CN108071591B

CN108071591B - Refrigerant compressor

Info

Publication number: CN108071591B
Application number: CN201711080780.5A
Authority: CN
Inventors: 石川晃广; 饭塚泰成; 高妻裕子; 福原百合子
Original assignee: Hitachi Johnson Controls Air Conditioning Inc
Current assignee: Hitachi Johnson Controls Air Conditioning Inc
Priority date: 2016-11-07
Filing date: 2017-11-06
Publication date: 2020-03-10
Anticipated expiration: 2037-11-06
Also published as: CN108071591A; JP2018076780A

Abstract

Damage to the bearing of the shaft support portion of the compressor due to galvanic corrosion occurs. As a countermeasure, an insulating member is provided between the shaft and the bearing, but since the insulating member is made of a material having lower strength than metal, abrasion powder is generated due to abrasion of the insulating member, and there is a problem that the bearing is damaged. In order to solve the above problems, a compressor according to the present invention includes a compressor mechanism portion for compressing a refrigerant, a motor portion for generating power, a crankshaft for transmitting the power of the motor portion to the compressor mechanism portion, and a bearing for rotatably supporting the crankshaft, wherein a substantially circular tubular insulating member is disposed between the crankshaft and the bearing, a shaft fixing portion fastened to the crankshaft is provided on an inner circumferential side of the insulating member, an oil accumulating space for accumulating a lubricating oil supplied from an oil supply hole of the crankshaft is formed on an outer circumferential side of the insulating member, and the crankshaft and the insulating member are rotated in synchronization with each other while sliding on the bearing.

Description

Refrigerant compressor

Technical Field

The present invention relates to a refrigerant compressor for an air conditioner.

Background

In the refrigerating and air-conditioning equipment, energy saving is required in response to improvement of annual energy consumption efficiency (APF). In order to achieve this object, the type of refrigerant compressor used in refrigeration and air-conditioning equipment is mainly a system in which a permanent magnet motor is inverter-controlled. In recent years, in response to a demand for rapid cooling, the compressor operating conditions have been increased to a high rotation speed and a high load, and thus the compressor driving current tends to be increased as compared with the current during normal operation.

As the compressor driving current increases, the motor current flows to the crankshaft and from there to the bearing supporting the crankshaft, and a discharge phenomenon occurs in the gap between the inner and outer races of the bearing and the rolling elements, thereby increasing the galvanic corrosion of the bearing damage. As a countermeasure, a method of assembling a material having high insulation between the crankshaft and the bearing portion is known.

For example, patent document 1 discloses in fig. 8 and paragraph 0041: "in the present embodiment, any one or a combination of the inner ring 50a, the rolling elements 50b, and the outer ring 50c as the shaft support portion 50 is configured as ceramic as an insulator, or a ceramic film is formed on the inner ring 50a, the rolling elements 50b, and the outer ring 50c, or a resin film having high insulation properties, for example, a PPS (polyphenylene sulfide) -based resin film is formed, and the current passing through the shaft support portion 50 from the crankshaft 51 at the shaft support portion is cut off. By combining the structure of the shaft supporting portion periphery and the structure of connecting the neutral points of the three phases to each other in a line, the bearing current of the displacement compressor is effectively prevented from increasing. Further, the same effect can be obtained also in a configuration in which a film or sheet having high insulation properties is sandwiched on the outer circumferential side of the shaft support portion 50. ".

Further, patent document 2 discloses in fig. 5, paragraphs 0033, and 0039: as described above, according to the first embodiment, the potential difference between the rotating shaft 5 and the ground is compressed into the parasitic capacitance Cb of the bearing 3 and the parasitic capacitance Ci parasitic through the insulator 41. Therefore, the potential difference applied to the bearing 3 can be reduced, and further, the galvanic corrosion of the bearing 3 can be reduced. Further, the rotating shaft 5 can be made of metal, and therefore has excellent strength. "; in addition, "since the insulator 41 is provided on the outer ring 32 side in the first embodiment, and the insulator 42 is provided on the inner ring 31 side in the second embodiment, the area of the bearing inner ring surface is sufficiently smaller than that of the outer ring surface, and therefore, if the thickness required for the insulator 41 provided on the outer ring 32 is set to the thickness of the insulator 42 provided on the inner ring 31 side, the capacitance of the insulator 42 can be sufficiently reduced, and the same operation as that of the first embodiment can be achieved. ".

