Compressor

Abstract

This compressor comprises: a sealed container that constitutes an outer shell; an electric mechanism part, that is disposed inside the sealed container, has a stator and a rotor disposed inside the stator, and rotates the rotor; a drive shaft that passes through the rotor of the electric mechanism part and rotates together with the rotor; a compression mechanism part that is disposed inside the sealed container, is fixed to the drive shaft, and compresses a refrigerant by rotation of the drive shaft; and a first balancer that is fixed to an end of the rotor opposite from the compression mechanism part in the axial direction of the drive shaft, rotates together with the drive shaft, and suppresses unbalance in the compression mechanism part. The first balancer (7) is provided with: a cylindrical part (71) that fits on the outer periphery of the drive shaft; and an oil separation part (72) that has a plurality of blades (73) provided so as to expand radially from the outer peripheral part of the cylindrical part, and that separates the refrigerant and the refrigerator oil. The first balancer has a center of gravity at a position that does not coincide with the axial center of the drive shaft.

Description

Compressor

[0001] The present disclosure relates to a compressor used in an air conditioner or the like.

[0002] A conventional rotary hermetic compressor includes a sealed container, a motor mechanism having a stator and a rotor, a compression mechanism for compressing a refrigerant, a discharge pipe for discharging the compressed refrigerant from the sealed container, and a drive shaft fixed to the rotor for transmitting the rotational driving force generated by the motor mechanism to the compression mechanism. In this type of compressor, refrigerant oil mixed with the refrigerant is discharged together with the refrigerant gas into a refrigerant system outside the compressor. A shortage of refrigerant oil in the sealed container can lead to a breakdown. For this reason, some compressors are equipped with an oil separator that separates the refrigerant oil and the refrigerant by centrifugal separation and returns the refrigerant oil to the inside of the compressor (see, for example, Patent Document 1).

[0003] In Patent Document 1, the oil separation unit is provided at the upper end of the drive shaft that protrudes above the rotor of the electric mechanism in the space between the rotor and the discharge pipe. The oil separation unit in Patent Document 1 has a cylindrical part attached to the upper end of the drive shaft and a plurality of blades that extend radially from the outer periphery of the cylindrical part and overlap with the rotor when viewed in the axial direction.

[0004] International Publication No. 2022 / 153482

[0005] Compressors require balancers to suppress imbalance in the compression mechanism, and balancers are often installed at both axial ends of the rotor. However, Patent Document 1 does not mention the installation of balancers. In the compressor of Patent Document 1, multiple blades of the oil separation section extend axially overlapping the rotor. Therefore, if a balancer were to be installed at the end of the rotor on the oil separation section side in the axial direction, it would be installed in the space between the end of the rotor and the multiple blades. However, because the upper end of the drive shaft is limited to a position lower than the end of the discharge pipe inside the sealed container, it is unclear whether sufficient space is provided between the end of the rotor and the multiple blades in the compressor of Patent Document 1 for the balancer to be installed. As a result, the compressor of Patent Document 1 has a problem in that a balancer cannot be installed, potentially preventing imbalance in the compression mechanism.

[0006] The present disclosure has been made in consideration of these points, and aims to provide a compressor that is equipped with an oil separation section having multiple blades and that can suppress imbalance in the compression mechanism section.

[0007] The compressor according to the present disclosure comprises: a sealed container forming an outer shell; an electric mechanism portion disposed inside the sealed container and having a stator and a rotor disposed inside the stator, and rotating the rotor; a drive shaft passing through the rotor of the electric mechanism portion and rotating together with the rotor; a compression mechanism portion disposed inside the sealed container and fixed to the drive shaft, and compressing a refrigerant by rotation of the drive shaft; and a first balancer fixed to an end of the rotor on the opposite side of the drive shaft in the axial direction from the compression mechanism portion, rotating together with the drive shaft, and suppressing imbalance in the compression mechanism portion, wherein the first balancer comprises a cylindrical portion that passes around the outer periphery of the drive shaft, and an oil separation portion that has a plurality of blades arranged radially extending from the outer periphery of the cylindrical portion and separates the refrigerant and refrigeration oil, and the first balancer has a center of gravity at a position that does not coincide with the axis of the drive shaft.

[0008] The compressor according to the present disclosure can suppress imbalance in the compression mechanism in a compressor equipped with an oil separation unit having a plurality of blades.

[0009] 5 is a longitudinal sectional view schematically showing the overall structure of a compressor according to a first embodiment. FIG. 6 is a view showing a drive shaft and a structure around the drive shaft of the compressor according to the first embodiment. FIG. 7 is a schematic side view showing a first balancer and a structure around the first balancer of the compressor according to the first embodiment. FIG. 8 is a schematic side view of the first balancer of the compressor according to the first embodiment. FIG. 9 is a schematic top view of the first balancer of the compressor according to the first embodiment. FIG. 10 is a sectional view taken along the line A-A of FIG. 5. FIG. 11 is a view showing a first modification of the oil separation section according to the first embodiment. FIG. 12 is a view (1 / 2) showing a second modification of the oil separation section according to the first embodiment. FIG. 13 is a view (2 / 2) showing a second modification of the oil separation section according to the first embodiment. FIG. 14 is a sectional view of a blade of the first balancer according to the second embodiment. FIG. 15 is a sectional view of another example of the blade of the first balancer according to the second embodiment. FIG. 16 is a schematic top view illustrating the positional relationship between the first balancer and the electric mechanism of the compressor according to the third embodiment. FIG. 17 is a schematic top view of the first balancer of the compressor according to the fourth embodiment. FIG. 18 is a schematic side view of the first balancer of the compressor according to the fourth embodiment. FIG. 19 is a view showing a drive shaft of a compressor according to a fifth embodiment. FIG. 10 is an explanatory diagram of whirling of a drive shaft and a rotor of a compressor according to embodiment 5. FIG. 11 is an explanatory diagram of whirling of a drive shaft and a rotor of comparative example 1. FIG. 12 is an explanatory diagram of whirling of a drive shaft and a rotor of comparative example 2. FIG. 13 is a graph showing the relationship between the unbalance amount ratio of the second balancer to the first balancer and the whirling ratio in comparative example 2. FIG. 14 is a graph showing the whirling suppression effect of the compressor according to embodiment 5, showing the relationship between the rotation speed of the drive shaft and the amount of whirling. FIG. 15 is a diagram showing the drive shaft of a compressor according to embodiment 6. FIG. 16 is a diagram showing the drive shaft of a compressor according to embodiment 7.

[0010] Hereinafter, a compressor according to an embodiment of the present disclosure will be described with reference to the drawings. In the following drawings, including FIG. 1, components denoted with the same reference numerals are identical or equivalent, and are common throughout the embodiments described below. Furthermore, the shape, size, arrangement, and the like of the configurations shown in each drawing may be changed as appropriate. Furthermore, the configurations of the components shown throughout the specification are merely examples and are not limited to the configurations described in the specification.

[0011] Embodiment 1 [Configuration of Compressor 100] Fig. 1 is a longitudinal cross-sectional view schematically illustrating the overall structure of compressor 100 according to Embodiment 1. Fig. 2 is a diagram illustrating a drive shaft 5 and the structure around the drive shaft of compressor 100 according to Embodiment 1. Compressor 100 according to Embodiment 1 is a rotary hermetic compressor. Compressor 100 includes an electric mechanism 4 and a compression mechanism 10 that draws in and compresses refrigerant by rotation of drive shaft 5 fixed to electric mechanism 4, and these are arranged inside a sealed container 60. Inside sealed container 60, electric mechanism 4 is arranged in an upper space within sealed container 60, and compression mechanism 10 is arranged in a lower space within sealed container 60. Inside sealed container 60, electric mechanism 4 is arranged above compression mechanism 10, and compression mechanism 10 is arranged below electric mechanism 4.

[0012] The compressor 100 also includes, inside the sealed container 60, a drive shaft 5 that transmits the rotational driving force generated in the electric mechanism 4 to the compression mechanism 10, and a first balancer 7 and a second balancer 8 that are provided in the electric mechanism 4 and suppress imbalance in the compression mechanism 10. Furthermore, suction pipes 62 and 63 for drawing in refrigerant are connected to the side wall of the sealed container 60. The number of suction pipes is not limited to two. A discharge pipe 64 for discharging compressed refrigerant is provided on the top surface of the sealed container 60. The discharge pipe 64 is erected so as to extend perpendicular to the top surface of the compressor 100, but the angle of the discharge pipe 64 with respect to the top surface is not limited to being perpendicular.

[0013] (Sealed casing 60) The sealed casing 60 forms the outer shell of the compressor 100 and forms a sealed space inside the sealed casing 60. The sealed casing 60 is formed from, for example, a steel plate, and the side wall portion of the sealed casing 60 is formed in a substantially circular shape.

[0014] (Electric mechanism 4) The electric mechanism 4 includes an annular stator 2 fixed to the sealed container 60, and a rotor 3 disposed inside the stator 2 with a predetermined gap between it and the inner peripheral surface of the stator 2. The rotor 3 is disposed so as to be freely rotatable relative to the stator 2. The rotor 3 is formed in a cylindrical shape, and a drive shaft 5 is fixed to the center of the rotor 3. The rotor 3 is fixed to a first main shaft portion 5d of the drive shaft 5, which will be described later. The rotor 3 is formed with through holes 3a that communicate between the space above the rotor 3 and the space below the rotor 3. The through holes 3a are disposed one by one at equal intervals in the circumferential direction. The shapes of the through holes 3a are not necessarily all the same.

[0015] The electric mechanism 4 is driven by power supplied from the outside via an airtight terminal (not shown). When current flows through the stator 2, the electric mechanism 4 generates a magnetic field, which in turn drives the rotor 3 to rotate. When the electric mechanism 4 is driven, the rotor 3 rotates due to the magnetic field generated in the stator 2, and the rotation of the rotor 3 also rotates the drive shaft 5 fixed to the rotor 3. The drive shaft 5 transmits the driving force generated in the rotor 3 of the electric mechanism 4 to the compression mechanism 10.

[0016] (Compression mechanism 10) The compression mechanism 10 is fixed to the drive shaft 5 and is driven by the rotation of the drive shaft 5 to compress the refrigerant. The compression mechanism 10 includes a bearing 11 and a bearing 12. Each of the bearings 11 and 12 includes a hollow cylindrical bearing boss 13 that rotatably supports the drive shaft 5 and a flat, annular end plate 14. The bearing 11 is disposed on the upper end surface of a cylinder 21 (described below), and the end plate 14 of the bearing 11 closes the end surface of the cylinder 21. A discharge port 14a is formed in the end plate 14 of the bearing 11 and penetrates in the axial direction of the drive shaft 5. The bearing 12 is disposed on the lower end surface of a cylinder 31 (described below), and the end plate 14 of the bearing 12 closes the lower end surface of the cylinder 31. A discharge port 14b is formed in the end plate 14 of the bearing 12 and penetrates in the axial direction.

