suppressing the increase in size of the rotor 62 in the axial direction.

  And since the refrigerating cycle apparatus 1 of this embodiment is equipped with the rotary compressor 2 mentioned above, the refrigerating cycle apparatus 1 with high quality and high reliability can be provided.

  As mentioned above, although several embodiment of this invention was described, these embodiment is shown as an example and is not intending limiting the range of invention. These novel embodiments can be implemented in various other forms, and various omissions, replacements, and changes can be made without departing from the spirit of the invention. These embodiments and modifications thereof are included in the scope and gist of the invention, and are included in the invention described in the claims and the equivalents thereof.

For example, in the above-described embodiment, the first permanent magnet 67a is formed shorter than the second permanent magnet 67b, so that one end of the second permanent magnet 67b in the axial direction is shifted with respect to the first permanent magnet 67a. Although the arranged configuration has been described, the present invention is not limited to this.
For example, as shown in FIG. 4, the axial lengths of both the first and second permanent magnets 67a and 67b are made shorter than the third permanent magnet 67c and the rotor iron core 65, and the axial length is set. Are arranged by shifting the permanent magnets 67a and 67b that are equivalent to each other in the axial direction, and a portion of one permanent magnet 67 that protrudes in the axial direction with respect to the other permanent magnet 67 functions as a weight region (balance weight). It doesn't matter. In this case, the first and second permanent magnets 67a and 67b have a lighter mass than the third permanent magnet 67c, are made of a material having a higher magnetic flux density than the third permanent magnet 67c, and the amount of magnetic flux is the first. It is equivalent to 3 permanent magnets 67c. In the example of FIG. 4, a portion of the first permanent magnet 67 a that protrudes toward the other end side in the axial direction with respect to the second permanent magnet 67 b constitutes the first weight region 100 a, and the second permanent magnet 67 b A portion protruding toward one end side in the axial direction with respect to the first permanent magnet 67a constitutes the second weight region 100b. In this case, the masses of the first permanent magnet 67a and the second permanent magnet 67b themselves and the relationship between the weight regions 100a and 100b are caused by the centrifugal force of the eccentric portions 51 and 52 and the rollers 53 and 54. The design can be changed as appropriate according to the moments M1 and M2 acting on.
According to this configuration, the first permanent magnet 67a and the second permanent magnet 67b function as balance weights at both ends in the axial direction. For example, the mass of a separate balance weight can be reduced, or separate balance weights can be used. Itself can be eliminated, and further cost reduction and weight reduction can be achieved.

In the example shown in FIG. 5, the second permanent magnet 67b is made of a material having a higher magnetic flux density than the first and third permanent magnets 67a and 67c, and the second permanent magnet 67b is shorter than the first permanent magnet 67a. Formed. The other end of the first permanent magnet 67a in the axial direction has a weight region 110 protruding in the axial direction with respect to the second permanent magnet 67b. Further, two weight members 74 are disposed on one end side in the axial direction with respect to the rotor core 65 on the second roller 54 side along the eccentric direction, and along the eccentric direction on the other end side in the axial direction. A single weight member 74 is disposed on the first roller 53 side.
According to this configuration, since the weight region 110 is provided at the other axial end of the first permanent magnet 67a, the mass (number) of the weight members 74 on the other axial end of the rotor core 65 is determined. Can be reduced. Thereby, cost reduction and weight reduction can be achieved.

Moreover, although the compression mechanism part 33 demonstrated the structure provided with the two cylinder chambers 46 and 47 in embodiment mentioned above, it is not restricted to this, A cylinder chamber may be more than three or may be single. . Even in these cases, by appropriately changing the arrangement and length (length of the weight region) of the first permanent magnet 67a and the second permanent magnet 67b, the rotation balance is maintained while maintaining the characteristics of the motor unit 32. It can be stabilized.
Furthermore, in the above-described embodiment, the rotary type compressor has been described.

Furthermore, in the above-described embodiment, the four-pole rotor 62 provided with four permanent magnets 67 has been described, but the number of permanent magnets 67 can be appropriately changed in design. For example, a rotor with 6 poles or the like can also be employed.
Moreover, although embodiment mentioned above demonstrated the structure from which the coercive force of the 1st permanent magnet 67a and the 2nd permanent magnet 67b differs, it is not restricted to this.

  In addition, in the range which does not deviate from the meaning of this invention, it is possible to replace suitably the component in the embodiment mentioned above by the known component, and you may combine the modification mentioned above suitably.

DESCRIPTION OF SYMBOLS 1 ... Refrigeration cycle apparatus 2 ... Rotary compressor (compressor)
DESCRIPTION OF SYMBOLS 3 ... Condenser 4 ... Expansion apparatus 5 ... Evaporator 31 ... Rotating shaft 32 ... Electric motor part 33 ... Compression mechanism part 62 ... Rotor 65 ... Rotor core 66 ... Housing hole 67 ... Permanent magnet 67a ... 1st permanent magnet 67b ... 1st 2 Permanent magnet

Claims (4)

A rotation axis;
An electric motor section for rotating the rotating shaft;
A compressor having a compression mechanism that compresses fluid by rotation of the rotating shaft,
The motor section is
A rotor core that is fixed to the rotating shaft and has a plurality of receiving holes that extend along the axial direction of the rotating shaft at intervals in the circumferential direction;
A plurality of permanent magnets respectively provided in the accommodation hole,
The plurality of permanent magnets are:
A first permanent magnet and a second permanent magnet disposed at positions facing each other in a direction along the eccentric direction of the eccentric portion of the rotating shaft as viewed from the axial direction of the rotating shaft;
The second permanent magnet is arranged such that at least one of the two end portions along the axial direction of the rotating shaft is shifted with respect to the first permanent magnet, and the amount of magnetic flux is the same as that of the first permanent magnet. Equally formed,
A compressor, wherein at least one of the first permanent magnet and the second permanent magnet is arranged to function as a balance weight.   The compressor according to claim 1, wherein the second permanent magnet has a coercive force different from that of the first permanent magnet.   The compressor according to claim 1, wherein the second permanent magnet has an axial length different from that of the first permanent magnet. The compressor according to any one of claims 1 to 3,
A condenser connected to the compressor;
An expansion device connected to the condenser;
An refrigeration cycle apparatus comprising: an evaporator connected between the expansion device and the compressor.

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