By these methods, the current flowing to the bearing portion can be reduced, and galvanic corrosion can be prevented.

Documents of the prior art

Patent document

Patent document 1: japanese patent laid-open publication No. 2011-259646

Patent document 2: japanese laid-open patent publication No. 2008-263698

Disclosure of Invention

Problems to be solved by the invention

However, when a resin material having high insulation is used for the bearing, the resin material may be worn by sliding between the crankshaft made of a metal material and the resin material having low strength, and the compressor component may be damaged by wear powder of the resin material. Further, when a ceramic material having high insulation is used for the bearing, there is a problem that the manufacturing cost of the bearing is greatly increased.

The purpose of the present invention is to provide a compressor having high reliability at low cost, in which wear due to sliding of an insulating member provided to prevent electrical corrosion of a bearing member can be suppressed, and damage to the bearing can be suppressed.

Means for solving the problems

In order to solve the above problem, a refrigerant compressor according to the present invention includes: a compressor mechanism unit that compresses a refrigerant; a motor unit that generates power; a crankshaft for transmitting power of the motor unit to the compressor mechanism unit; and a bearing rotatably supporting the crankshaft, wherein a substantially circular tubular insulating member is disposed between the crankshaft and the bearing, a shaft fixing portion fastened to the crankshaft is provided on an inner circumferential side of the insulating member, an oil accumulation space for accumulating a lubricating oil supplied from an oil supply hole of the crankshaft is formed on an outer circumferential side of the insulating member, and the insulating member and the bearing are slidably rotated in synchronization with each other.

The refrigerant compressor of the present invention is configured as follows, and includes: a compressor mechanism unit that compresses a refrigerant; a motor unit that generates power; a crankshaft for transmitting power of the motor unit to the compressor mechanism unit; and a ball bearing that rotatably supports the crankshaft, wherein a substantially circular tubular insulating member is disposed between the crankshaft and the ball bearing, wherein a shaft fixing portion that is fastened to the crankshaft is provided on an inner circumferential side of the insulating member, an inner ring fixing portion that is fastened to an inner ring of the ball bearing is provided on an outer circumferential side of the insulating member, and the crankshaft, the insulating member, and the inner ring of the ball bearing rotate in synchronization with each other.

The effects of the invention are as follows.

Even when the insulating member disposed in the bearing is made of a low-cost resin, the insulating member is configured to be less likely to be worn, so that wear of the bearing of the refrigerant compressor due to sliding can be suppressed, wear powder of the insulating member is reduced, damage of the bearing due to the wear powder and damage of a sliding portion in another compressor can be suppressed, and reliability of the compressor can be improved.

Drawings

Fig. 1 is a longitudinal sectional view of a scroll compressor according to embodiment 1.

Fig. 2 is an enlarged view of the sub bearing portion of embodiment 1.

Fig. 3 is a structural view of an insulating member of embodiment 1.

Fig. 4 is a structural view of an insulating member of embodiment 2.

Fig. 5 is a structural diagram of an insulating member of embodiment 3.

Fig. 6 is an enlarged view of the sub bearing portion of embodiment 4.

Fig. 7 is a structural view of an insulating member of embodiment 4.

Fig. 8 is a structural view of a ball bearing of embodiment 4.

Fig. 9 is an assembly diagram of an insulating member and a ball bearing of embodiment 4.

Description of the symbols

1-scroll compressor, 2-compression mechanism portion, 3-drive portion, 4-motor, 5-fixed scroll, 5 a-fixed scroll discharge port, 5 b-fixed scroll top plate portion, 5 c-fixed scroll spiral, 6-orbiting scroll, 6 a-orbiting scroll spiral, 6 b-orbiting scroll bottom plate, 6 c-sliding bearing of orbiting scroll bearing portion, 7-frame, 8-suction pipe, 9-discharge pipe, 10-rotor, 11-stator, 12-crank shaft, 12 a-crank pin, 12 b-main shaft portion, 12 c-auxiliary shaft portion, 12 d-pump joint, 13-european ring, 14-sliding bearing, 15-oil feed pump, 16-ball bearing, 17-lower frame, 18-housing, 19-housing cover, 30-closed container, 31-suction port, 32-compression chamber, 33-oil accumulation portion, 34-oil feed hole, 35-lateral oil feed hole, 36-lateral oil feed hole, 50-insulating part, 51-through hole, 52-slit, 53-concave part, 54-oil outlet, 55-oil supply pocket, 56-oil passage, 57-projection of insulating part, 58-notch of ball bearing inner ring, 59-space, 60-shaft, 61-rotation stopping piece.