[0017] The compression mechanism 10 includes two compression sections arranged in the axial direction. The first compression section 10A is the compression section on the electric mechanism side in the axial direction. The second compression section 10B is the compression section on the opposite side of the electric mechanism side in the axial direction. The first compression section 10A includes a cylindrical cylinder 21 having a cylinder chamber, a rolling piston 22 driven by a drive shaft 5 and housed in the cylinder chamber of the cylinder 21, and a vane (not shown) slidably arranged in a vane groove (not shown) provided in the cylinder 21. The second compression section 10B includes a cylindrical cylinder 31 having a cylinder chamber, a rolling piston 32 driven by a drive shaft 5 and housed in the cylinder chamber of the cylinder 31, and a vane (not shown) slidably arranged in a vane groove (not shown) provided in the cylinder 31.

[0018] The rolling piston 22 is rotatably mounted on the first eccentric shaft portion 5a of the drive shaft 5, and the rolling piston 32 is rotatably mounted on the second eccentric shaft portion 5b of the drive shaft 5. The cylinders 21 and 31 are configured in a columnar shape, and a substantially cylindrical through-hole is formed in the approximate center thereof, penetrating in the vertical direction. The through-hole of the cylinder 21 is closed by the end plate portion 14 of the bearing 11 and the intermediate partition plate 15, thereby forming a cylinder chamber within the cylinder 21. The through-hole of the cylinder 31 is closed by the end plate portion 14 of the bearing 12 and the intermediate partition plate 15, thereby forming a cylinder chamber within the cylinder 31. The cylinder chamber within the cylinder 21 and the cylinder chamber within the cylinder 31 are each partitioned into a suction chamber and a compression chamber by a vane.

[0019] (Drive shaft 5) The drive shaft 5 is formed in a columnar shape, passes through the rotor 3, and rotates together with the rotor 3. The drive shaft 5 is formed to extend in the vertical direction of the compressor 100. The vertical direction of the compressor 100 refers to the height direction of the compressor 100 when the compressor 100 is placed upright with the electric mechanism 4 located above the compression mechanism 10.

[0020] The drive shaft 5 has a first main shaft portion 5d constituting an upper portion, which is one end of the drive shaft 5, a second main shaft portion 5e constituting a lower portion, which is the other end of the drive shaft 5, and a first eccentric shaft portion 5a, a second eccentric shaft portion 5b, and an intermediate shaft portion 5c formed between the first main shaft portion 5d and the second main shaft portion 5e. The drive shaft 5 is formed with the first main shaft portion 5d, the first eccentric shaft portion 5a, the intermediate shaft portion 5c, the second eccentric shaft portion 5b, and the second main shaft portion 5e aligned in this order in the axial direction of the drive shaft 5 from the top to the bottom of the compressor 100. The first main shaft portion 5d, the first eccentric shaft portion 5a, the intermediate shaft portion 5c, the second eccentric shaft portion 5b, and the second main shaft portion 5e are integrally formed from the same material.

[0021] The first main shaft portion 5d is formed to have a longer axial length than the second main shaft portion 5e. The diameter of the first main shaft portion 5d is the same as the diameter of the second main shaft portion 5e. The axial centers of the first main shaft portion 5d and the second main shaft portion 5e are aligned. Hereinafter, the "axial center C of the drive shaft 5" refers to the axial centers of the first main shaft portion 5d and the second main shaft portion 5e.

[0022] The first main shaft portion 5d has a protrusion 51d. The protrusion 51d is a portion that protrudes above the upper surface of the rotor 3 and extends from the rotor 3 toward the discharge pipe 64. The tip of the protrusion 51d faces the end of the discharge pipe 64. However, this configuration is not limited, and the tip of the protrusion 51d does not have to face the end of the discharge pipe 64. The end of the discharge pipe 64 is the tip portion of the discharge pipe 64 located inside the compressor 100, which is the suction port 64a of the discharge pipe 64.

[0023] The first eccentric shaft portion 5a has a central axis that is eccentric from the axis C of the drive shaft 5. The first eccentric shaft portion 5a is rotatably mounted inside the rolling piston 22, and is disposed in the cylinder chamber of the cylinder 21. The second eccentric shaft portion 5b has a central axis that is eccentric from the axis C of the drive shaft 5. The second eccentric shaft portion 5b is rotatably mounted inside the rolling piston 32, and is disposed in the cylinder chamber of the cylinder 31. The first eccentric shaft portion 5a and the second eccentric shaft portion 5b are provided with a phase difference of 180 degrees.

[0024] The first eccentric shaft portion 5a and the second eccentric shaft portion 5b are connected by an intermediate shaft portion 5c. The axis of the intermediate shaft portion 5c coincides with the axis C of the drive shaft 5. The diameter of the intermediate shaft portion 5c is the same as the diameters of the first main shaft portion 5d and the second main shaft portion 5e. The intermediate shaft portion 5c is disposed within a through hole of the intermediate partition plate 15.

[0025] In the drive shaft 5 having the above-described configuration, the first main shaft portion 5d is rotatably supported by a bearing 11, and the second main shaft portion 5e is rotatably supported by a bearing 12.

[0026] (First balancer 7 and second balancer 8) The first balancer 7 and second balancer 8 balance the entire rotating system of the compressor 100 to suppress imbalance in the compression mechanism 10. The first balancer 7 and second balancer 8 are mainly made of metal or resin, but are not limited to these materials.

[0027] The first balancer 7 is fixed to an end of the rotor 3 on the axial side opposite the compression mechanism 10, and the second balancer 8 is fixed to an end of the rotor 3 on the axial side of the compression mechanism 10. The first balancer 7 and the second balancer 8 rotate together with the rotor 3 as the drive shaft 5 rotates. The first balancer 7 and the second balancer 8 are set in positions where their respective centers of gravity do not coincide with the axis C of the drive shaft 5. By setting the first balancer 7 and the second balancer 8 in positions where their respective centers of gravity do not coincide with the axis C of the drive shaft 5, an imbalance is generated, which adjusts the weight balance of the entire drive shaft and suppresses imbalance in the compression mechanism 10.

[0028] The first balancer 7 is disposed in the space between the rotor 3 and the discharge pipe 64. The first balancer 7 is disposed at a position away from the suction port 64a of the discharge pipe 64. The first balancer 7 is disposed at a position not in contact with the discharge pipe 64. The first balancer 7 is fixed to the upper part of the rotor 3.

[0029] The first balancer 7 has a cylindrical portion 71 and an oil separation portion 72. As shown in Fig. 1, the first balancer 7 is fixed to the rotor 3 with the cylindrical portion 71 passing over the outer periphery of the protruding portion 51d of the drive shaft 5. The first balancer 7 is fixed to the rotor 3 with bolts or the like, with the drive shaft 5 passing through a through-hole 71a in the cylindrical portion 71.

[0030] The second balancer 8 is disposed in the space between the rotor 3 and the bearing 11. The second balancer 8 is fixed to the lower part of the rotor 3. The second balancer 8 is formed in a semicircular ring shape. The second balancer 8 has a communication hole 8a that penetrates in the axial direction at a position opposite the through hole 3a so as not to block the through hole 3a when fixed to the rotor 3. Note that the shape of the second balancer 8 is not limited to a semicircular ring. The second balancer 8 may have, for example, a ring-shaped main body portion and an arc-shaped portion that protrudes in an arc-like shape in the axial direction from the surface of the main body opposite the rotor 3 in the axial direction.

[0031] 2, the center of gravity G1 of the first balancer 7 is located on the radially opposite side of the axis C1 of the first eccentric shaft portion 5a with respect to the axis C of the drive shaft 5, and is located on the same side of the axis C2 of the second eccentric shaft portion 5b with respect to the axis C of the drive shaft 5. The center of gravity G2 of the second balancer 8 is located on the radially opposite side of the axis C1 of the first eccentric shaft portion 5a with respect to the axis C of the drive shaft 5, and is located on the radially opposite side of the axis C2 of the second eccentric shaft portion 5b with respect to the axis C of the drive shaft 5.

[0032] The first balancer 7 and the second balancer 8 have the following configuration (A) or (B): (A) LG1 = LG2 and WG1 < WG2 (B) LG1 < LG2 and WG1 = WG2 where, LG1: radial distance between the center of gravity G1 of the first balancer 7 and the axis C of the drive shaft 5 LG2: radial distance between the center of gravity G2 of the second balancer 8 and the axis C of the drive shaft 5 WG1: weight of the first balancer 7 WG2: weight of the second balancer 8

[0033] By having the above-described configuration (A) or (B), the compressor 100 can balance the entire rotating system of the compressor 100 and suppress imbalance in the compression mechanism 10 .

[0034] FIG. 3 is a schematic side view showing the first balancer 7 of the compressor 100 according to the first embodiment and the surrounding structure of the first balancer 7. FIG. 4 is a schematic side view of the first balancer 7 of the compressor 100 according to the first embodiment. FIG. 5 is a schematic top view of the first balancer 7 of the compressor 100 according to the first embodiment. FIG. 6 is a cross-sectional view taken along line A-A in FIG. 5. The rotational direction DR indicated by the arrows in FIGS. 3 to 6 is the rotational direction of the drive shaft 5 and the first balancer 7. The axial direction S indicated by the arrow in FIG. 3 is the axial direction of the drive shaft 5. The circumferential direction CD indicated by the double-ended arrow in FIG. 5 is the circumferential direction of the drive shaft 5 and the first balancer 7. The radial direction R indicated by the double-ended arrow in FIG. 5 is the radial direction of the drive shaft 5 and the first balancer 7.

[0035] The configuration of the first balancer 7 will be described in detail below with reference to FIGS.

[0036] As described above, the first balancer 7 has the cylindrical portion 71 and the oil separation portion 72. The oil separation portion 72 rotates together with the drive shaft 5 during operation of the compressor 100 to agitate the refrigerant gas inside the compressor 100 and the refrigerant oil contained therein, thereby separating the refrigerant from the refrigerant oil. The oil separation portion 72 has a plurality of blades 73 equally spaced in the circumferential direction CD on the outer circumferential surface of the cylindrical portion 71. In the illustrated example, the oil separation portion 72 has three blades 73. The number of blades 73 is not limited to three and may be one or more. In the illustrated example, the blades 73 are spaced apart in the circumferential direction CD on the outer circumferential surface of the cylindrical portion 71, but they may also be continuously spaced apart in the circumferential direction CD.

