CN102803729B - compressor - Google Patents

Abstract

The compressor (1) of the present invention has a housing (10), a compression mechanism (15), a drive source (16), a shaft (17), a housing (23), and a lower main bearing (60). The drive source has a stator (51) and a rotor (52) and generates power to drive the compression mechanism. The shaft is connected to the rotor and transmits the power generated by the drive source to the compression mechanism. The housing has a main bearing portion (32) that supports the shaft for rotation. The lower main bearing is disposed opposite to the housing across the drive source and has a secondary bearing portion (61) and a foot portion (62). The secondary bearing portion supports the shaft for rotation. The foot portion extends radially from the outer peripheral surface of the bearing portion to the inner peripheral surface of the housing. In the minimum cross-sectional area portion, the height dimension of the foot portion is greater than its width dimension.

Description

compressor

technical field

The present invention relates to compressors.

Background technique

In the past, in order to reduce the vibration and noise of rotary compressors, it was proposed to "arrange and fix a rolling type thrust bearing as an auxiliary bearing near the auxiliary bearing". In addition, such a proposal is described in detail in, for example, Patent Document 1 (Japanese Patent Application Laid-Open No. 5-133353).

Contents of the invention

The problem to be solved by the invention

However, when the auxiliary bearing of the rolling-type thrust bearing is added in addition to the auxiliary bearing in this way, the manufacturing cost increases. In addition, by providing the sub-bearing, compared with when the shaft is in a cantilevered state, the whirling vibration caused by the bending of the shaft is suppressed, but the motor excitation due to the magnetic attraction between the rotor and the stator of the motor is generated. Vibration and noise caused by vibration force. In the prior Patent Document 1, as a method of reducing the vibration and noise, for example, no consideration was given to increasing the rigidity of the shaft and the bearing, and there was a problem of generating vibration and noise due to the excitation force of the motor.

The object of the present invention is to suppress vibration and noise to be low while maintaining low manufacturing cost.

means to solve the problem

The compressor according to the first aspect includes a housing, a compression mechanism, a drive source, a shaft, a main bearing member, and a sub bearing member. The compression mechanism is housed in the casing. The drive source generates power to drive the compression mechanism. The drive source has a stator and a rotor rotatably arranged 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 components are housed in the housing. The main bearing component has a main bearing portion. The main bearing portion rotatably supports the shaft. The sub bearing member is disposed at a position opposing the main bearing member across the drive source. The sub-bearing component has a sub-bearing part and a leg part. The sub-bearing portion supports the shaft in a rotatable manner. The legs extend radially from the outer peripheral surface of the sub-bearing to the inner peripheral surface of the housing. Also, the foot portion has a height dimension greater than a width dimension in the smallest cross-sectional area portion.

In a compressor provided with only the main bearing unit and the sub bearing unit, the shaft vibrates in an arcuate vibration mode with the main bearing unit and the sub bearing unit as fulcrums due to the magnetic attraction force between the rotor and the stator of the driving source. In order to suppress this vibration mode, for example, it is effective to increase the rigidity of the shaft by changing the material of the shaft or increasing the thickness of the shaft by increasing the diameter, or increasing the rigidity of the main bearing and the sub bearing in the same way. However, a simple material change or thickening increases the cost, so it is necessary to efficiently increase the rigidity.

In this compressor, the foot portion of the sub-bearing member has a height dimension larger than a width dimension in the smallest cross-sectional area portion. Therefore, in this compressor, the secondary moment of section in the foot portion with respect to the X-axis extending in the horizontal direction is larger than the secondary moment of section 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 to be low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to bending in the vertical direction compared with the horizontal direction, thereby suppressing the bow-shaped vibration mode of the shaft and efficiently reducing the vibration caused by the motor excitation force. The vibration and noise suppression is lower.

In the compressor of the second aspect, in the compressor of the first aspect, three or four legs are provided.

Therefore, in this compressor, it is possible to moderately disperse the vibration while suppressing the manufacturing cost.

In the compressor of the third aspect, in the compressor of the first aspect or the second aspect, the stator is fixed to the casing at least at the same position as the fixed position of the leg portion with respect to the casing in plan view.

In this compressor, the stator is fixed to the casing at least at the same position as the fixed position of the leg portion with respect to the casing in plan view. Therefore, in this compressor, the rigidity of the casing can be increased to suppress vibration and noise.

