JP4835772B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor.

  In the past, in order to reduce vibration and noise of the rotary compressor, it has been proposed that “a rolling thrust bearing is disposed and fixed as an auxiliary bearing in the vicinity of the auxiliary bearing”. Such a proposal is detailed in, for example, Patent Document 1 (Japanese Patent Laid-Open No. 5-133353).

  However, if an auxiliary bearing for a rolling thrust bearing is further added in addition to the auxiliary bearing, the manufacturing cost is increased. In addition, by providing a secondary bearing, whirling vibration due to bending of the shaft is suppressed compared to when the shaft is cantilevered, but due to the motor excitation force generated by the magnetic attractive force between the rotor and stator of the motor. Vibration and noise will occur. Even in the previous Patent Document 1, as a method of reducing the vibration and noise, for example, increasing the rigidity of the shaft and the bearing is not considered, and there is a problem that vibration and noise are generated by the motor excitation force.

  An object of the present invention is to keep vibration and noise low while maintaining a low manufacturing cost.

  A compressor according to a first invention includes a casing, a compression mechanism, a drive source, a shaft, a main bearing member, and a sub-bearing member. The compression mechanism is accommodated in the casing. The drive source generates power for driving the compression mechanism. The drive source includes a stator and a rotor that is rotatably disposed inside the stator. The shaft is connected to the rotor. The shaft transmits power generated by the drive source to the compression mechanism. The main bearing member is accommodated in the casing. The main bearing member has a main bearing portion. The main bearing portion rotatably supports the shaft. The auxiliary bearing member is disposed at a position facing the main bearing member across the drive source. The auxiliary bearing member has an auxiliary bearing portion and a leg portion. The auxiliary bearing portion rotatably supports the shaft. The leg portion extends radially from the outer peripheral surface of the auxiliary bearing portion to the inner peripheral surface of the casing. Moreover, this leg part has a height dimension larger than a width dimension in the minimum cross-sectional area part. The minimum cross-sectional area portion is a portion where the width dimension is minimum in the portion where the height dimension is minimum. The height dimension is the thickness of the leg in the vertical direction. The width dimension is the width of the leg portion in plan view.

  In a compressor that has only a main bearing member and a sub-bearing member, a vibration mode in which the shaft is bow-shaped with the main bearing and sub-bearing as fulcrums due to the magnetic attraction between the rotor and stator of the drive source. Vibrate. In order to suppress this vibration mode, for example, increase the rigidity of the shaft by changing the material of the shaft or increasing the diameter, etc., or increase the rigidity of the main bearing or sub-bearing by the same method. Is effective. However, simply changing the material or increasing the thickness increases the cost, so it is necessary to increase the rigidity efficiently.

  In this compressor, the leg portion of the auxiliary bearing member has a height dimension larger than a width dimension at the minimum cross-sectional area portion. For this reason, in this compressor, the cross-sectional secondary moment with respect to the X-axis extending in the horizontal direction in the leg portion is larger than the cross-sectional secondary moment with respect to the Z-axis extending in the vertical direction. That is, in this compressor, the support rigidity of the shaft can be improved. Therefore, in this compressor, vibration and noise can be suppressed low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to the bending in the vertical direction rather than in the horizontal direction, so that the bow-like vibration mode of the shaft is suppressed and vibration and noise due to the motor excitation force are efficiently suppressed. Can be kept low.

  The compressor which concerns on 2nd invention is a compressor which concerns on 1st invention, Comprising: Three or four legs are provided.

  For this reason, in this compressor, vibration can be dispersed moderately while suppressing the manufacturing cost.

  A compressor according to a third aspect is the compressor according to the first aspect or the second aspect, wherein the stator is fixed to the casing at least at the same position as the fixed position of the leg with respect to the casing in plan view. The

  In this compressor, the stator is fixed to the casing at least at the same position as the fixed position of the legs with respect to the casing in plan view. For this reason, in this compressor, the rigidity of a casing can be improved and a vibration and a noise can be suppressed.

  A compressor according to a fourth aspect of the present invention is the compressor according to the first or second aspect of the present invention, wherein the stator has a plurality of concentrated winding coils.

  In this compressor, the stator of the electric motor has a plurality of concentrated winding coils. For this reason, in this compressor, a coil end can be made small compared with a distributed winding coil. Therefore, in this compressor, the distance between the main bearing member and the auxiliary bearing member can be shortened. Therefore, in this compressor, the support rigidity of the shaft can be improved. As a result, this compressor can suppress vibration.