[0037] As shown in Fig. 5 , the plurality of blades 73 are formed to extend radially from the outer periphery of the cylindrical portion 71, centered on the center O of the cylindrical portion 71. Some of the plurality of blades 73 are formed so that the length of some of the blades 73 is shorter than the length of the other blades 73. Fig. 5 shows an example in which two of the three blades 73 have the same length in the radial direction R and one is shorter than the other, but the lengths of the radial direction R of the three blades 73 may be different.

[0038] In this way, the first balancer 7 is set at a position where the center of gravity of the first balancer 7 does not coincide with the axis C of the drive shaft 5 because the radial lengths R of some or all of the multiple blades 73 of the oil separation section 72 are different.

[0039] Each of the multiple blades 73 is formed in a paddle blade shape. Specifically, the blade 73 has a front portion 73a and a rear portion 73b. The front portion 73a is a plate-shaped portion formed on the forward side in the rotational direction DR of the first balancer 7. The rear portion 73b is a plate-shaped portion formed integrally with the front portion 73a, located on the backward side in the rotational direction DR of the first balancer 7, and inclined relative to the front portion 73a. The front portion 73a and the rear portion 73b are each a rectangular plate-shaped portion formed to extend outward from the outer periphery of the cylindrical portion 71.

[0040] 3 and 4, the front portion 73a is inclined upward from the front end toward the rear end in the direction of rotation DR as viewed in the radial direction. The rear portion 73b is inclined upward from the rear end toward the front end in the direction of rotation DR as viewed in the radial direction. The inclination of the front portion 73a and the inclination of the rear portion 73b are the same. The blade 73 is formed integrally with the rear edge of the front portion 73a and the front edge of the rear portion 73b abutting against each other, and is formed in a triangular roof shape, in other words, an inverted V shape as viewed in the radial direction.

[0041] The oil separation section 72 is not limited to the shape shown in the figure, and may have the following shapes: Modified examples of the oil separation section 72 are shown below.

[0042] (Modification 1) Figure 7 is a diagram showing Modification 1 of the oil separation unit 72 according to Embodiment 1. The oil separation unit 72 of Modification 1 has a configuration in which all three blades 73 have the same length in the radial direction R, but the spacing between the three blades 73 in the circumferential direction CD is different. Specifically, of the spacings W1, W2, and W3 between two adjacent blades of the three blades 73 in the circumferential direction CD, W1 and W2 are the same, and W3 is shorter than W1 and W2. Figure 7 shows an example in which the lengths of two of W1, W2, and W3 are the same, and one of W1, W2, and W3 is shorter than the other W1 and W2, but W1, W2, and W3 may be different.

[0043] Modification 1 includes a configuration in which, when there are two blades 73, there are two intervals in the circumferential direction CD between two adjacent blades 73, and the two intervals are different. In short, Modification 1 has a configuration in which at least one of the intervals in the circumferential direction CD between two adjacent blades 73 among the multiple blades 73 is different from the other intervals, or all of the intervals are different from each other. With the above configuration, Modification 1 can set the center of gravity of the first balancer 7 at a position that does not coincide with the axis C of the drive shaft 5.

[0044] (Variation 2) Figures 8 and 9 are diagrams showing a variation 2 of the oil separation section 72 according to the first embodiment. In Figure 3 and the like, the blades 73 in the oil separation section 72 have a uniform thickness, but in variation 2 of Figures 8 and 9, the blades 73 do not have a uniform thickness. Specifically, in variation 2 of Figure 8, the blades 73 have a shape in which the thickness increases from the radially inner side to the radially outer side (hereinafter referred to as an outer thickness shape). Furthermore, in variation 2 of Figure 9, the blades 73 have a shape in which the thickness decreases from the radially inner side to the radially outer side (hereinafter referred to as an inner thickness shape).

[0045] As described above, the oil separation unit 72 is not limited to a configuration in which the blades 73 have a uniform thickness, and the blades 73 may have a non-uniform thickness. Furthermore, all three blades 73 of the oil separation unit 72 may have an outer thickness shape or an inner thickness shape, or a combination of outer and inner thickness shapes may be present. The lengths of the radial directions R of the blades 73 may be the same or different. Furthermore, the spacing between two adjacent blades 73 among the three blades 73 may be the same or different. In short, in the second modification, at least one of the blades 73 has an outer thickness shape or an inner thickness shape. By virtue of the above configuration, the second modification allows the center of gravity of the first balancer 7 to be set at a position that does not coincide with the axis C of the drive shaft 5.

[0046] [Operation of Compressor 100] In the compressor 100 configured as described above, the rotation of the rotor 3 rotates the drive shaft 5, and the refrigerant is compressed in the compression mechanism 10 in accordance with the rotation of the drive shaft 5. Specifically, in the compression mechanism 10, the rotation of the drive shaft 5 rotates the first eccentric shaft portion 5a and the second eccentric shaft portion 5b.

[0047] As the first eccentric shaft portion 5a rotates, the rolling piston 22 rotates eccentrically inside the cylinder 21 along the inner circumferential surface of the cylinder 21. When the rolling piston 22 rotates eccentrically inside the cylinder 21, refrigerant gas is drawn into the suction chamber inside the cylinder 21 from the suction pipe 62. The refrigerant gas drawn into the suction chamber inside the cylinder 21 is compressed in the compression chamber inside the cylinder 21 to become high-pressure refrigerant gas. The high-pressure refrigerant gas is discharged into the sealed container 60 from the discharge port 14a.

[0048] As the second eccentric shaft portion 5b rotates, the rolling piston 32 rotates eccentrically inside the cylinder 31 along the inner circumferential surface of the cylinder 31. When the rolling piston 32 rotates eccentrically inside the cylinder 31, refrigerant gas is drawn into the suction chamber inside the cylinder 31 from the suction pipe 63. The refrigerant gas drawn into the suction chamber inside the cylinder 31 is compressed in the compression chamber inside the cylinder 31 to become high-pressure refrigerant gas. The high-pressure refrigerant gas is discharged into the sealed container 60 from the discharge port 14b.

[0049] The high-pressure refrigerant gas discharged from the discharge ports 14a and 14b passes through the through-holes 3a formed in the rotor 3, the air gap between the stator 2 and the rotor 3, and the gaps between the stator windings, and flows into the space above the electric mechanism 4. The refrigerant gas that flows into the space above the electric mechanism 4 contains refrigerant oil. The oil separator 72 of the first balancer 7 separates the refrigerant oil from the refrigerant gas by centrifugation. The refrigerant gas from which the refrigerant oil has been separated is discharged from the discharge pipe 64 to the outside of the sealed container 60.

[0050] 4 and 5 , the effects of the oil separation unit 72 of the first balancer 7 will be described. The flow of refrigerant gas containing refrigerant oil that has flowed into the space above the electric mechanism 4 collides with the blades 73 of the oil separation unit 72, which rotate together with the drive shaft 5, and changes from the axial direction to the radial direction or the rotational direction. This prevents the refrigerant oil from being discharged to the outside of the sealed container 60 via the discharge pipe 64 located above the oil separation unit 72. The refrigerant gas containing refrigerant oil that has flowed into the space above the electric mechanism 4 comes into contact with the lower surfaces of the blades 73 of the oil separation unit 72 from below. Furthermore, the refrigerant gas containing refrigerant oil floating in the space above the electric mechanism 4 comes into contact with the upper surfaces of the blades 73 of the oil separation unit 72.

[0051] Centrifugal force is applied to the refrigerant gas containing refrigerant oil that contacts the surfaces of the vanes 73 of the oil separation unit 72 due to the rotation of the drive shaft 5. The refrigerant oil has a higher specific gravity than the refrigerant gas. Therefore, the refrigerant oil is separated from the refrigerant gas by centrifugal force and flows radially outward along the surfaces of the vanes 73. The refrigerant gas containing refrigerant oil that contacts the surfaces of the vanes 73 of the oil separation unit 72 flows radially outward along the surfaces of the vanes 73. At the same time, the refrigerant gas flows from the front portion 73a to the rear portion 73b of the vanes 73 along the inclined surfaces, as shown by the arrows in FIG. 6 . The refrigerant oil that flows from the radially inward to the radially outward and from the top to the bottom along the inclined surfaces of the vanes 73 of the oil separation unit 72 is blown toward the inner circumferential wall of the sealed container 60. The refrigeration oil blown toward the inner peripheral wall of the sealed container 60 flows along the inner peripheral wall of the sealed container 60 toward the bottom and is returned to the oil reservoir at the bottom of the sealed container 60.

[0052] Here, the vanes 73 are not simply horizontal but have a triangular roof shape. As a result, the refrigerant converges directly below the contact point between the front portion 73a and the rear portion 73b, and the shape makes it easier for the refrigerant to change its flow path in the radial direction rather than the rotational direction. Considering the circulation path of the refrigeration oil inside the sealed container 60, it is desirable for the refrigeration oil to move toward the inner wall of the sealed container 60, that is, in the radial direction. In the compressor 100, the vanes 73 have a triangular roof shape, which allows the refrigeration oil adhering to the vanes 73 to be guided in the radial direction, which is effective for oil separation.

[0053] [Operation and Effect of Compressor 100 of First Embodiment] As described above, the compressor 100 of the first embodiment includes a sealed container 60 that forms an outer shell, and an electric mechanism 4 that is disposed inside the sealed container 60 and has a stator 2 and a rotor 3 disposed inside the stator 2, and that rotates the rotor 3. The compressor 100 includes a drive shaft 5 that passes through the rotor 3 of the electric mechanism 4 and rotates together with the rotor 3, and a compression mechanism 10 that is disposed inside the sealed container 60 and fixed to the drive shaft 5, and compresses the refrigerant by the rotation of the drive shaft 5. The compressor 100 includes a first balancer 7 that is fixed to an end of the rotor 3 on the opposite side to the compression mechanism 10 in the axial direction S of the drive shaft 5, rotates together with the drive shaft 5, and suppresses imbalance in the compression mechanism 10. The first balancer 7 includes a cylindrical portion 71 that is passed around the outer periphery of the drive shaft 5, and an oil separation portion 72 that separates the refrigerant from the refrigeration oil and has a plurality of blades 73 that are provided so as to radiate from the outer periphery of the cylindrical portion 71. The first balancer 7 has a center of gravity that does not coincide with the axis C of the drive shaft 5.