Detailed Description

In the following description of the refrigerant compressor of the present invention, a scroll compressor is taken as an example, but the present invention can also be applied to a fluid compressor having another compression mechanism such as a rotary compressor. Further, although the description will be given of the case where the bearing portion is applied to a ball bearing, the bearing portion may be applied to other bearing structures.

[ example 1 ]

First, a refrigerant compressor according to embodiment 1 will be described with reference to fig. 1 to 3. Fig. 1 is a longitudinal sectional view of a scroll compressor according to embodiment 1. As shown here, the scroll compressor 1 of the present embodiment is configured to accommodate the compression mechanism 2, the drive portion 3, and the crankshaft 12 (crank pin 12a, main shaft portion 12b, and sub shaft portion 12c) in the closed casing 30.

The compression mechanism 2 is configured with a fixed scroll 5, an orbiting scroll 6, and a frame 7 as basic elements. The fixed scroll 5 has a basic structure of a fixed scroll spiral 5c, a fixed scroll top plate 5b, and a fixed scroll discharge port 5 a. The orbiting scroll 6 has an orbiting scroll spiral 6a, an orbiting scroll base plate 6b, and a sliding bearing 6c of an orbiting scroll bearing portion as a basic structure. The sliding bearing 6c of the orbiting scroll bearing portion is formed to protrude perpendicularly to the other side (the opposite side to the spiral body side) of the orbiting scroll base plate 6 b. The frame 7 constitutes a member on which a slide bearing 14 is disposed, and the slide bearing 14 supports one end of the crank shaft 12.

The drive unit 3 for rotationally driving the orbiting scroll 6 is configured by the following components as basic elements: a motor 4 including a stator 11 and a rotor 10; a crankshaft 12; an oil supply pump 15; an oldham ring 13 as a main component of the rotation preventing mechanism of the orbiting scroll 6; a sliding bearing 14 of the crankshaft main bearing; a ball bearing 16 of the crank shaft sub-bearing; and a sliding bearing 6c of the orbiting scroll bearing portion.

The sliding bearing 6c of the orbiting scroll bearing portion is provided on the orbiting scroll 6 so as to be movably and rotatably engaged with the crank pin 12a of the crank shaft 12 in the thrust direction as the rotation axis direction.

European ring 13 is disposed on the back surface of orbiting scroll base plate 6 b. One of two sets of orthogonal key portions formed on the euro-ring 13 is lubricated sliding in a key groove formed on a receiving portion of the euro-ring 13 of the frame 7 (tone), and the remaining one is lubricated sliding in a key groove formed on a back side of the orbiting scroll spiral 6 a. Thereby, the orbiting scroll 6 performs an orbiting motion relative to the fixed scroll 5 in a plane perpendicular to the axial direction, which is the direction in which the orbiting scroll spiral 6a is erected.

In the compression mechanism 2, the orbiting scroll 6 orbits around the fixed scroll 5 without rotating on its own axis by the rotation of the crankshaft 12 connected to the motor 4, and gas is sucked into a compression chamber 32 formed by the fixed scroll spiral 5c and the orbiting scroll spiral 6a through the suction pipe 8 and the suction port 31. By the orbiting motion of the orbiting scroll 6, the compression chamber 32 compresses the gas while reducing its volume while moving toward the center, and the compressed gas is discharged from the fixed scroll discharge port 5a toward the closed casing 30. Then, the liquid is discharged from the closed casing 30 through the discharge pipe 9. Thereby, the space in the closed vessel 30 is maintained at the discharge pressure. As the working fluid compressed in the compression mechanism, HFC refrigerants such as R410A and R32 are used.

A sliding bearing 14 that supports the main shaft portion 12b of the crank shaft 12 is disposed above the motor 4, and a ball bearing 16 that supports the sub shaft portion 12c is disposed below the motor 4. That is, the slide bearing 14 and the ball bearing 16 support the crank shaft 12 on both sides of the motor 4.