In the compressor of the fourth aspect, in the compressor of the first aspect or the second aspect, the stator has a plurality of concentrated winding coils.

In this compressor, the stator of the electric motor has a plurality of concentratedly wound coils. Therefore, in this compressor, the coil end can be reduced in size compared with the distributed winding coil. Therefore, in this compressor, the distance between the main bearing member and the sub bearing member can be shortened. Thereby, in this compressor, the support rigidity of a shaft can be improved. As a result, in this compressor, vibration can be suppressed.

The compressor of the fifth aspect is the compressor of the fourth aspect, wherein the compressor further includes an oil separation plate. The oil separation plate is mounted on the lower part of the auxiliary bearing part. In addition, it is preferable that the oil separation plate is attached to the lowermost end of the sub-bearing member.

Therefore, in this compressor, even when the sub-bearing member is far from the oil surface, the oil separation plate can be brought as close as possible to the oil surface of the oil groove. Therefore, in this compressor, the oil separation function can be maintained favorably.

In the compressor of the sixth aspect, in the compressor of the fourth aspect, the fixed position of the leg portion with respect to the housing is within a height range of the sub-bearing member.

Therefore, in this compressor, the rigidity of the sub-bearing member can be improved. Therefore, in this compressor, the vibration of the foot can be suppressed.

A compressor according to a seventh aspect has a housing, a compression mechanism, a drive source, a shaft, a main bearing member, and a sub bearing member. The compression mechanism is housed in the casing. The drive source generates power to drive the compression mechanism. The drive source has a stator and a rotor rotatably arranged 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 components are housed in the housing. The main bearing component has a main bearing portion. The main bearing portion rotatably supports the shaft. The sub bearing member is disposed at a position opposing the main bearing member across the drive source. The sub-bearing component has a sub-bearing portion and a leg portion. The sub-bearing surrounds a part of the shaft. The legs extend radially from the outer peripheral surface of the sub-bearing to the inner peripheral surface of the housing. Also, the secondary moment of section in the foot portion with respect to the X-axis extending in the horizontal direction is larger than the secondary moment of section with respect to the Z-axis extending in the vertical direction.

In this compressor, the secondary moment of section for the X-axis extending in the horizontal direction is greater than the secondary moment of section for the Z-axis extending in the vertical direction in the foot portion of the sub-bearing member. Therefore, in this compressor, the support rigidity of a shaft can be improved. Therefore, in this compressor, vibration and noise can be suppressed to be low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to bending in the vertical direction compared with the horizontal direction, thereby suppressing the bow-shaped vibration mode of the shaft and efficiently reducing the vibration caused by the motor excitation force. The vibration and noise suppression is lower.

Invention effect

In the compressor of the first aspect, the secondary moment of section in the leg portion with respect to the X-axis extending in the horizontal direction is larger than the secondary moment of section 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 to be low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to bending in the vertical direction compared with the horizontal direction, thereby suppressing the bow-shaped vibration mode of the shaft and efficiently reducing the vibration caused by the motor excitation force. The vibration and noise suppression is lower.

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

In the compressor according to the third aspect, the rigidity of the casing can be increased to suppress vibration and noise.

In the compressor according to the fourth aspect, the coil end can be reduced in size compared with the distributed winding coil. Therefore, in this compressor, the distance between the main bearing member and the sub bearing member can be shortened. Thereby, in this compressor, the support rigidity of a shaft can be improved. As a result, in this compressor, vibration can be suppressed.

In the compressor according to the fifth aspect, even when the sub-bearing member is far from the oil surface, the oil separation plate can be brought as close as possible to the oil surface of the oil groove. Therefore, in this compressor, the oil separation function can be maintained favorably.

In the compressor according to the sixth aspect, the rigidity of the sub-bearing member can be increased. Therefore, in this compressor, the vibration of the leg can be suppressed.

In the compressor according to the seventh aspect, the support rigidity of the shaft can be increased. Therefore, in this compressor, vibration and noise can be suppressed to be low. In particular, in this compressor, the rigidity of the sub-bearing portion is increased with respect to bending in the vertical direction compared with the horizontal direction, thereby suppressing the bow-shaped vibration mode of the shaft and efficiently reducing the vibration caused by the motor excitation force. The vibration and noise suppression is lower.