[0054] According to the above configuration, the compressor 100 is provided with the first balancer 7, which is provided with an oil separation section 72 having a plurality of blades 73. The first balancer 7 has a center of gravity at a position that does not coincide with the axis C of the drive shaft 5, and in addition to functioning as a balancer, the first balancer 7 is also provided with an oil separation function by the oil separation section 72. In this way, by being provided with the first balancer 7 that performs both oil separation and balance adjustment, the compressor 100 can perform oil separation and suppress imbalance in the compression mechanism section 10.

[0055] Furthermore, since the first balancer 7 has both a balancing function and an oil separation function, it is possible to avoid a situation where a balancer cannot be installed when attempting to install a new balancer in a compressor equipped with an oil separation section having multiple blades, as in the past. Also, because the first balancer 7 has both a balancing function and an oil separation function, the number of parts in the compressor 100 can be reduced compared to when these functions are configured as separate parts.

[0056] In the compressor 100, the lengths of the plurality of blades 73 in the radial direction R of the drive shaft 5 are different for some or all of them. Alternatively, in the compressor 100, at least one of the intervals in the circumferential direction CD of the drive shaft 5 between two adjacent blades 73 among the plurality of blades 73 is different from the other intervals, or all of the intervals are different from each other. Alternatively, in the compressor 100, at least one of the plurality of blades 73 has a shape in which the plate thickness increases from the radially inner side to the radially outer side. Alternatively, in the compressor 100, at least one of the plurality of blades 73 has a shape in which the plate thickness decreases from the radially inner side to the radially outer side.

[0057] With the above-described configuration, the compressor 100 can be configured so that the first balancer 7 has a center of gravity at a position that does not coincide with the axis C of the drive shaft 5 .

[0058] Each of the multiple blades 73 of the oil separation section 72 has a front portion 73a formed in a plate shape on the forward side in the rotational direction DR of the first balancer 7, and a rear portion 73b formed integrally with the front portion 73a, located on the rearward side of the rotational direction DR than the front portion 73a, and formed in a plate shape inclined relative to the front portion 73a.

[0059] With the above-described configuration, the compressor 100 can separate the refrigerant and the refrigerating machine oil in the oil separation section 72 .

[0060] The compressor 100 includes a second balancer 8 that is fixed to an end of the rotor 3 on the compression mechanism 10 side in the axial direction S, rotates together with the drive shaft 5, and suppresses imbalance in the compression mechanism 10. The first balancer 7 and the second balancer 8 are located on opposite sides of the axis C of the drive shaft 5 in the radial direction R of the drive shaft 5.

[0061] With the above-described configuration, the compressor 100 can suppress imbalance in the compression mechanism 10 .

[0062] The radial distance R between the center of gravity of the first balancer 7 and the axis C of the drive shaft 5 is the same as the radial distance R between the center of gravity of the second balancer 8 and the axis C of the drive shaft 5, and the weight of the first balancer 7 is smaller than the weight of the second balancer 8.

[0063] With the above-described configuration, the compressor 100 can suppress imbalance in the compression mechanism 10 .

[0064] The radial distance R between the center of gravity of the first balancer 7 and the axis C of the drive shaft 5 is shorter than the radial distance R between the center of gravity of the second balancer 8 and the axis C of the drive shaft 5, and the weight of the first balancer 7 and the weight of the second balancer 8 are the same.

[0065] With the above-described configuration, the compressor 100 can suppress imbalance in the compression mechanism 10 .

[0066] Embodiment 2 Embodiment 2 differs from Embodiment 1 in the configuration of the oil separation section 72 of the first balancer 7. In Embodiment 2, the oil separation section 72 of the first balancer 7 has a configuration in which the front portions 73a of the blades 73 have smaller air resistance during rotation than the rear portions 73b. The following description will focus on the configuration in Embodiment 2 that differs from Embodiment 1, and the configuration not described in Embodiment 2 is the same as that in Embodiment 1.

[0067] FIG. 10 is a cross-sectional view of the blade 73 of the first balancer 7 according to the second embodiment. FIG. 11 is a cross-sectional view of another example of the blade 73 of the first balancer 7 according to the second embodiment. The oil separation section 72 of the first balancer 7 according to the second embodiment has a configuration in which the front portion 73a of the blade 73 has smaller air resistance during rotation than the rear portion 73b. Specifically, as shown in FIG. 10 , the length L1 of the front portion 73a of the blade 73 in the circumferential direction CD is shorter than the length L2 of the rear portion 73b of the blade 73 in the circumferential direction CD. As another configuration example, the blade 73 may have a shape in which the front portion 73a extends parallel to the direction of rotation DR and the rear portion 73b is inclined, as shown in FIG.

[0068] [Operation and Effects of Compressor 100 of Second Embodiment] The compressor 100 of the second embodiment has the same effects as those of the first embodiment, and also has the following effects due to the above-described configuration of the blades 73 of the oil separation section 72 of the first balancer 7. The compressor 100 has a configuration in which the front portions 73a of the blades 73 have less air resistance during rotation than the rear portions 73b, and this can reduce the load on the electric mechanism 4 that rotates the blades 73 during rotation, resulting in reduced power consumption.

[0069] Third Embodiment The third embodiment relates to the positional relationship between the first balancer 7 and the electric mechanism unit 4. The following description will focus on the configuration of the third embodiment that differs from the first and second embodiments, and the configuration not described in the third embodiment is the same as the first and second embodiments.

[0070] Fig. 12 is a schematic top view illustrating the positional relationship between the first balancer 7 and the electric mechanism unit 4 of the compressor 100 according to the third embodiment. In the first balancer 7 according to the third embodiment, at least one of the plurality of blades 73 of the oil separation unit 72 is formed at a position overlapping with the through hole 3a of the rotor 3 as viewed in the axial direction S. Fig. 12 shows an example in which all of the blades 73 are formed at positions overlapping with the through hole 3a of the rotor 3 as viewed in the axial direction S, but it is sufficient that at least one blade 73 is formed at a position overlapping with the through hole 3a of the rotor 3 as viewed in the axial direction S.

[0071] [Operation and effect of compressor 100 of embodiment 3] The compressor 100 of embodiment 3 has the same effects as those of embodiments 1 and 2 described above, and also has the following effect due to the blades 73 of the oil separation unit 72 being positioned to block the through-hole 3 a of the rotor 3. In the compressor 100, the blades 73 are positioned to block the through-hole 3 a of the rotor 3, so that the refrigerant gas containing refrigerant oil that flows out from the upper opening of the through-hole 3 a collides with the blades 73 of the oil separation unit 72, thereby enhancing the separation effect of the refrigerant oil contained in the refrigerant gas. Therefore, the compressor 100 can more efficiently separate the refrigerant oil from the refrigerant gas containing refrigerant oil that flows out from the through-hole 3 a, compared to a configuration in which the blades 73 are formed in a position other than the position to block the through-hole 3 a of the rotor 3.

[0072] Embodiment 4 Embodiment 4 differs from Embodiments 1 to 3 in the configuration of the first balancer 7. The following description will focus on the configuration in which Embodiment 4 differs from Embodiments 1 to 3, and configurations in which Embodiment 4 is not described are the same as those in Embodiments 1 to 3.

[0073] Fig. 13 is a schematic top view of the first balancer 7 of the compressor 100 according to embodiment 4. Fig. 14 is a schematic side view of the first balancer 7 of the compressor 100 according to embodiment 4. The first balancer 7 of embodiment 4 has a cylindrical portion 71 and an oil separation portion 72, similar to embodiment 1. The first balancer 7 has a plurality of divided balancers 7A divided in the axial direction S. In the illustrated example, the first balancer 7 has three divided balancers 7A. The number of divided balancers 7A is not limited to three, and may be two or more.

[0074] The split balancer 7A has a split cylindrical portion 71A formed by splitting the cylindrical portion 71 in the axial direction S, and one of the three blades 73 that make up the oil separation portion 72, with the one blade 73 fixed to the outer periphery of the split cylindrical portion 71A. The split cylindrical portion 71A has an insertion hole 71Aa that penetrates in the axial direction S. A plurality of the insertion holes 71Aa are formed at intervals in the circumferential direction CD. The number of insertion holes 71Aa is the same as or greater than the number of split balancers 7A that make up the first balancer 7. In this example, the number of insertion holes 71Aa is six. The blade 73 can have any of the shapes described in the above-mentioned Embodiment 1 and Modifications 1 and 2 of Embodiment 1.

[0075] The split balancer 7A has wings 73 on the outer periphery of the split cylindrical portion 71A, so that the center of gravity of the split balancer 7A moves from the center of the split cylindrical portion 71A radially outward toward the wings 73. In this way, each split balancer 7A has a center of gravity at a position shifted radially outward from the center O.

[0076] The multiple split balancers 7A configured as described above are stacked in the axial direction S, so that the insertion holes 71Aa communicate with each other to form a communication hole 74. The first balancer 7 is integrated by inserting fasteners 75 such as rivets or bolts into the communication holes 74. The cylindrical portion 71 of the first balancer 7 is made up of multiple split cylindrical portions 71A, and the oil separation portion 72 of the first balancer 7 is made up of blades 73 provided on each split balancer 7A.

[0077] In this way, the first balancer 7 is configured by stacking multiple split balancers 7A in the axial direction S. The first balancer 7 in Fig. 13 shows an example in which the blades 73 are arranged at equal intervals in the circumferential direction CD when viewed in the axial direction S, but the positions of the blades 73 are not limited to the positions shown. Because the first balancer 7 is divided into multiple split balancers 7A, the positions of the blades 73 of each split balancer 7A in the circumferential direction CD can be set freely.

[0078] [Operations and Effects of the Compressor 100 of Embodiment 4] The compressor 100 of Embodiment 4 has the same effects as those of Embodiments 1 to 3 described above, as well as the following effect. The first balancer 7 of the compressor 100 has a configuration in which multiple split balancers 7A, each having a split cylindrical portion 71A and a blade 73, are stacked. This allows the circumferential CD position of the blade 73 of each split balancer 7A to be freely set. Because the first balancer 7 allows the circumferential CD position of the blade 73 of each split balancer 7A to be freely set, balancers with a variety of center of gravity patterns can be easily configured depending on how the split balancers 7A are stacked. Furthermore, the shape of the split balancer 7A is configured to have a split cylindrical portion 71A and one blade 73, so to speak, a single pattern. Because the compressor 100 allows balancers with a variety of center of gravity patterns to be configured using a single pattern of split balancers 7A, there is no need to prepare multiple types of balancers with different center of gravity patterns. This reduces manufacturing costs by standardizing parts.

[0079] Embodiment 5 Embodiment 5 relates to a configuration that suppresses whirling of the drive shaft 5A and the rotor 3 due to centrifugal forces generated in the first eccentric shaft portion 5a and the second eccentric shaft portion 5b. In Embodiment 5, the configuration of the intermediate shaft portion 5c of the drive shaft 5A differs from that of Embodiments 1 to 4. The following description will focus on the configuration in Embodiment 5 that differs from Embodiments 1 to 4, and the configuration not described in Embodiment 5 is the same as that of Embodiments 1 to 4.