The oil feed pump 15 is a positive displacement pump mounted to the lower end of the crankshaft 12. The oil feed pump 15 forcibly supplies the lubricating oil accumulated in the oil accumulating portion 33 to the ball bearing 16, the sliding bearing 6c of the orbiting scroll bearing portion, and the sliding bearing 14 through the pump joint 12d and the oil feed hole 34. The oil supply hole 34 is located in the crankshaft and formed to penetrate in the axial direction of the crankshaft. The oil supplied to the oil supply hole 34 is also supplied to the sliding portions of the orbiting scroll 6 and the fixed scroll 5. The oil supply hole 34 is provided with a lateral oil supply hole 35 for supplying oil to the sliding bearing 14 and a lateral oil supply hole 36 for supplying oil to the ball bearing portion.

The ball bearing 16 constitutes a main part of the sub bearing portion 37. The housing 18 is fixed to the lower frame 17 fixed to the closed casing 30 by bolts. The ball bearing 16 is inserted into the housing 18 from above. A housing cover 19 is also mounted above the ball bearing 16. The housing cover 19 is located above the opening portion of the lateral oil supply hole 36 and the ball bearing 16. The lubricating oil flowing out from the opening of the lateral oil supply hole 36 is supplied to the ball bearing 16 without being dispersed upward (toward the motor 4) by the housing cover 19.

Hereinafter, the features of the present embodiment will be described with reference to fig. 2 in which the sub-bearing portion 37 of fig. 1 is enlarged. As shown here, in the present embodiment, a resin insulating member 50 is provided between the crank shaft 12 and the ball bearing 16. By providing the insulating member 50, when the electric current flows while the electric motor 4 is driven, the electric current flowing from the inside of the crank shaft 12 to the ball bearing 16 can be cut off, and the electric corrosion of the ball bearing 16 due to the electric current can be prevented.

The insulating member 50 is fastened to the crankshaft 12 by press fitting the inner diameter of the insulating member 50 into the outer diameter of the auxiliary shaft portion 12c of the crankshaft before the pump joint 12d is attached. At this time, the insulating member 50 is fastened in the axial direction and the rotational direction by providing a slit in the outer peripheral surface of the front end of the auxiliary shaft portion 12c of the crank shaft and assembling the rotation stopper 61 (shaft fixing portion) of the insulating member 50 thereto. By fastening, the insulating member 50 rotates integrally with the crankshaft 12 in synchronization with the rotation of the crankshaft when the motor 4 is driven. As described above, the refrigerant compressor of the present embodiment has the following configuration: when the motor 4 is driven and the crank shaft 12 is rotated, the outer diameter of the insulating member 50 and the inner diameter of the ball bearing 16 slide.

Therefore, in the present embodiment, an oil film of lubricating oil is required to prevent the abrasion of the insulating member 50 due to the sliding. Therefore, in fig. 2, the lubricating oil is sucked from the oil reservoir 33 by the oil feed pump 15, passes through the oil feed hole 34 in the crankshaft 12, and is supplied from the lateral oil feed hole 36 to the ball bearing 16. The supplied lubricating oil fills the space 59 provided in the insulating member 50, whereby an oil film can be formed between the insulating member 50 and the ball bearing 16, and the abrasion of the insulating member 50 can be suppressed.

Next, fig. 3 shows a detailed structure of the space 59 necessary for forming an oil film on the outer peripheral surface of the insulating member 50. As shown here, the insulating member 50 is formed in a substantially circular tubular shape, and includes a through hole 51 penetrating in the radial direction, a slit 52 provided on the outer peripheral surface facing upward, and a rotation stopper 61 provided on the lower end of the inner peripheral surface. As shown in fig. 2, since the through hole 51 is provided coaxially with the cross oil supply hole 36 of the crankshaft 12 and the through hole 51 is connected to the slit 52, the lubricating oil supplied from the cross oil supply hole 36 is supplied to the slit 52 through the through hole 51, and the oil film between the insulating member 50 and the ball bearing 16 is formed by the lubricating oil. Further, since the insulating member 50 is press-fitted with the outer diameter of the auxiliary shaft portion 12c of the crankshaft and the inner diameter of the insulating member 50 and the rotation stopper 61 provided with the insulating member 50, the through hole 51 through which the crankshaft rotates and the lateral oil supply hole 36 of the crankshaft 12 are not displaced from each other, and the holes are not closed.