Description of drawings

Fig. 1 is a longitudinal sectional view of a scroll compressor according to one embodiment of the present invention.

Fig. 2 is a cross-sectional view of a scroll compressor according to an embodiment of the present invention.

Fig. 3 is a plan view of the lower main bearing of the scroll compressor according to the embodiment of the present invention.

Fig. 4 is an A-A sectional view of the lower main bearing shown in Fig. 3 .

Fig. 5 is a bottom view of the lower main bearing shown in Fig. 3 .

Fig. 6 is a diagram showing a vibration mode of a crankshaft of a scroll compressor according to an embodiment of the present invention.

FIG. 7 is a comparison diagram of noise characteristics between a scroll compressor according to an embodiment of the present invention and a comparative example.

Detailed ways

The high-low pressure dome scroll compressor 1 according to the embodiment of the present invention constitutes a refrigerant circuit together with an evaporator, a condenser, an expansion mechanism, etc. Refrigerant, etc.) to compress, as shown in Figure 1, the scroll compressor 1 is mainly composed of a closed dome-shaped casing 10, a scroll compression mechanism 15, a crank shaft 17, a drive motor 16, a lower main bearing 60, oil The separation plate 70, the suction pipe 19, and the discharge pipe 20 are comprised. Next, the components of the high and low pressure dome scroll compressor 1 will be described in detail. In addition, in this embodiment, as shown in FIG. 1 , let the horizontal direction be the X axis, and let the vertical direction be the Y axis.

<Details of Components of High and Low Pressure Dome Scroll Compressors>

(1) Housing

As shown in FIG. 1 , the casing 10 is composed of a main body casing portion 11 , an upper wall portion 12 , and a bottom wall portion 13 . The main body casing portion 11 is a substantially cylindrical pressure-resistant member. The upper wall portion 12 is bowl-shaped and covers the upper end of the main body shell portion 11 . The bottom wall portion 13 is bowl-shaped and covers the lower end of the main body shell portion 11 . Furthermore, the scroll compression mechanism 15 , the crankshaft 17 , the drive motor 16 , the lower main bearing 60 , and the oil separation plate 70 are mainly accommodated in the casing 10 . In addition, in this embodiment, the drive motor 16 is arranged below the scroll compression mechanism 15 . Further, the scroll compression mechanism 15 and the drive motor 16 are connected by a crankshaft 17 arranged to extend in the vertical direction within the casing 10 .

(2) Scroll compression mechanism

As shown in FIG. 1 , the scroll compression mechanism 15 is mainly composed of a housing 23 , a fixed scroll 24 , a movable scroll 26 and an Oldham Link 39 . The components of the scroll compression mechanism 15 will be described in detail below.

a) Shell

The casing 23 is press-fitted and fixed to the main body casing portion 11 in its entirety in the circumferential direction on its outer peripheral surface. That is, the main body casing 11 and the housing 23 are in close contact with each other in an airtight manner over the entire circumference. Therefore, the inside of the casing 10 is divided into two spaces by the casing 23 . In addition, in the high-low pressure dome scroll compressor 1 of this embodiment, during operation, 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. . In addition, the casing 23 is arranged such that the upper end surface is in close contact with the lower end surface of the fixed scroll 24 , and the fixed scroll 24 is fastened and fixed to the casing 23 by bolts (not shown). Furthermore, a case recessed portion 31 and a main bearing portion 32 are formed in the case 23 . The housing recess 31 is recessed in the upper center of the housing. A bearing portion 26c (described later) of the movable scroll 26 and an eccentric shaft portion 17a (described later) of the crankshaft 17 are arranged in the housing recessed portion 31 . The main bearing portion 32 is formed downward from the center of the lower portion. Further, 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 into the bearing hole 33 via a slide bearing 34 .

b) fixed scroll

The fixed scroll 24 is a component arranged to be in close contact with the upper part of the housing 23, and as shown in FIG. constitute.