[0080] Fig. 15 is a diagram showing the drive shaft 5A of the compressor 100 according to the fifth embodiment. Fig. 16 is an explanatory diagram of whirling of the drive shaft 5A and the rotor 3 of the compressor 100 according to the fifth embodiment. As shown in Fig. 15 , the intermediate shaft portion 5c of the drive shaft 5A according to the fifth embodiment is divided into two in the axial direction S, and has a first intermediate shaft portion 5c1 and a second intermediate shaft portion 5c2. The first intermediate shaft portion 5c1 is on the first eccentric shaft portion 5a side in the axial direction S, and the second intermediate shaft portion 5c2 is on the second eccentric shaft portion 5b side in the axial direction S. In Fig. 16 , the value in parentheses indicates the amount of imbalance, which will be described later, and the value outside the parentheses indicates the centrifugal force.

[0081] As shown in FIG. 15 , the first intermediate shaft portion 5c1 is eccentric to the axis C1 of the first eccentric shaft portion 5a relative to the axis C of the drive shaft 5A. The second intermediate shaft portion 5c2 is eccentric to the axis C2 of the second eccentric shaft portion 5b relative to the axis C of the drive shaft 5A. In other words, the intermediate shaft portion 5c is eccentric. The intermediate shaft portion 5c is configured such that the unbalance amount of the second intermediate shaft portion 5c2 is smaller than the unbalance amount of the first intermediate shaft portion 5c1. The unbalance amount is defined as the moment around the axis of the drive shaft 5 generated by centrifugal force. The unbalance amount of the first intermediate shaft portion 5c1 is a moment defined by the product of the distance in the radial direction R from the axis C of the drive shaft 5 to the center of gravity of the first intermediate shaft portion 5c1 and the weight of the first intermediate shaft portion 5c1. The amount of unbalance of the second intermediate shaft portion 5c2 is a moment defined by the product of the distance in the radial direction R from the axis C of the drive shaft 5 to the center of gravity of the second intermediate shaft portion 5c2 and the weight of the second intermediate shaft portion 5c2.

[0082] The intermediate shaft portion 5c has the following specific configuration so that the amount of unbalance of the second intermediate shaft portion 5c2 is smaller than the amount of unbalance of the first intermediate shaft portion 5c1: The weight of the second intermediate shaft portion 5c2 is smaller than the weight of the first intermediate shaft portion 5c1. The relationships L1 > L2 and D1 = D2 are satisfied, where D1: diameter of the first intermediate shaft portion 5c1 D2: diameter of the second intermediate shaft portion 5c2 L1: axial length of the first intermediate shaft portion 5c1 L2: axial length of the second intermediate shaft portion 5c2

[0083] The effects of the above configuration will be explained in comparison with Comparative Example 1 and Comparative Example 2. Comparative Example 1 and Comparative Example 2 have a structure in which the intermediate shaft portion 5c is not eccentric. Comparative Example 1 is an example in which whirling of the drive shaft 5 and rotor 3 occurs. Comparative Example 2 is an example in which whirling of the drive shaft 5 and rotor 3 is suppressed more than in Comparative Example 1.

[0084] (Comparative Example 1) Figure 17 is an explanatory diagram of whirling of the drive shaft 5 and rotor 3 in Comparative Example 1. Here, a general balance design will be described with reference to Figure 17. The drive shaft 5 in Comparative Example 1 has the same structure as the drive shaft 5 in the first embodiment, and the intermediate shaft portion 5c is configured not to have eccentricity. In Comparative Example 1, a first balancer 70 and a second balancer 80 are fixed to the rotor 3. The first balancer 70 and the second balancer 80 are semicircular ring-shaped. In Comparative Example 1, the same components as those in the first embodiment are assigned the same reference numerals.

[0085] In the rotary compressor, rotation of the drive shaft 5 generates centrifugal forces in the respective eccentric directions on the first eccentric shaft portion 5a and the second eccentric shaft portion 5b. When the first eccentric shaft portion 5a and the second eccentric shaft portion 5b have eccentricities that are symmetrical with respect to the axis C of the drive shaft 5, centrifugal forces are generated in opposite directions on the first eccentric shaft portion 5a and the second eccentric shaft portion 5b. "Eccentricity that is symmetrical with respect to the axis C of the drive shaft 5" means that the eccentric positions of the first eccentric shaft portion 5a and the second eccentric shaft portion 5b are symmetrical with respect to the axis C of the drive shaft 5. "Eccentricity that is symmetrical with respect to the axis C of the drive shaft 5" means that the eccentric weights of the first eccentric shaft portion 5a and the second eccentric shaft portion 5b are symmetrical with respect to the axis C of the drive shaft 5.

[0086] When the first eccentric shaft portion 5a and the second eccentric shaft portion 5b are symmetrical with respect to the axis C of the drive shaft 5 in terms of the eccentric position and the eccentric weight, the centrifugal force F acting on each of the first eccentric shaft portion 5a and the second eccentric shaft portion 5b is ＲＰ Therefore, in the drive shaft 5, at the center of the axial direction S of the intermediate shaft portion 5c, there is a force (L Ｍ +H Ｃ ) F ＲＰ It can be considered that an equivalent moment MC expressed as follows acts. Ｍis the axial length of the intermediate shaft portion 5c. Ｃ are the axial lengths of the first eccentric shaft portion 5a and the second eccentric shaft portion 5b.

[0087] In Comparative Example 1, the weight of the first balancer 70 and the weight of the second balancer 80 are the same. The first balancer 70 and the second balancer 80 are arranged symmetrically with respect to the axis C of the drive shaft 5. In Comparative Example 1, the unbalance amount of the first balancer 70 (hereinafter referred to as the first unbalance amount) and the unbalance amount of the second balancer 80 (hereinafter referred to as the second unbalance amount) are defined to be the same. As described above, the unbalance amount is defined as the moment around the axis of the drive shaft 5 generated by centrifugal force. The first unbalance amount is a moment defined by the product of the distance in the radial direction R from the axis C of the drive shaft 5 to the center of gravity of the first balancer 70 and the weight of the first balancer 70. The second unbalance amount is a moment defined by the product of the distance in the radial direction R from the axis C of the drive shaft 5 to the center of gravity of the second balancer 80 and the weight of the second balancer 80.

[0088] In a typical balancer design, the first unbalance amount, which is a moment based on the centrifugal force of the first balancer 70, and the second unbalance amount, which is a moment based on the centrifugal force of the second balancer 80, are set to be equal to the equivalent moment MC due to the first eccentric shaft portion 5a and the second eccentric shaft portion 5b. In other words, the first unbalance amount and the second unbalance amount are determined so that the equivalent moment MC can be canceled out by the moments based on the centrifugal forces of the first balancer 70 and the second balancer 80.

[0089] In Comparative Example 1, the first unbalance amount is ＢＷ１ , the second unbalance amount MR ＢＷ２ When the formula (a) is defined as follows, the following formula (a) is satisfied and they are the same. ＢＷ１ and M.R. ＢＷ２ MR ＢＷ The amount of imbalance between the first eccentric shaft portion 5a and the second eccentric shaft portion 5b is set as MR ＲＰ When defined as ＲＰ and M.R. ＢＷ satisfies the following formula (b).

[0090] MR ＢＷ１ =MR ＢＷ２ =MR ＢＷ ... (a) (L Ｍ +H Ｃ ) MR ＲＰ = H ＲＴ MR ＢＷ ...(b)

[0091] Here, H ＲＴ is the axial distance between the center of gravity of the first balancer 70 and the center of gravity of the second balancer 80.

[0092] The above-described general balancer design does not take into consideration the axial distance between the first eccentric shaft portion 5a and the second eccentric shaft portion 5b and the first balancer 70 and the second balancer 80. Meanwhile, the first main shaft portion 5d can be regarded as a cantilever beam with the bearing 11 as a fixed end. In Comparative Example 1, the weights of the first balancer 70 and the second balancer 80 are the same, and the distances of the first balancer 70 and the second balancer 80 from the bearing 11 are different from each other, resulting in a bending moment being generated in the drive shaft 5. As a result, the first main shaft portion 5d deflects in the eccentric direction of the first balancer 70. This deflection causes the center of gravity of the rotor 3 fixed to the first main shaft portion 5d to misalign with the axis C of the drive shaft 5, causing the rotor 3 to whirl.

[0093] (Comparative Example 2) Fig. 18 is an explanatory diagram of whirling of the drive shaft 5 and the rotor 3 in Comparative Example 2. In the above Comparative Example 1, the first unbalance amount MR ＢＷ１ and the second unbalance amount MR ＢＷ２ The first unbalance amount MR ＢＷ１ and the second unbalance amount MR ＢＷ２ and is asymmetrical with respect to the axis C of the drive shaft 5, and the first unbalance amount MR ＢＷ１ is the second unbalance amount MR ＢＷ２ That is, MR ＢＷ１ <MR ＢＷ２In Comparative Example 2, the weights of the first balancer 70 and the second balancer 81 are different, and the weight of the first balancer 70 is reduced to be less than that of the second balancer 81. In Comparative Example 2, the weight of the first balancer 70 is less than the weight of the second balancer 81, so that the first unbalance amount MR of the first balancer 70 is ＢＷ１ is the second unbalance amount MR of the second balancer 81 ＢＷ２ It is smaller than.

[0094] In Comparative Example 2, the first unbalance amount MR ＢＷ１ is the second unbalance amount MR ＢＷ２ Since the distance is smaller than the distance t1, the deflection of the drive shaft 5 that occurs in the eccentric direction of the first balancer 70 due to the rotation of the drive shaft 5 can be reduced, and the whirling of the rotor 3 can be reduced.

[0095] The effect of reducing the amount of whirling, which will be described later, due to the asymmetry between the first balancer 70 and the second balancer 81 is the first unbalance amount MR ＢＷ１ Second unbalance amount MR ＢＷ２ The amount of whirling depends on the reduction amount from the first unbalance amount MR ＢＷ１ Second unbalance amount MR ＢＷ２ In other words, there is a reduction amount at which the amount of whirling becomes a minimum. Furthermore, the effect of reducing the amount of whirling by making the balancer asymmetrical is ＢＷ２ That is, the first unbalance amount MR when the amount of whirling is at a minimum value also depends on ＢＷ１ Second unbalance amount MR ＢＷ２ The reduction amount from the second imbalance amount MR ＢＷ２ The larger the second unbalance amount MR ＢＷ２ If is small, it is small.