  A compressor according to a fifth aspect of the invention is the compressor according to the fourth aspect of the invention, further comprising an oil separation plate. The oil separation plate is attached to the lower part of the auxiliary bearing member. In addition, it is preferable that this oil separation board is attached to the lowest end of a sub bearing member.

  For this reason, in this compressor, even when the auxiliary bearing member is far from the oil level, the oil separation plate can be as close as possible to the oil level of the oil reservoir. Therefore, this compressor can maintain the oil separation function well.

  The compressor which concerns on 6th invention is a compressor which concerns on 4th invention, Comprising: The fixed position with respect to a casing has a leg part in the height range of a subbearing member.

  For this reason, in this compressor, the rigidity of the auxiliary bearing member can be improved. Therefore, in this compressor, the vibration of the legs can be suppressed.

A compressor according to a seventh aspect of the present invention is the compressor according to any one of the first to sixth aspects of the present invention, wherein the leg portion has a Z-direction secondary moment with respect to the X axis extending in the horizontal direction extending in the vertical direction. It is larger than the cross-sectional second moment with respect to the axis.

  In this compressor, the leg portion of the auxiliary bearing member has a cross-sectional secondary moment with respect to the X axis extending in the vertical direction and a cross-sectional secondary moment with respect to the Z axis extending in the vertical direction. For this reason, in this compressor, the support rigidity of the shaft can be improved. Therefore, in this compressor, vibration and noise can be suppressed low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to the bending in the vertical direction rather than in the horizontal direction, so that the bow-like vibration mode of the shaft is suppressed and vibration and noise due to the motor excitation force are efficiently suppressed. Can be kept low.

  In the compressor according to the first aspect of the invention, the cross-sectional secondary moment with respect to the X axis extending in the horizontal direction at the leg portion is larger than the cross-sectional secondary moment with respect to the Z axis extending in the vertical direction. That is, in this compressor, the support rigidity of the shaft can be improved. Therefore, in this compressor, vibration and noise can be suppressed low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to the bending in the vertical direction rather than in the horizontal direction, so that the bow-like vibration mode of the shaft is suppressed and vibration and noise due to the motor excitation force are efficiently suppressed. Can be kept low.

  In the compressor according to the second aspect of the present invention, vibration can be appropriately dispersed while suppressing the manufacturing cost.

  In the compressor which concerns on 3rd invention, the rigidity of a casing can be improved and a vibration and a noise can be suppressed.

  In the compressor according to the fourth aspect of the present invention, the coil end can be made smaller than the distributed winding coil. Therefore, in this compressor, the distance between the main bearing member and the auxiliary bearing member can be shortened. Therefore, in this compressor, the support rigidity of the shaft can be improved. As a result, this compressor can suppress vibration.

  In the compressor according to the fifth aspect of the invention, the oil separation plate can be brought as close as possible to the oil level of the oil reservoir even when the auxiliary bearing member is far from the oil level. Therefore, this compressor can maintain the oil separation function well.

  In the compressor according to the sixth aspect of the invention, the rigidity of the auxiliary bearing member can be improved. Therefore, in this compressor, the vibration of the legs can be suppressed.

  In the compressor according to the seventh aspect of the invention, the support rigidity of the shaft can be improved. Therefore, in this compressor, vibration and noise can be suppressed low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to the bending in the vertical direction rather than in the horizontal direction, so that the bow-like vibration mode of the shaft is suppressed and vibration and noise due to the motor excitation force are efficiently suppressed. Can be kept low.

It is a longitudinal section of a scroll compressor concerning one embodiment of the present invention. It is a cross-sectional view of a scroll compressor according to an embodiment of the present invention. It is a top view of the lower main bearing of the scroll compressor concerning one embodiment of the present invention. It is AA sectional drawing of the lower main bearing shown by FIG. FIG. 4 is a bottom view of the lower main bearing shown in FIG. 3. It is a figure showing the vibration mode of the crankshaft of the scroll compressor which concerns on one Embodiment of this invention. It is a comparison figure of the noise characteristic between the scroll compressor concerning one embodiment of the present invention, and a comparative example.