A discharge passage 41 and an enlarged concave portion 42 are formed in the end plate 24a. The discharge passage 41 is formed in the central part of the end plate 24a so as to extend in the vertical direction, and the discharge passage 41 communicates with the compression chamber 40 (described later). The enlarged concave portion 42 is formed to open on the upper surface of the end plate 24 a and communicates with the discharge passage 41 . And the cover body 44 is fastened and fixed to the end plate 24a by the bolt 44a so that this enlarged recessed part 42 may be closed. In addition, by covering the enlarged recessed portion 42 with the cover body 44 in this way, an expansion chamber for silencing the operation sound of the scroll compression mechanism 15 , that is, a silencing space 45 is formed. In addition, the fixed scroll 24 and the cover body 44 are tightly bonded to each other through a gasket (not shown) to be sealed.

The scroll 24b is formed on the lower side of the end plate 24a.

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

c) Movable scroll

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

The scroll 26b is formed on the upper side of the end plate 26a. In addition, this wrap 26 b meshes with the wrap 24 b of the fixed scroll 24 . As a result, a compression chamber 40 is formed between the contact portions of the two wraps 24b, 26b.

The bearing portion 26c is formed on the lower side of the end plate 26a. In addition, the eccentric shaft portion 17a of the crankshaft 17 is fitted into the bearing portion 26c.

Groove portions 26d are formed at both end portions of the end plate 26a. In addition, the movable scroll side key portion of the Oldhams 39 (described later) is fitted into the groove portion 26d. In addition, the case-side key portion of the Oldham link 39 is fitted into a groove provided in the case 23 . That is, the movable scroll 26 is rotatably supported by the casing 23 via the Oldham link 39 , and revolves inside the casing 23 without autorotation due to the rotation of the crankshaft 17 . In addition, as the movable scroll 26 revolves, the volume between the two scrolls 24b, 26b contracts toward the center, and the refrigerant is compressed.

d) Cross link

The Oldham link 39 is a member for preventing the autorotation of the movable scroll 26 , the movable scroll side key part fits into the groove part 26 d of the movable scroll 26 , and the casing side key part fits into the cross groove of the casing 23 . (not shown). In addition, the cross grooves are oblong grooves, and are disposed at positions facing each other in the housing 23 .

(3) Crankshaft

As shown in FIG. 1 , the crankshaft 17 is a substantially cylindrical integrally formed member, and is mainly composed of an eccentric shaft portion 17a, a main shaft portion 17b, a counterweight portion 17c, and a counter shaft portion 17d. The eccentric shaft portion 17 a is housed in a bearing portion 26 c of the movable scroll 26 . The main shaft portion 17b is accommodated in the bearing hole 33 of the housing 23 via the slide bearing 34 . The sub shaft portion 17d is accommodated in a bearing hole of a lower main bearing 60 (described later).

(4) Drive motor

In this embodiment, the drive motor 16 is a brushless DC motor, and is mainly composed of a stator 51 and a rotor 52 .

The stator 51 is an annular body, and copper wires are collectively wound around a plurality of teeth (not shown). Also, coil ends 53 are formed above and below the teeth. In this stator 51 , the coil ends 53 are smaller than the distributed winding coils. Further, as shown in FIGS. 1 and 2 , nine core cut portions (Core Cut) 55 are provided at equal intervals on the outer peripheral portion of the stator 51 . That is, the stator 51 is in the shape of a spur gear. Furthermore, the stator 51 is press-fitted and fixed to the inner wall surface of the casing 10 .

The rotor 52 is rotatably housed inside the stator 51 with a slight gap (air gap passage). Further, 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

As shown in FIG. 1 , the lower main bearing 60 is arranged on the lower side of the drive motor 16 . And, as shown in FIGS. 3 to 5 , the lower main bearing 60 is mainly composed of a sub-bearing portion 61 and a leg portion 62 . The sub bearing portion 61 rotatably supports the sub shaft portion 17 d of the crankshaft 17 . Three leg portions 62 are formed, and are fixed to the main body case portion 11 by spot welding so as not to overlap the core cut portion 55 of the stator 51 when viewed along the rotation axis of the rotor 52 . Furthermore, in the present embodiment, the spot welding position is located within the height range of the lower main bearing 60 . Furthermore, as shown in FIG. 4 , the leg portion 62 has a portion where the thickness in the vertical direction (Z-axis direction), that is, the height dimension H is the smallest. Furthermore, as shown in FIG. 3 , the leg portion 62 has a portion having the smallest width W in a planar view in the portion where the height H is the smallest. Therefore, as shown in Figures 3 and 4, the foot portion 62 has the part with the smallest cross-sectional area, that is, the smallest cross-sectional area part R. In this smallest cross-sectional area part R, the height dimension H is 27 mm, and the width dimension W is 25 mm, designed as The height dimension H is greater than the width dimension W. Also, the lower main bearing 60 is disposed closer to the drive motor side than in the case of applying a stator having distributed winding coils. In addition, this is due to the fact that the coil ends of a stator with concentratedly wound coils are smaller than those of a stator with distributedly wound coils.