[0096] The amount of whirling is the amount of radial movement of the shaft center due to centrifugal force when the drive shaft 5 rotates. When the drive shaft 5 rotates, the shaft center traces a circular or elliptical locus when viewed in the axial direction. The maximum radius of the locus of the shaft center at the tip of the first main shaft portion 5d is referred to as the amount of whirling here.

[0097] In Comparative Example 2, when the rotation speed of the drive shaft 5 is increased from 130 rps to 160 rps, the increase in rotation speed is 23%, and the centrifugal force that affects whirling increases by 1.51 times.

[0098] The inventors have confirmed that when the relationships of the following formulas (1), (2), and (3) are satisfied, the influence of centrifugal force caused by the increase in rotation speed when the rotation speed of the drive shaft 5 is increased from 130 rps to 160 rps can be suppressed, and the amount of whirling can be improved by 34% or more.

[0099] MR ＢＷ２ =MR ＢＷ (1+a) ...(1) MR ＢＷ１ =MR ＢＷ２ (1-b)...(2) b=0.7a+x, however, 0.2≦x≦1.2...(3)

[0100] Here, MR ＢＷ : Unbalance amount that satisfies the above formula (a) and formula (b) a: MR ＢＷ MR for ＢＷ２ Coefficient representing the rate of increase b: MR ＢＷ２ MR for ＢＷ１ Coefficient representing the rate of decrease

[0101] The inventors have confirmed that, particularly when x = 0.7, it is possible to suppress the amount of whirling even when the rotation speed of the drive shaft 5 is 160 rps to the same level as when it is 130 rps. In other words, the inventors have confirmed that, when x = 0.7, the effect of centrifugal force due to the increase in rotation speed when the rotation speed of the drive shaft 5 is increased from 130 rps to 160 rps is canceled out, and it is possible to suppress the amount of whirling to the same level as when it is 130 rps. Note that, when x = 0.7, MR ＢＷ１ can take either a positive or negative value depending on the values ​​of a and b, but MR ＢＷ１ When the center of gravity of the first eccentric shaft portion 5a is located at the MR ＢＷ１ is a positive value, the center of gravity of the first eccentric shaft portion 5a is on the opposite side of the drive shaft 5 as the center.

[0102] 19 is a graph showing the relationship between the unbalance ratio of the second balancer 81 to the first balancer 70 and the whirling ratio in Comparative Example 2. The horizontal axis represents the unbalance ratio [-] of the second balancer 81 to the first balancer 70. The horizontal axis represents the MR ＢＷ２ / MR ＢＷ１ The case where the horizontal axis is 1 corresponds to the case where b = 0 in formula (2). The vertical axis is the whirl ratio [-] when the whirl amount is the same as the whirl amount of Comparative Example 1 is set to 1. In the example of FIG. 19, when the unbalance amount ratio is 0.585, the whirl ratio is 1, which indicates that the whirl amount is the same as the whirl amount of Comparative Example 1. The whirl amount of Comparative Example 1 is the first unbalance amount MR ＢＷ１ and the second unbalance amount MR ＢＷ２ is the amount of whirling when formulas (a) and (b) are satisfied and are symmetrical with respect to the axis C of the drive shaft 5.

[0103] The graph in FIG. 19 shows the first imbalance amount MR ＢＷ１ This graph plots the unbalance ratio and the whirl ratio for each condition where the imbalance ratio is increased or decreased by a fixed amount. The horizontal axis is expressed as a ratio, so the values ​​on the horizontal axis are discontinuous.

[0104] The horizontal axis represents the second imbalance amount MR. ＢＷ２ The first unbalance amount MR ＢＷ１ When the horizontal axis is at "1.0", the first balancer 70 and the second balancer 81 have the same unbalance amount, and the first balancer 70 and the second balancer 81 are on opposite sides of the axis C of the drive shaft 5 in the radial direction R. As the horizontal axis moves to the left of "1.0", the first unbalance amount MR ＢＷ１ becomes larger, and the unbalance ratio (MR ＢＷ２ / MR ＢＷ１ As the horizontal axis moves to the right of "1.0", the first unbalance amount MR ＢＷ１ becomes smaller, and the unbalance ratio (MR ＢＷ２ / MR ＢＷ１ ) becomes larger.

[0105] When the value on the horizontal axis is a positive value, the centers of gravity of the first balancer 70 and the second balancer 81 are on opposite sides of the axis C of the drive shaft 5 in the radial direction R. When the value on the horizontal axis is a negative value, the first unbalance amount MR ＢＷ１ is reduced until the imbalance on the opposite side of the radial direction R with respect to the axis C of the drive shaft 5 is eliminated. When the value on the horizontal axis is a negative value, the centers of gravity of the first balancer 70 and the second balancer 81 are on the same side of the radial direction R with respect to the axis C of the drive shaft 5. For example, when the horizontal axis is "-2", the amount of imbalance of the first balancer 70 is half that of the second balancer 81, and the centers of gravity of the first balancer 70 and the second balancer 81 are on the same side of the radial direction R with respect to the axis C of the drive shaft 5. When the horizontal axis is "-0.5", the amount of imbalance of the first balancer 70 is twice that of the second balancer 81, and the centers of gravity of the first balancer 70 and the second balancer 81 are on the same side of the radial direction R with respect to the axis C of the drive shaft 5.

[0106] 19, when the unbalance amount ratio is in the range of 2.0 to −0.29, the amount of whirl is improved by approximately 34% compared to the amount of whirl in Comparative Example 1. When the weight ratio of the second balancer 81 to the first balancer 70 is in the range of −2.0 to −0.4, the amount of whirl is improved by 70% compared to the amount of whirl in Comparative Example 1. When the unbalance amount ratio of the second balancer 81 to the first balancer 70 is −0.67, the whirl ratio becomes a minimal value of approximately 0, and the amount of whirl is improved by approximately 100% compared to when the weight ratio of the second balancer 81 to the first balancer 70 is 1.

[0107] According to the above Comparative Examples 1 and 2, the amount of whirling is the first unbalance amount MR ＢＷ１ and the second unbalance amount MR ＢＷ２ It can be seen that the value can be reduced by adjusting the value.

[0108] Next, a comparison will be made between Comparative Example 2 and the compressor 100 of the fifth embodiment. In Comparative Example 2, the intermediate shaft portion 5c does not have eccentricity, whereas in the compressor 100 of the fifth embodiment, the intermediate shaft portion 5c has eccentricity as described above. In the compressor 100 of the fifth embodiment, the first unbalance amount MR ＢＷ１ is the second unbalance amount MR ＢＷ２ , similarly to Comparative Example 2. That is, the compressor 100 of the fifth embodiment corresponds to a configuration in which the intermediate shaft portion 5c is eccentric in addition to the configuration of Comparative Example 2.

[0109] The effect of suppressing the amount of whirling can be enhanced by making the amount of unbalance f of the second intermediate shaft portion 5c2 smaller than the amount of unbalance G-f of the first intermediate shaft portion 5c1 and by increasing the total amount of unbalance G of the first intermediate shaft portion 5c1 and the second intermediate shaft portion 5c2.

[0110] Tests conducted by the present inventors have confirmed that, when f is 0.25 or less and G is 20 or more, the compressor 100 can suppress whirling by 15% or more compared to Comparative Example 2. Fig. 20 shows, as an example, a graph illustrating the whirling suppression effect when f = 0.25 and G = 50.

[0111] FIG. 20 is a graph showing the whirling suppression effect of the compressor 100 of the fifth embodiment, showing the relationship between the rotation speed of the drive shaft 5 and the amount of whirling. The horizontal axis is the rotation speed [rps] of the drive shaft 5A. The vertical axis is the amount of whirling [μm]. (A) of FIG. 20 is a graph of Comparative Example 2, in which the intermediate shaft portion 5c is not eccentric. (B) of FIG. 20 is a graph of the fifth embodiment, in which the intermediate shaft portion 5c is eccentric. (B) of FIG. 20 is a graph in which f=0.25 and G=50.

[0112] As shown in Fig. 20, compressor 100 can suppress an increase in the amount of whirling even when the rotation speed is higher than that of Comparative Example 2. Fig. 20 shows that when the rotation speed is 100 rps or higher, the difference in the amount of whirling is 15% or more between (A) showing Comparative Example 2 and (B) showing Embodiment 5.

[0113] As described in Comparative Example 2, the compressor 100 has an asymmetrical first balancer 7 and a second balancer 8 provided above and below the rotor 3, in other words, an asymmetrical balancer that can suppress whirling of the drive shaft 5A. In addition, during high-speed rotation, the compressor 100 offsets part of the centrifugal force of the rotor 3 by the eccentric weight balance of the first intermediate shaft portion 5c1 and the second intermediate shaft portion 5c2, thereby further suppressing whirling of the drive shaft 5A. In other words, the compressor 100 can improve the effect of the asymmetrical balancer by having the first intermediate shaft portion 5c1 and the second intermediate shaft portion 5c2 of the intermediate shaft portion 5c function as a third balancer and a fourth balancer, so to speak.

[0114] [Operation and Effects of Compressor 100 of Embodiment 5] The compressor 100 of Embodiment 5 has the same effects as those of Embodiments 1 to 4 described above, as well as the following effect. In the compressor 100, the first intermediate shaft portion 5c1 has a first intermediate shaft portion 5c1 on the axial side of the first eccentric shaft portion 5a and a second intermediate shaft portion 5c2 on the axial side of the second eccentric shaft portion 5b. The unbalance amount f of the second intermediate shaft portion 5c2 is smaller than the unbalance amount G-f of the first intermediate shaft portion 5c1. Specifically, the compressor 100 has the relationships L1 > L2 and D1 = D2. The eccentricity amount of the first intermediate shaft portion 5c1 is larger than the eccentricity amount of the second intermediate shaft portion 5c2, and the first intermediate shaft portion 5c1 is eccentric to the same side as the axis C1 of the first eccentric shaft portion 5a. The second intermediate shaft portion 5c2 is eccentric to the same side as the axis C2 of the second eccentric shaft portion 5b.

[0115] With the above configuration, the compressor 100 can offset part of the centrifugal force of the rotor 3 to which the first balancer 7 and the second balancer 8 are fixed by the eccentric weight balance of the intermediate shaft portion 5c, thereby further suppressing the whirling of the drive shaft 5A.

[0116] In theory, the greater the number of balancers in a compressor, the higher the operating speed of the compressor can be. Therefore, in the compressor 100 of the fifth embodiment, in addition to the first balancer 7 and the second balancer 8, the intermediate shaft portion 5c of the drive shaft 5A has the above-described configuration, and the intermediate shaft portion 5c has the balancer function as described above, thereby providing a synergistic effect as a configuration advantageous for high-speed operation.