The slit 52 is open upward (toward the motor 4) and closed downward, and therefore the excess lubricant is discharged only toward the upper housing cover 19. That is, since the lubricating oil does not flow downward by its own weight through the path passing through the through hole 51 of the insulating member 50 from the lateral oil supply hole 36 of the crankshaft 12, an oil film can be formed on the inner peripheral surface of the ball bearing 16 at all times by the lubricating oil filling the space 59. This prevents the insulating member 50 from being worn due to sliding between the outer diameter of the rotating insulating member 50 and the inner diameter of the ball bearing 16, and also prevents the ball bearing 16 from being electrically corroded.

[ example 2 ]

Fig. 4 shows the structure of an insulating member 50 of embodiment 2 of the present invention. A repeated description of portions having the same functions as those of embodiment 1 is omitted.

As shown in fig. 4, the insulating member 50 of the present embodiment is formed in a substantially tubular shape, and includes a through hole 51 penetrating in the radial direction, a substantially annular recess 53 provided over the entire circumference of the outer peripheral surface, an oil outlet 54 provided on the outer peripheral surface so as to face upward, and a detent 61 provided at the lower end of the inner peripheral surface. The position and orientation of the insulating member 50 to the refrigerant compressor and the fastening method are the same as those in embodiment 1.

In the present embodiment, the lubricating oil supplied from the through hole 51 of the insulating member 50 is accumulated in the recess 53 provided in the outer peripheral surface. As in example 1, since the lubricating oil is discharged from the oil outlet 54 provided at the upper side (the motor 4 side), rather than flowing downward due to its own weight, an oil film can be formed on the outer peripheral surface of the insulating member 50 at all times. This prevents the insulating member 50 from being worn due to sliding between the outer diameter of the rotating insulating member 50 and the inner diameter of the ball bearing 16, and also prevents the ball bearing 16 from being electrically corroded. The shape of the recess 53 is not limited to the shape shown in fig. 4, and may be another shape that can obtain the above-described function.

[ example 3 ]

Fig. 5 shows the structure of an insulating member 50 according to embodiment 3 of the present invention. A repeated description of portions having the same functions as those in embodiment 1 or embodiment 2 is omitted.

As shown in fig. 5, the insulating member 50 of the present embodiment is formed in a substantially circular tubular shape, and includes a through hole 51 penetrating in the radial direction, an oil outlet 54 provided on the outer peripheral surface so as to face upward, a plurality of oil supply pockets 55 formed by recessing the outer peripheral surface, an oil passage 56 connecting the oil supply pockets 55, and a rotation stopper 61 provided on the lower end of the inner peripheral surface. The position and orientation of the insulating member 50 to the refrigerant compressor and the fastening method are the same as those in embodiment 1.

In the present embodiment, the lubricating oil supplied from the through hole 51 of the insulating member 50 flows through the oil passage 56 and is accumulated in each oil supply pocket 55. As in example 1, since the lubricating oil is discharged from the oil outlet 54 provided above (on the motor 4 side) and does not flow downward due to its own weight, an oil film can be formed on the outer peripheral surface of the insulating member 50 at all times. This prevents the insulating member 50 from being worn due to sliding between the outer diameter of the rotating insulating member 50 and the inner diameter of the ball bearing 16, and also prevents the ball bearing 16 from being electrically corroded. The shape, size, and number of the supply pockets 55, the shape and size of the oil passages 56, and the method of connecting the supply pockets 55 are not limited to those shown in fig. 5, and may be other configurations capable of obtaining the above-described operation.

[ example 4 ]

Next, a refrigerant compressor according to embodiment 4 of the present invention will be described with reference to fig. 6 to 9. Note that a repeated description of a portion having the same function as the structure of the reference numeral already described is omitted.

Fig. 6 is an enlarged view of the vicinity of the sub-bearing portion 37 of the refrigerant compressor of the present embodiment. In the present embodiment, the cross oil supply hole 36 of the crankshaft 12 is also provided above the insulating member 50 and the ball bearing 16 (on the motor 4 side), as in embodiment 1.