(6) Oil separation plate

The oil separation plate 70 is a substantially semicircular plate member. And, as shown in FIGS. 3 to 5 , the oil separation plate 70 is attached to a position slightly lower than the center point in the height direction of the lower main bearing 60 .

(7) Suction pipe

The suction pipe 19 guides the refrigerant in the refrigerant circuit to the scroll compression mechanism 15 , and is airtightly fitted into the upper wall portion 12 of the housing 10 . The inner end of the suction pipe 19 is fitted into the fixed scroll 24 .

(8) Discharge pipe

The discharge pipe 20 is used to discharge the refrigerant in the casing 10 to the refrigerant circuit, and is airtightly fitted into the main body casing portion 11 of the casing 10 .

<Features of the high-low pressure dome-type scroll compressor of the present embodiment>

(1)

In the lower main bearing 60 of the embodiment of the present invention, the foot portion 62 is designed so that the height dimension H is larger than the width dimension W in the smallest cross-sectional area portion R. As shown in FIG. Therefore, in the high-low pressure dome type scroll compressor 1 of the present embodiment, the secondary moment of the section in the leg portion 62 with respect to the X-axis extending in the horizontal direction is larger than the section with respect to the Z-axis extending in the vertical direction. secondary moment. 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. In addition, in this high-low pressure dome scroll compressor 1, since the sub-bearing portion 61 has higher rigidity against bending in the vertical direction than in the horizontal direction, it is possible to suppress bending of the main bearing portion 32 and the sub-bearing portion. 61 is a fulcrum, and the vibration mode in which the crankshaft 17 vibrates in a bow shape can efficiently suppress the vibration and noise caused by the excitation force of the motor to a low level. FIG. 6 shows the vibration mode M of the bow shape of the crankshaft 17 . This vibration mode M is generated due to the magnetic attraction force between the rotor 52 and the stator 51 of the drive motor 16 .

7 shows the noise characteristics with respect to frequency of the high and low pressure dome type scroll compressor 1 having the lower main bearing 60 of the embodiment of the present invention and the compressor without the lower main bearing 60 of the embodiment of the present invention (comparative example). ) comparison plot of noise characteristics against frequency. In FIG. 7 , the noise level is a measured value under the test condition that the rotational speed of the motor is 90 rps. As shown in FIG. 7 , in the high-low pressure dome scroll compressor 1 according to the embodiment of the present invention, compared with the comparative example, the low-order components (100 Hz to 315 Hz) of the rotation frequency components of the crankshaft 17 are The noise level is kept low. In addition, in the high-low pressure dome-type scroll compressor 1 according to the embodiment of the present invention, compared with the comparative example, the natural value of the rotation frequency of the crankshaft 17 coincides with the frequency of the fundamental excitation force of the motor. The noise level at the frequency (500Hz-630Hz) of the resonance phenomenon is also suppressed to be low.

(2)

In the lower main bearing 60 according to the embodiment of the present invention, three leg portions 62 are provided. Therefore, in the high-low pressure dome scroll compressor 1 of the present embodiment, it is possible to moderately disperse the vibration while suppressing the processing cost.

(3)

In the lower main bearing 60 according to the embodiment of the present invention, when viewed along the rotation axis of the rotor 52 , the leg portion 62 is welded by spot welding so that the leg portion 62 does not overlap the core cut portion 55 of the stator 51 . 62 is fixed to the main body shell portion 11 . That is, in the present embodiment, when viewed along the rotation axis of the rotor 52 , the fixed position of the lower main bearing 60 coincides with the fixed position of the stator 51 . Therefore, in the high-low pressure dome scroll compressor 1 of the present embodiment, the rigidity of the casing 10 can be increased to suppress vibration and noise.