[0117] Embodiment 6 In embodiment 6, the configuration of the intermediate shaft portion 5c of the drive shaft 5B is different from embodiment 5. The following description will focus on the configuration in embodiment 6 that is different from embodiment 5, and the configuration not described in embodiment 6 is the same as embodiment 5.

[0118] FIG. 21 illustrates a drive shaft 5B of a compressor 100 according to a sixth embodiment. Similar to the drive shaft 5A, the drive shaft 5B includes a first intermediate shaft portion 5c1 on the first eccentric shaft portion 5a side and a second intermediate shaft portion 5c2 on the second eccentric shaft portion 5b side in the axial direction S. The unbalance amount f of the second intermediate shaft portion 5c2 is smaller than the unbalance amount G-f of the first intermediate shaft portion 5c1. The first intermediate shaft portion 5c1 is eccentric to the same side as the axis C1 of the first eccentric shaft portion 5a, and the second intermediate shaft portion 5c2 is eccentric to the same side as the axis C2 of the second eccentric shaft portion 5b. The drive shaft 5B differs from the drive shaft 5A of FIG. 15 in that the drive shaft 5B satisfies the relationship L1 = L2 and the relationship D1 > D2. The drive shaft 5B has a configuration in which the relationship L1=L2 and D1>D2 is satisfied, so that the unbalance amount f of the second intermediate shaft portion 5c2 is smaller than the unbalance amount Gf of the first intermediate shaft portion 5c1.

[0119] [Operations and Effects of Compressor 100 of Sixth Embodiment] The compressor 100 of the sixth embodiment can achieve the same operations and effects as the compressor 100 of the fifth embodiment.

[0120] Embodiment 7 In embodiment 7, the configuration of the intermediate shaft portion 5c of the drive shaft 5C differs from embodiment 5. The following description will focus on the configuration in embodiment 7 that differs from embodiments 5 and 6, and the configuration not described in embodiment 7 is the same as in embodiments 5 and 6.

[0121] FIG. 22 is a diagram illustrating a drive shaft 5C of a compressor 100 according to the seventh embodiment. Similar to the drive shafts 5A and 5B, the drive shaft 5C has a configuration in which the unbalance amount f of the second intermediate shaft portion 5c2 is smaller than the unbalance amount G-f of the first intermediate shaft portion 5c1. Similarly to the drive shaft 5B of FIG. 21, the drive shaft 5C has the relationship L1 = L2 and D1 > D2, so that the unbalance amount f of the second intermediate shaft portion 5c2 is smaller than the unbalance amount G-f of the first intermediate shaft portion 5c1. The diameter D1 of the first intermediate shaft portion 5c1 is the same as the diameters of the first main shaft portion 5d and the second main shaft portion 5e. The difference between the drive shaft 5C and the drive shaft 5B of FIG. 21 is that the drive shaft 5C has a configuration in which only the first intermediate shaft portion 5c1 is eccentric, but the second intermediate shaft portion 5c2 is not eccentric. The first intermediate shaft portion 5c1 is eccentric to the same side as the axis C1 of the first eccentric shaft portion 5a. The second intermediate shaft portion 5c2 is not eccentric, and the axis of the second intermediate shaft portion 5c2 coincides with the axis C of the drive shaft 5C.

[0122] [Operations and Effects of Compressor 100 of Seventh Embodiment] The compressor 100 of the seventh embodiment can achieve the same operations and effects as the compressors 100 of the fifth and sixth embodiments.

[0123] Aspects of the present disclosure are described below as appendices. (Appendix 1) A compressor comprising: a sealed container forming an outer shell; an electric mechanism disposed inside the sealed container and having a stator and a rotor disposed inside the stator, and rotating the rotor; a drive shaft passing through the rotor of the electric mechanism and rotating together with the rotor; a compression mechanism disposed inside the sealed container and fixed to the drive shaft, and compressing a refrigerant by rotation of the drive shaft; and a first balancer fixed to an end of the rotor on an axial side of the drive shaft opposite to the compression mechanism, rotating together with the drive shaft, and suppressing imbalance in the compression mechanism, wherein the first balancer comprises: a cylindrical portion passed around the outer periphery of the drive shaft; and an oil separation portion having a plurality of blades arranged radially extending from the outer periphery of the cylindrical portion, and separating the refrigerant and refrigeration oil, (Supplementary Note 2) The compressor according to Supplementary Note 1, wherein some or all of the lengths of the plurality of blades in the radial direction of the drive shaft are different. (Supplementary Note 3) The compressor according to Supplementary Note 1 or Supplementary Note 2, wherein at least one of the intervals in the circumferential direction of the drive shaft between two adjacent blades among the plurality of blades is different from the other intervals, or all of the intervals are different from each other. (Supplementary Note 4) The compressor according to any one of Supplementary Notes 1 to 3, wherein at least one of the plurality of blades has a shape in which the plate thickness increases from the radially inner side to the radially outer side. (Supplementary Note 5) The compressor according to any one of Supplementary Notes 1 to 4, wherein at least one of the plurality of blades has a shape in which the plate thickness decreases from the radially inner side to the radially outer side. (Appendix 6) The compressor according to any one of appendices 1 to 5, wherein the rotor of the electric mechanism has a through hole passing through in the axial direction, and at least one of the plurality of blades of the oil separation section is formed at a position overlapping the through hole when viewed in the axial direction.(Supplementary Note 7) The compressor according to any one of Supplementary Notes 1 to 6, wherein the first balancer includes a plurality of split balancers split in the axial direction, each of the plurality of split balancers having a split cylindrical portion formed by splitting the cylindrical portion in the axial direction and one of the plurality of blades, the one blade being fixed to an outer periphery of the split cylindrical portion, the split cylindrical portion having a plurality of insertion holes penetrating in the axial direction at intervals in the circumferential direction, and the first balancer is integrated with the split balancers by inserting a fastener into a communication hole formed by communicating the insertion holes of the plurality of split balancers in the axial direction. (Supplementary Note 8) The compressor according to any one of Supplementary Notes 1 to 7, wherein each of the plurality of blades in the oil separation section has: a front portion formed in a plate shape on the forward side in the rotational direction of the first balancer, and a rear portion formed integrally with the front portion, located on the rearward side in the rotational direction of the first balancer than the front portion, and formed in a plate shape inclined relative to the front portion. (Supplementary Note 9) The compressor according to Supplementary Note 8, wherein each of the plurality of blades has a configuration in which the front portion has smaller air resistance during rotation than the rear portion. (Supplementary Note 10) The compressor according to Supplementary Note 9, wherein the circumferential length of the front portion of each of the plurality of blades is shorter than the circumferential length of the rear portion. (Supplementary Note 11) The compressor according to Supplementary Note 9, wherein the front portion of each of the plurality of blades extends parallel to the rotation direction of the drive shaft. (Supplementary Note 12) The compressor according to any one of Supplementary Notes 1 to 11, further comprising: a second balancer fixed to an end of the rotor on a compression mechanism side in the axial direction, rotating together with the drive shaft, and suppressing imbalance of the compression mechanism, the first balancer and the second balancer being located on opposite sides of the drive shaft in the radial direction with respect to the axis of the drive shaft.(Supplementary Note 13) The compression mechanism unit includes two compression units in the axial direction, each compression unit including a cylindrical cylinder having a cylinder chamber, and a rolling piston driven by the drive shaft and housed in the cylinder chamber; when one of the two compression units in the axial direction is defined as a first compression unit on the electric mechanism unit side and a second compression unit on the opposite side to the electric mechanism unit side, the drive shaft includes: a first eccentric shaft portion rotatably mounted inside the rolling piston of the first compression unit and eccentric with respect to the axis of the drive shaft; a second eccentric shaft portion rotatably mounted inside the rolling piston of the second compression unit and eccentric with respect to the axis of the drive shaft; and an intermediate shaft portion between the first eccentric shaft portion and the second eccentric shaft portion, the intermediate shaft portion having a first intermediate shaft portion on the side of the first eccentric shaft portion and a second intermediate shaft portion on the side of the second eccentric shaft portion, the first eccentric shaft portion and the second eccentric shaft portion are eccentric to opposite radial sides of the axis of the drive shaft; the center of gravity of the first balancer is on the same side of the axis of the drive shaft as the axis of the second eccentric shaft portion; the center of gravity of the second balancer is on the same side of the axis of the drive shaft as the axis of the first eccentric shaft portion; and, when a moment around the axis of the drive shaft generated by centrifugal force is defined as an unbalance amount, a first unbalance amount of the first balancer is smaller than a second unbalance amount of the second balancer; and an unbalance amount of the second intermediate shaft portion is smaller than an unbalance amount of the first intermediate shaft portion. (Supplementary Note 14) The compressor according to Supplementary Note 13, wherein the radial distance between the center of gravity of the first balancer and the axial center of the drive shaft is the same as the radial distance between the center of gravity of the second balancer and the axial center of the drive shaft, and the weight of the first balancer is less than the weight of the second balancer. (Supplementary Note 15) The compressor according to Supplementary Note 13, wherein the radial distance between the center of gravity of the first balancer and the axial center of the drive shaft is shorter than the radial distance between the center of gravity of the second balancer and the axial center of the drive shaft, and the weight of the first balancer is the same as the weight of the second balancer. (Supplementary Note 16) The first imbalance amount is MR. ＢＷ１ , the second imbalance amount MR ＢＷ２When the above definition is given, the unbalance amount MR that satisfies the formula (a) and the formula (b) is ＢＷ The compressor according to any one of Supplementary Note 13 to Supplementary Note 15, wherein the relationships of the formulas (1), (2), and (3) are satisfied using MR ＢＷ１ =MR ＢＷ２ =MR ＢＷ ... (a) (L Ｍ +H Ｃ ) MR ＲＰ = H ＲＴ MR ＢＷ ...(b) where L Ｍ : Length H of the intermediate shaft portion in the axial direction Ｃ : the length in the axial direction of each of the first eccentric shaft portion and the second eccentric shaft portion, H ＲＴ MR: the distance in the axial direction between the center of gravity of the first balancer and the center of gravity of the second balancer ＢＷ２ =MR ＢＷ (1+a)...(1) MR ＢＷ１ =MR ＢＷ２ (1-b) (2) b = 0.7a + x, where 0.2≦x≦1.2 (3) where a: MR ＢＷ MR for ＢＷ２ Coefficient representing the rate of increase b: MR ＢＷ２ MR for ＢＷ１(Supplementary Note 17) The compressor according to Supplementary Note 16, wherein x in formula (3) is 0.7. (Supplementary Note 18) The compressor according to any one of Supplementary Notes 13 to 17, wherein the axial length of the first intermediate shaft portion is longer than the axial length of the second intermediate shaft portion, and wherein the diameter of the first intermediate shaft portion is the same as the diameter of the second intermediate shaft portion. (Supplementary Note 19) The compressor according to any one of Supplementary Notes 13 to 17, wherein the axial length of the first intermediate shaft portion is the same as the axial length of the second intermediate shaft portion, and wherein the diameter of the first intermediate shaft portion is larger than the diameter of the second intermediate shaft portion, the first intermediate shaft portion is eccentric to the same side as the first eccentric shaft portion, and the second intermediate shaft portion is eccentric to the same side as the second eccentric shaft portion. (Supplementary Note 20) The compressor according to any one of Supplementary Notes 13 to 17, wherein the axial length of the first intermediate shaft portion and the axial length of the second intermediate shaft portion are the same, and the diameter of the first intermediate shaft portion is larger than the diameter of the second intermediate shaft portion, the first intermediate shaft portion is eccentric to the same side as the first eccentric shaft portion, and the axis of the second intermediate shaft portion coincides with the axis of the drive shaft.