  A high / low pressure dome type scroll compressor 1 according to an embodiment of the present invention constitutes a refrigerant circuit together with an evaporator, a condenser, an expansion mechanism, and the like, and refrigerants (such as a fluorocarbon refrigerant and a carbon dioxide refrigerant) in the refrigerant circuit. 1), and mainly includes a sealed dome-shaped casing 10, a scroll compression mechanism 15, a crankshaft 17, a drive motor 16, a lower main bearing 60, oil, as shown in FIG. 1. It consists of a separation plate 70, a suction pipe 19 and a discharge pipe 20. Hereinafter, the components of the high / low pressure dome type scroll compressor 1 will be described in detail. In the present embodiment, as shown in FIG. 1, the horizontal direction is the X axis and the vertical direction is the Z axis.

<Details of components of high-low pressure dome type scroll compressor>
(1) Casing The casing 10 is comprised from the trunk | drum casing part 11, the upper wall part 12, and the bottom wall part 13, as FIG. 1 shows. The trunk | drum casing part 11 is a substantially cylindrical pressure | voltage resistant member. The upper wall portion 12 has a bowl shape and covers the upper end of the trunk casing portion 11. The bottom wall portion 13 has a bowl shape and covers the lower end of the trunk casing portion 11. The casing 10 mainly contains a scroll compression mechanism 15, a crankshaft 17, a drive motor 16, a lower main bearing 60, and an oil separation plate 70. In the present embodiment, the drive motor 16 is disposed below the scroll compression mechanism 15. And the scroll compression mechanism 15 and the drive motor 16 are connected by the crankshaft 17 arrange | positioned so that the inside of the casing 10 may be extended in an up-down direction.

(2) Scroll compression mechanism As shown in FIG. 1, the scroll compression mechanism 15 mainly includes a housing 23, a fixed scroll 24, a movable scroll 26, and an Oldham link 39. Hereinafter, the components of the scroll compression mechanism 15 will be described in detail.

a) Housing The housing 23 is press-fitted and fixed to the body casing portion 11 over the entire outer circumferential surface in the circumferential direction. That is, the body casing part 11 and the housing 23 are in close contact with each other in an airtight manner over the entire circumference. For this reason, the inside of the casing 10 is partitioned into two spaces by the housing 23. In the high and low pressure dome type scroll compressor 1 according to the present embodiment, the space above the housing 23 is in a low pressure state and the space below the housing 23 is in a high pressure state during operation. Further, the housing 23 is disposed so that the upper end surface thereof is in close contact with the lower end surface of the fixed scroll 24, and the fixed scroll 24 is fastened and fixed by bolts (not shown). Further, the housing 23 is formed with a housing recess 31 and a main bearing portion 32. The housing recess 31 is recessed in the upper center of the housing. A bearing portion 26 c (described later) of the movable scroll 26 and an eccentric shaft portion 17 a (described later) of the crankshaft 17 are disposed in the housing recess 31. The main bearing portion 32 is formed downward from the lower center. A bearing hole 33 penetrating in the vertical direction is formed in the main bearing portion 32, and the main shaft portion 17 b of the crankshaft 17 is rotatably fitted in the bearing hole 33 via a slide bearing 34.

b) Fixed Scroll The fixed scroll 24 is a member arranged in close contact with the upper portion of the housing 23. As shown in FIG. 1, the fixed scroll 24 mainly includes an end plate 24a, a spiral (involute) wrap 24b, and an outer periphery. It is comprised from the wall 24c.

  A discharge passage 41 and an enlarged recess 42 are formed in the end plate 24a. The discharge passage 41 is formed to extend in the vertical direction at the central portion of the end plate 24a, and communicates with the compression chamber 40 (described later). The enlarged recess 42 is formed so as to open on the upper surface of the end plate 24 a and communicates with the discharge passage 41. Then, a lid 44 is fastened and fixed to the end plate 24a with bolts 44a so as to close the enlarged recess 42. By covering the enlarged recess 42 with the lid body 44 in this way, an expansion chamber, i.e., a muffler space 45 is formed to mute the operation sound of the scroll compression mechanism 15. Note that the fixed scroll 24 and the lid 44 are sealed by being brought into close contact with each other via a gasket (not shown).

  The wrap 24b is formed below the end plate 24a.