(4)

In the high-low pressure dome-type scroll compressor 1 according to the embodiment of the present invention, the stator 51 having concentrated winding coils is used, and the lower main bearing 60 is closer to the drive motor than in the case of using the stator having distributed winding coils. 16 configurations. Therefore, in this high-low pressure dome type scroll compressor 1 , the distance between the housing 23 and the lower main bearing 60 can be shortened compared to the case of using a stator having distributed winding coils. Therefore, in this high-low pressure dome type scroll compressor 1, the support rigidity of the crankshaft 17 can be improved. Accordingly, in the high-low pressure dome scroll compressor 1, vibration can be suppressed.

(5)

In the high-low pressure dome 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 . Therefore, in the high-low pressure dome scroll compressor 1, the oil separation plate 70 can be brought as close as possible to the oil surface of the oil groove. Therefore, in the high-low pressure dome scroll compressor 1, the oil separation function can be maintained satisfactorily.

(6)

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

<Modification>

(A)

In the lower main bearing 60 of the previous embodiment, three leg portions 62 are provided, but the number of leg portions 62 is not particularly limited, and may be four or six. In addition, it is preferable to have a large number of legs in terms of function, but it is preferable to have a small number of legs in terms of manufacturing cost.

(B)

In the lower main bearing 60 of the previous embodiment, the oil separation plate 70 is attached slightly below the center point in the height direction, but the oil separation plate 70 may be attached to the lowermost end of the lower main bearing 60 .

(C)

In the previous embodiment, the lower main bearing 60 of the present invention is applied to a high-low pressure dome type scroll compressor, however, the dome type and the type of compression mechanism are not limited, and the lower main bearing 60 can be applied to a low pressure dome type scroll compressor. The top-type scroll compressor can also be applied to a high-pressure dome-type scroll compressor with a high-pressure dome as a whole, and can also be applied to a rotary compressor or a screw compressor.

(D)

In the previous embodiment, the lower main bearing 60 of the present invention was applied to a hermetic compressor, but the lower main bearing 60 may also be applied to a semi-hermetic compressor.

Industrial availability

The compressor of the present invention is useful because it can suppress vibration and noise to a low level.

Label description

1: High and low pressure dome type scroll compressor (compressor); 10: Shell; 15: Scroll compression mechanism (compression mechanism); 16: Drive motor (drive source); 17: Crankshaft (shaft); 23: Housing (main bearing part); 32: main bearing part; 51: stator; 52: rotor; 60: lower main bearing (sub-bearing part); 61: sub-bearing part; 62: foot part; 70: oil separation plate.

prior art literature

patent documents

Patent Document 1: Japanese Patent Application Laid-Open No. 5-133353

Claims (7)

1. A compressor (1), wherein the compressor has: shell (10); a compression mechanism (15) housed within said housing; A drive source (16), which generates power to drive the compression mechanism, has a stator (51) and a rotor (52) rotatably arranged inside the stator; a shaft (17), which is connected to the rotor, and transmits the power generated by the driving source to the compression mechanism; a main bearing member (23), housed in the housing, having a main bearing portion (32) rotatably supporting the shaft; and A sub-bearing part (60) is arranged at a position opposite to the main bearing part across the drive source, the sub-bearing part (60) has a sub-bearing part (61) and a leg part (62), and the The sub-bearing part supports the shaft in a rotatable manner, the legs extend radially from the outer peripheral surface of the sub-bearing part to the inner peripheral surface of the housing, and the height dimension is larger than the width dimension in the smallest cross-sectional area part. , The portion with the smallest cross-sectional area is a portion in which the vertical thickness of the leg portion, that is, the height dimension is the smallest, and the width dimension, that is, the width dimension of the leg portion in plan view is the smallest. 2. The compressor of claim 1, wherein: Described foot is provided with 3 or 4. 3. A compressor according to claim 1 or 2, wherein: The stator is fixed to the housing at least at the same position as the fixing position of the foot with respect to the housing when viewed from above. 4. The compressor of claim 1 or 2, wherein: The stator has a plurality of concentrated winding coils. 5. The compressor of claim 4, wherein: The compressor also has an oil separation plate (70) mounted on the lower portion of the sub bearing member. 6. The compressor of claim 4, wherein: The fixed position of the foot relative to the housing is within the height range of the secondary bearing part. 7. The compressor of claim 1 or 2, wherein: A second moment of section in the foot with respect to an X-axis extending in a horizontal direction is greater than a second moment of section about a Z-axis extending in a vertical direction.