[0124] DESCRIPTION OF SYMBOLS 2 Stator, 3 Rotor, 3a Through hole, 4 Electric mechanism section, 5 Drive shaft, 5A Drive shaft, 5B Drive shaft, 5C Drive shaft, 5D Drive shaft, 5a First eccentric shaft section, 5b Second eccentric shaft section, 5c Intermediate shaft section, 5c1 First intermediate shaft section, 5c2 Second intermediate shaft section, 5d First main shaft section, 5e Second main shaft section, 7 First balancer, 7A Split balancer, 8 Second balancer, 8a Communication hole, 10 Compression mechanism section, 10A First compression section, 10B Second compression section, 11 Bearing, 12 Bearing, 13 Bearing boss section, 14 End plate section, 14a Discharge port, 14b Discharge port, 15 Intermediate partition plate, 21 Cylinder, 22 Rolling piston, 31 Cylinder, 32 Rolling piston, 51d Protrusion, 60 Sealed container, 62 Suction pipe, 63 suction pipe, 64 discharge pipe, 64a suction port, 70 first balancer, 71 cylindrical portion, 71A divided cylindrical portion, 71Aa insertion hole, 71a through hole, 72 oil separation portion, 73 blade, 73a front portion, 73b rear portion, 74 communication hole, 75 fastener, 80 second balancer, 81 second balancer, 100 compressor, C axial center, C1 axial center, C2 axial center, CD circumferential direction, DR rotational direction, FRP centrifugal force, G total unbalance amount, G-f unbalance amount, G1 center of gravity, G2 center of gravity, MC equivalent moment, MR ＢＷ１ First unbalance amount, MR ＢＷ２ Second imbalance amount, MR ＲＰ Unbalance amount, O: center, R: radial direction, S: axial direction, f: unbalance amount.

Claims

1. A compressor comprising: a sealed container that forms an outer shell; an electric mechanism section that is arranged inside the sealed container and has a stator and a rotor arranged inside the stator, and rotates the rotor; a drive shaft that passes through the rotor of the electric mechanism section and rotates together with the rotor; a compression mechanism section that is arranged inside the sealed container and fixed to the drive shaft, and compresses a refrigerant by rotation of the drive shaft; and a first balancer that is fixed to an end of the rotor on the opposite side of the axial direction of the drive shaft from the compression mechanism section, rotates together with the drive shaft, and suppresses imbalance in the compression mechanism section, wherein the first balancer comprises: a cylindrical section that is passed around the outer periphery of the drive shaft; and an oil separation section that has a plurality of blades that are arranged to spread radially from the outer periphery of the cylindrical section, and separates the refrigerant and refrigeration oil, 2. The compressor according to claim 1, wherein the lengths of the plurality of blades in the radial direction of the drive shaft are all different.

3. A compressor according to claim 1 or claim 2, wherein at least one of the intervals between two adjacent blades in the circumferential direction of the drive shaft is different from the other intervals, or all of the intervals are different from each other.

4. A compressor according to any one of claims 1 to 3, wherein at least one of the plurality of blades has a shape in which the plate thickness increases from the radially inner side to the radially outer side.

5. A compressor according to any one of claims 1 to 4, wherein at least one of the plurality of blades has a shape in which the plate thickness decreases from the radially inner side to the radially outer side.

6. A compressor as claimed in any one of claims 1 to 5, wherein the rotor of the electric mechanism has a through hole passing through in the axial direction, and at least one of the plurality of blades of the oil separation section is formed in a position overlapping the through hole when viewed in the axial direction.

7. A compressor as claimed in any one of claims 1 to 6, wherein the first balancer includes a plurality of split balancers split in the axial direction, each of the plurality of split balancers having a split cylindrical portion formed by splitting the cylindrical portion in the axial direction and one of the plurality of blades, with the one blade fixed to the outer periphery of the split cylindrical portion, the split cylindrical portion having a plurality of insertion holes penetrating in the axial direction and spaced apart circumferentially, and the first balancer is integrated by inserting a fastener into a communication hole formed by communicating the insertion holes of the plurality of split balancers in the axial direction.

8. A compressor as claimed in any one of claims 1 to 7, wherein each of the plurality of vanes of the oil separation section has a front section formed in a plate shape on the forward side in the rotational direction of the first balancer, and a rear section formed integrally with the front section, positioned on the rearward side of the rotational direction relative to the front section, and formed in a plate shape inclined relative to the front section.

9. A compressor according to claim 8, wherein each of said plurality of blades has a configuration in which the front portion has smaller air resistance during rotation than the rear portion.

10. A compressor according to claim 9, wherein the circumferential length of the front portion of each of said plurality of blades is shorter than the circumferential length of the rear portion.

11. A compressor according to claim 9, wherein the front portion of each of said plurality of blades extends parallel to the direction of rotation of said drive shaft.

12. A compressor as claimed in any one of claims 1 to 11, further comprising a second balancer fixed to the end of the rotor on the compression mechanism side in the axial direction, rotating together with the drive shaft, and suppressing imbalance in the compression mechanism, wherein the first balancer and the second balancer are located on opposite sides of the drive shaft in the radial direction relative to the axial center of the drive shaft.

13. The compression mechanism comprises two compression sections in the axial direction, each compression section comprising a cylindrical cylinder having a cylinder chamber, and a rolling piston driven by the drive shaft and housed in the cylinder chamber; when the one of the two compression sections in the axial direction closest to the electric mechanism is defined as a first compression section, and the other opposite to the electric mechanism is defined as a second compression section, the drive shaft comprises: a first eccentric shaft section rotatably mounted inside the rolling piston of the first compression section and eccentric with respect to the axis of the drive shaft; a second eccentric shaft section rotatably mounted inside the rolling piston of the second compression section and eccentric with respect to the axis of the drive shaft; and an intermediate shaft section between the first eccentric shaft section and the second eccentric shaft section, the intermediate shaft section having a first intermediate shaft section on the side of the first eccentric shaft section and a second intermediate shaft section on the side of the second eccentric shaft section; the first eccentric shaft section and the second eccentric shaft section are eccentric to opposite radial sides of the axis of the drive shaft; 13. The compressor according to claim 12, wherein the center of gravity of the first balancer is on the same side of the axis of the drive shaft as the axis of the second eccentric shaft portion, the center of gravity of the second balancer is on the same side of the axis of the drive shaft as the axis of the first eccentric shaft portion, and when the moment around the axis of the drive shaft generated by centrifugal force is defined as an unbalance amount, a first unbalance amount of the first balancer is smaller than a second unbalance amount of the second balancer, and an unbalance amount of the second intermediate shaft portion is smaller than an unbalance amount of the first intermediate shaft portion.

14. A compressor according to claim 13, wherein the radial distance between the center of gravity of said first balancer and the axis of said drive shaft is the same as the radial distance between the center of gravity of said second balancer and the axis of said drive shaft, and the weight of said first balancer is less than the weight of said second balancer.

15. A compressor according to claim 13, wherein the radial distance between the center of gravity of the first balancer and the axial center of the drive shaft is shorter than the radial distance between the center of gravity of the second balancer and the axial center of the drive shaft, and the weight of the first balancer is the same as the weight of the second balancer.

16. The first unbalance amount is MR ＢＷ１ , the second imbalance amount MR ＢＷ２ When the above definition is given, the unbalance amount MR that satisfies the formula (a) and the formula (b) is ＢＷ The compressor according to any one of claims 13 to 15, wherein the relationships of formulas (1), (2) and (3) are satisfied using MR ＢＷ１ =MR ＢＷ２ =MR ＢＷ ... (a) (L Ｍ +H Ｃ ) MR ＲＰ = H ＲＴ MR ＢＷ ...(b) where L Ｍ : Length H of the intermediate shaft portion in the axial direction Ｃ : the length in the axial direction of each of the first eccentric shaft portion and the second eccentric shaft portion, H ＲＴ MR: the distance in the axial direction between the center of gravity of the first balancer and the center of gravity of the second balancer ＢＷ２ =MR ＢＷ (1+a)...(1) MR ＢＷ１ =MR ＢＷ２ (1-b) (2) b = 0.7a + x, where 0.2≦x≦1.2 (3) where a: MR ＢＷ MR for ＢＷ２ Coefficient representing the rate of increase b: MR ＢＷ２ MR for ＢＷ１ Coefficient representing the rate of decrease 17. The compressor according to claim 16, wherein x in formula (3) is 0.

7.

18. A compressor as set forth in any one of claims 13 to 17, wherein the axial length of the first intermediate shaft portion is longer than the axial length of the second intermediate shaft portion, and the diameter of the first intermediate shaft portion and the diameter of the second intermediate shaft portion are the same.

19. A compressor as set forth in any one of claims 13 to 17, wherein the axial length of the first intermediate shaft portion and the axial length of the second intermediate shaft portion are the same, and the diameter of the first intermediate shaft portion is larger than the diameter of the second intermediate shaft portion, the first intermediate shaft portion is eccentric to the same side as the first eccentric shaft portion, and the second intermediate shaft portion is eccentric to the same side as the second eccentric shaft portion.

20. A compressor as set forth in any one of claims 13 to 17, wherein the axial length of the first intermediate shaft portion and the axial length of the second intermediate shaft portion are the same, and the diameter of the first intermediate shaft portion is larger than the diameter of the second intermediate shaft portion, the first intermediate shaft portion is eccentric to the same side as the first eccentric shaft portion, and the axis of the second intermediate shaft portion coincides with the axis of the drive shaft.

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