  The outer peripheral wall 24c extends below the fixed scroll 24 so as to surround the wrap 24b.

c) Movable Scroll As shown in FIG. 1, the movable scroll 26 mainly includes an end plate 26a, a spiral (involute) wrap 26b, a bearing portion 26c, and a groove portion 26d.

  The wrap 26b is formed on the upper side of the end plate 26a. The wrap 26b is engaged with the wrap 24b of the fixed scroll 24. As a result, a compression chamber 40 is formed between the contact portions of both wraps 24b and 26b.

  The bearing portion 26c is formed below the end plate 26a. The eccentric shaft portion 17a of the crankshaft 17 is fitted into the bearing portion 26c.

  The groove 26d is formed at both ends of the end plate 26a. Note that the movable scroll side key portion of the Oldham link 39 (described later) is fitted into the groove portion 26d. The housing-side key portion of the Oldham link 39 is fitted into a groove provided in the housing 23. That is, the movable scroll 26 is supported by the housing 23 through the Oldham link 39 so as to revolve freely, and revolves within the housing 23 without rotating by the rotation of the crankshaft 17. As the movable scroll 26 revolves, the volume between the wraps 24b and 26b contracts toward the center, and the refrigerant is compressed.

d) Oldham link The Oldham link 39 is a member for preventing the rotational movement of the movable scroll 26, and the movable scroll side key portion is fitted into the groove portion 26 d of the movable scroll 26, and the housing side key portion is the Oldham of the housing 23. It is inserted into a groove (not shown). The Oldham groove is an oval groove and is disposed at a position facing each other in the housing 23.

(3) Crankshaft As shown in FIG. 1, the crankshaft 17 is a substantially cylindrical integrally formed component, and mainly includes an eccentric shaft portion 17 a, a main shaft portion 17 b, a balance weight portion 17 c, and a countershaft portion 17 d. It is composed of The eccentric shaft portion 17 a is accommodated in the bearing portion 26 c of the movable scroll 26. The main shaft portion 17 b is accommodated in the bearing hole 33 of the housing 23 via the slide bearing 34. The auxiliary shaft portion 17d is accommodated in a bearing hole of the lower main bearing 60 (described later).

(4) Drive Motor The drive motor 16 is a brushless DC motor in the present embodiment, and mainly includes a stator 51 and a rotor 52.

  The stator 51 is an annular body, and copper wires are concentratedly wound around each of a plurality of tooth portions (not shown). A coil end 53 is formed above and below the tooth portion. In the stator 51, the coil end 53 is smaller than the distributed winding coil. Further, as shown in FIGS. 1 and 2, the stator 51 is provided with nine core cuts 55 at equal intervals on the outer peripheral portion. That is, the stator 51 has a shape like a spur gear. The stator 51 is press-fitted and fixed to the inner wall surface of the casing 10.

  The rotor 52 is rotatably accommodated inside the stator 51 with a slight gap (air gap passage). The rotor 52 is drivingly connected to the movable scroll 26 of the scroll compression mechanism 15 via the crankshaft 17.

(5) Lower Main Bearing The lower main bearing 60 is disposed below the drive motor 16 as shown in FIG. And this lower main bearing 60 is mainly comprised from the subbearing part 61 and the leg part 62, as FIG. 3-FIG. 5 show. The auxiliary bearing portion 61 rotatably supports the auxiliary shaft portion 17d of the crankshaft 17. Three leg portions 62 are formed and are fixed to the body casing portion 11 by spot welding so as not to overlap the core cut 55 of the stator 51 when viewed along the rotation axis of the rotor 52. Further, in the present embodiment, the spot welding position is within the height range of the lower main bearing 60. Further, as shown in FIG. 4, the leg portion 62 has a portion where the height dimension H which is the thickness in the vertical direction (Z-axis direction) is minimized. Further, as shown in FIG. 3, the leg portion 62 has a portion where the width dimension W, which is the width in plan view, is the smallest in the portion where the height dimension H is the smallest. Therefore, as shown in FIGS. 3 and 4, the leg portion 62 has a minimum cross-sectional area portion R that is a portion having a minimum cross-sectional area, and the height dimension H is 27 mm in the minimum cross-sectional area portion R. The width dimension W is 25 mm, and the height dimension H is designed to be larger than the width dimension W. Further, the lower main bearing 60 is disposed closer to the drive motor side than in the case where a stator having distributed winding coils is applied. This is because the coil end of the stator having the concentrated winding coil is smaller than the coil end of the stator having the distributed winding coil.