Fig. 7 shows the structure of the insulating member 50 of the present embodiment. As shown here, the insulating member 50 of the present embodiment has a structure in which the projection 57 is provided at the upper end of the outer peripheral surface and the rotation stopper 61 is provided at the lower end of the inner peripheral surface. The perspective view of fig. 8 shows the structure of the ball bearing 16. A cutout 58 is provided on the upper surface of the inner ring of the ball bearing 16. Fig. 9 is a view of the assembled ball bearing 16 and insulating member 50 of the present embodiment. In this way, the projection 57 of the insulating member 50 is provided in the notch 58 of the inner ring of the ball bearing, so that when the insulating member 50 rotates relative to the shaft 60, the projection 57 of the insulating member 50 and the notch 58 of the inner ring of the ball bearing 16 contact each other, and therefore the insulating member 50 and the inner ring of the ball bearing 16 rotate in synchronization. Here, as shown in fig. 6, in the present embodiment, the crank shaft 12 and the insulating member 50 also rotate in synchronization, and therefore, the crank shaft 12, the insulating member 50, and the inner ring of the ball bearing 16 rotate in synchronization. Accordingly, between the crank shaft 12 and the insulating member 50 and between the insulating member 50 and the ball bearing 16, the insulating member 50 is not abraded and abrasion powder is not generated.

In addition, in order to assemble the projection 57 of the insulating member 50 and the notch 58 of the inner ring of the ball bearing 16, it is preferable to provide a clearance of a degree of transition fit between the projection 57 of the insulating member and the notch 58 of the inner ring of the ball bearing in view of synchronization of rotation of the shaft 60 and ease of assembly.

In embodiments 1 to 3, the insulating member 50 and the crankshaft 12 are fastened, and the outer peripheral surface of the insulating member 50 rotates in a sliding manner on the inner peripheral surface of the ball bearing 16 when the motor 4 is driven, and here, the abrasion of the insulating member 50 is suppressed by positively forming an oil film, thereby preventing the generation of abrasion powder.

In contrast, as in the present embodiment, the insulating member 50 and the inner ring of the ball bearing 16 are assembled, and the insulating member 50 rotates in synchronization with the crank shaft 12 and the inner ring of the ball bearing 16 when the motor 4 is driven, and by excluding the sliding portion from the insulating member 50, the abrasion can be eliminated, and the generation of abrasion powder can be prevented.

According to the configuration of the present embodiment described above, only by providing the insulating member 50 in the sub-bearing portion 37, the insulating member 50 is not worn, and the electric corrosion of the ball bearing 16 can be prevented. The shape, size, and number of the protrusions 57 of the insulating member, and the shape, size, and number of the notches 58 of the inner ring of the ball bearing 16 are not limited to those shown in fig. 7 to 9, and may be other configurations capable of obtaining the above-described effects.

The present invention is not limited to the above-described embodiments, and various modifications are possible. For example, the above-described embodiments are described in detail for easy understanding of the present invention, and are not limited to the embodiments having all the structures described. Moreover, a part of the structure of one embodiment may be replaced with the structure of another embodiment, and the structure of another embodiment may be added to the structure of one embodiment. Further, the structure of each embodiment can be added, deleted, or replaced with another structure.

Claims

1. A refrigerant compressor is characterized by comprising:

a compressor mechanism unit that compresses a refrigerant;

a motor unit that generates power;

a crankshaft for transmitting power of the motor unit to the compressor mechanism unit; and

a bearing for rotatably supporting the crankshaft,

an insulating member having a substantially circular tubular shape is disposed between the crankshaft and the bearing, a shaft fixing portion fastened to the crankshaft is provided on an inner peripheral side of the insulating member, an oil accumulating space for accumulating a lubricating oil supplied from an oil supply hole of the crankshaft is formed on an outer peripheral side of the insulating member,

the crankshaft and the insulating member are synchronized, the insulating member and the bearing are slidably rotated,

the oil accumulation space is composed of a through hole communicating with the oil supply hole and a slit connected to the through hole and parallel to the crankshaft.

2. A refrigerant compressor is characterized by comprising:

a compressor mechanism unit that compresses a refrigerant;

a motor unit that generates power;

a bearing for rotatably supporting the crankshaft,

the oil accumulation space is formed by a through hole communicating with the oil supply hole and a substantially annular recess connected to the through hole.

3. A refrigerant compressor is characterized by comprising:

a compressor mechanism unit that compresses a refrigerant;

a motor unit that generates power;

a bearing for rotatably supporting the crankshaft,

the oil accumulation space is composed of a through hole communicating with the oil supply hole, an oil supply pocket provided on an outer peripheral surface of the insulating member, and an oil passage connecting the through hole and the oil supply pocket.

4. Refrigerant compressor according to any one of claims 1 to 3,

the insulating member is made of resin.