(6) Oil separation plate The oil separation plate 70 is a substantially semicircular plate member. The oil separation plate 70 is attached slightly below the center point in the height direction of the lower main bearing 60 as shown in FIGS.

(7) Suction Pipe The suction pipe 19 is for guiding the refrigerant in the refrigerant circuit to the scroll compression mechanism 15 and is fitted into the upper wall portion 12 of the casing 10 in an airtight manner. The suction pipe 19 has an inner end fitted into the fixed scroll 24.

(8) Discharge pipe The discharge pipe 20 is for discharging the refrigerant in the casing 10 into the refrigerant circuit, and is fitted into the body casing portion 11 of the casing 10 in an airtight manner.

<Characteristics of high-low pressure dome type scroll compressor according to this embodiment>
(1)
In the lower main bearing 60 according to the embodiment of the present invention, the leg portion 62 is designed such that the height dimension H is larger than the width dimension W in the minimum cross-sectional area portion R. For this reason, in the high-low pressure dome-type scroll compressor 1 according to the present embodiment, the cross-sectional secondary moment with respect to the X-axis extending in the horizontal direction is larger than the cross-sectional secondary moment with respect to the Z-axis extending in the vertical direction. . Therefore, in this high / low pressure dome type scroll compressor 1, the support rigidity of the crankshaft 17 can be improved. Therefore, in this high / low pressure dome type scroll compressor 1, vibration and noise can be kept low. Further, in this high / low pressure dome type scroll compressor 1, the auxiliary bearing 61 has higher rigidity against bending in the vertical direction than in the horizontal direction, so that the crankshaft 17 is supported by the main bearing 32 and the auxiliary bearing 61. The vibration mode that vibrates like a bow can be suppressed, and the vibration and noise caused by the motor excitation force can be efficiently reduced. A bow-like vibration mode M of the crankshaft 17 is shown in FIG. This vibration mode M is generated by a magnetic attractive force between the rotor 52 of the drive motor 16 and the stator 51.

  Noise characteristics with respect to frequency of the high and low pressure dome type scroll compressor 1 having the lower main bearing 60 according to the embodiment of the present invention, and a compressor not having the lower main bearing 60 according to the embodiment of the present invention (comparative example) FIG. 7 shows a comparison diagram of noise characteristics with respect to the frequency of). In FIG. 7, the noise level is a measured value under test conditions in which the rotation speed of the motor is 90 rps. As shown in FIG. 7, in the high and low pressure dome type scroll compressor 1 according to the embodiment of the present invention, the noise level in the low order component (100 to 315 Hz) of the rotational frequency component of the crankshaft 17 is in the comparative example. Compared to low. Further, in the high / low pressure dome type scroll compressor 1 according to the embodiment of the present invention, a frequency (resonance phenomenon caused by the fact that the eigenvalue of the rotation frequency of the crankshaft 17 coincides with the frequency of the motor basic excitation force) ( The noise level at 500 to 630 Hz is also kept low compared to the comparative example.

(2)
In the lower main bearing 60 according to the embodiment of the present invention, three leg portions 62 are provided. For this reason, in the high and low pressure dome type scroll compressor 1 which concerns on this Embodiment, a vibration can be disperse | distributed moderately, suppressing processing cost.

(3)
In the lower main bearing 60 according to the embodiment of the present invention, the leg portion 62 has a trunk casing portion so that the leg portion 62 and the core cut 55 of the stator 51 do not overlap when viewed along the rotation axis of the rotor 52. 11 is fixed by spot welding. That is, in the present embodiment, the fixed position of the lower main bearing 60 matches the fixed position of the stator 51 when viewed along the rotation axis of the rotor 52. For this reason, in the high-low pressure dome-type scroll compressor 1 according to the present embodiment, the rigidity of the casing 10 can be increased to suppress vibration and noise.

(4)
In the high and low pressure dome type scroll compressor 1 according to the embodiment of the present invention, the stator 51 having concentrated winding coils is adopted, and the lower main bearing 60 is compared with the case where the stator having distributed winding coils is adopted. It arrange | positions so that the drive motor 16 may be approached. For this reason, in this high and low pressure dome type scroll compressor 1, the distance between the housing 23 and the lower main bearing 60 can be shortened as compared with the case where a stator having distributed winding coils is employed. Therefore, in this high / low pressure dome type scroll compressor 1, the support rigidity of the crankshaft 17 can be improved. Therefore, in this high / low pressure dome type scroll compressor 1, vibration can be suppressed.

(5)
In the high and low pressure dome type scroll compressor 1 according to the embodiment of the present invention, the oil separation plate 70 is attached slightly below the center point in the height direction of the lower main bearing 60. For this reason, in this high-low pressure dome type scroll compressor 1, the oil separation plate 70 can be brought as close as possible to the oil surface of the oil reservoir. Therefore, in this high and low pressure dome type scroll compressor 1, the oil separation function can be maintained well.

(6)
In the high / low pressure dome type scroll compressor 1 according to the embodiment of the present invention, the welding position of the leg portion 62 is within the height range of the lower main bearing 60. For this reason, in the high-low pressure dome type scroll compressor 1, the rigidity of the lower main bearing 60 can be improved. Therefore, in the high / low pressure dome type scroll compressor 1, the vibration of the leg portion 62 can be suppressed.

<Modification>
(A)
The lower main bearing 60 according to the previous embodiment was provided with three legs 62, but the number of legs 62 is not particularly limited, and may be four or six. Also good. The number of legs is preferably larger in terms of function, but is preferably smaller in terms of manufacturing cost.

(B)
Although the oil separation plate 70 is attached to the lower main bearing 60 according to the previous embodiment slightly below the center point in the height direction, the oil separation plate 70 is attached to the lowermost end of the lower main bearing 60. It does not matter if it is

(C)
In the previous embodiment, the lower main bearing 60 according to the present invention is applied to the high and low pressure dome type scroll compressor. However, the lower main bearing 60 is not limited to the dome type or the type of the compression mechanism. The present invention may be applied to a scroll compressor, may be applied to a high-pressure dome type scroll compressor whose entire dome has a high pressure, or may be applied to a rotary compressor or a screw compressor.

(D)
In the previous embodiment, the lower main bearing 60 according to the present invention is applied to a hermetic compressor, but the lower main bearing 60 may be applied to a semi-hermetic compressor.

  The compressor according to the present invention is useful because it has a feature that vibration and noise can be kept low.

1 High / low pressure dome type scroll compressor (compressor)
10 Casing 15 Scroll compression mechanism (compression mechanism)
16 Drive motor (drive source)
17 Crankshaft
23 Housing (Main bearing member)
32 Main bearing 51 Stator (stator)
52 Rotor
60 Lower main bearing (sub bearing member)
61 Sub bearing 62 Leg 70 Oil separation plate

JP-A-5-133353

Claims (7)

A casing (10);
A compression mechanism (15) housed in the casing;
A driving source (16) for generating power for driving the compression mechanism and having a stator (51) and a rotor (52) rotatably disposed inside the stator;
A shaft (17) connected to the rotor and transmitting the power generated by the drive source to the compression mechanism;
A main bearing member (23) having a main bearing portion (32) housed in the casing and rotatably supporting the shaft;
A sub-bearing portion (61) disposed at a position facing the main bearing member across the drive source and rotatably supporting the shaft, and radially from the outer peripheral surface of the sub-bearing portion to the inner peripheral surface of the casing A secondary bearing member (60) having a leg (62) extending to
With
The leg portion has a height dimension that is a width in a minimum cross-sectional area portion that is a portion in which a width dimension that is a width in a plan view is a minimum in a portion in which a height dimension that is a thickness in the vertical direction is a minimum. Larger than the dimensions,
Compressor (1). The compressor according to claim 1, wherein three or four legs are provided. 3. The compressor according to claim 1, wherein the stator is fixed to the casing at least at the same position as a fixed position of the leg with respect to the casing in a plan view. The compressor according to claim 1, wherein the stator has a plurality of concentrated winding coils. The compressor according to claim 4, further comprising an oil separation plate (70) attached to a lower portion of the auxiliary bearing member. The compressor according to claim 4, wherein the leg portion has a fixed position with respect to the casing within a height range of the auxiliary bearing member. The leg portion has a cross-sectional secondary moment with respect to the X axis extending in the horizontal direction greater than a cross-sectional secondary moment with respect to the Z axis extending in the vertical direction.
The compressor according to any one of claims 1 to 6 .

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