Refrigerant compressor and air conditioning device

Abstract

To provide a refrigerant compressor having improved reliability in a configuration in which an insulating bush is provided in an auxiliary bearing, and an air conditioner using the same. [Solution] A refrigerant compressor 1 that compresses a refrigerant in a refrigeration cycle, comprising a crankshaft 33 that rotates integrally with an electric motor 20 including a stator 20a and a rotor 20b, and a ball bearing 34 that supports the compression mechanism side and bottom side of the crankshaft 33, the ball bearing 34 having an insulating bush 344 composed of a resin member 344a and a metal member 344b, and the portion of the crankshaft 33 that is inserted into the ball bearing 34 is tapered.

Description

[Technical field]

[0001] The present invention relates to the reliability of a refrigerant compressor and an air conditioner using the same. [Background technology]

[0002] Refrigerant compressors constituting a refrigeration cycle are widely used in variable speed operation in which an inverter is used to drive an electric motor, from the viewpoints of energy saving, efficiency improvement, and cost reduction.

[0003] In a refrigerant compressor that uses an inverter, the drive current increases when it is driven under high load compared to a conventional constant speed refrigerant compressor, and the voltage (shaft voltage) generated in the crankshaft that rotates together with the electric motor increases. When the shaft voltage increases, the potential difference between the inner and outer rings of the rolling bearing that supports the crankshaft increases, and the current flowing through the rolling bearing increases. This can cause electrolytic corrosion between the rolling elements and the raceway surfaces of both the inner and outer rings of the rolling bearing, reducing the reliability of the refrigerant compressor.

[0004] In this regard, Japanese Patent Application Laid-Open No. 2021-143713 (Patent Document 1) discloses a refrigerant compressor having an insulating bush made of a cylindrical resin and metal on the inner diameter of the inner ring of the rolling bearing. According to Patent Document 1, electrolytic corrosion can be prevented.

[0005] However, when an insulating bush is provided, the crankshaft is inserted into the rolling bearing, and the insertion surface of the crankshaft is made of resin, which is easily damaged during insertion. In addition, the resin part of the insulating bush is softer than the metal part, so if the crankshaft is inserted at an angle, it is more likely to be damaged, which reduces the ease of insertion. Furthermore, inserting the insulating bush makes it difficult to supply lubricating oil, which can reduce the lubrication of the rolling bearing.

[0006] Therefore, there has been a demand for further technology to provide an insulating bush to prevent electrolytic corrosion, reduce damage during manufacturing, improve lubrication, and increase the reliability of refrigerant compressors. [Prior art documents] [Patent documents]

[0007] [Patent Document 1] JP 2021-143713 A Summary of the Invention [Problem to be solved by the invention]

[0008] The present invention has been made in consideration of the problems in the conventional technology described above, and has an object to provide a refrigerant compressor having improved reliability in a configuration in which an insulating bush is provided in an auxiliary bearing, and an air conditioning apparatus using the same. [Means for solving the problem]

[0009] That is, according to the present invention, A refrigerant compressor that compresses a refrigerant in a refrigeration cycle, A crankshaft that rotates integrally with an electric motor that includes a stator and a rotor; a bearing for supporting the compression mechanism side and the bottom side of the crankshaft; Equipped with The bearing includes an insulating bush made of a resin member and a metal member, A portion of the crankshaft that is inserted into the bearing has a tapered shape. A refrigerant compressor is provided. Effect of the Invention

[0010] According to the present invention, it is possible to provide a refrigerant compressor having improved reliability in a configuration in which an insulating bush is provided in an auxiliary bearing, and an air conditioner using the same. [Brief description of the drawings]

[0011] [Figure 1] FIG. 2 is a cross-sectional view showing the structure of a refrigerant compressor according to the embodiment. [Diagram 2] FIG. 2 is an enlarged cross-sectional view of the vicinity of a sub-bearing of the refrigerant compressor of the embodiment. [Diagram 3] FIG. 4 is a cross-sectional view showing the structure of the auxiliary bearing of the embodiment. [Figure 4] FIG. 2 is a diagram showing the structure of a crankshaft according to the embodiment; [Diagram 5] FIG. 4 is an enlarged cross-sectional view of the insulating bush of the embodiment. [Figure 6] 5A to 5C are diagrams illustrating examples of a gap provided between a crankshaft and an insulating bush in the embodiment. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0012] The present invention will be described below with reference to an embodiment, but the present invention is not limited to the embodiment described below. In addition, in each drawing referred to below, the same reference numerals are used for common elements, and the description thereof will be omitted as appropriate.

[0013] In the embodiment described below, a volumetric scroll compressor is used as an example of the refrigerant compressor 1, but this is not intended to limit the embodiment. Therefore, other types of compressors, such as rotary, reciprocating, and screw types, may also be used.

[0014] Fig. 1 is a cross-sectional view showing the structure of a refrigerant compressor 1 in this embodiment. The refrigerant compressor 1 shown in Fig. 1 is configured as a vertical scroll compressor, with a compression mechanism and a drive unit that drives the compression mechanism housed in a sealed container 28. The sealed container 28 is cylindrical, and from the top, the compression mechanism, the drive unit, and an oil reservoir 37 are arranged in this order inside the sealed container 28. The compression mechanism is connected to the drive unit via a crankshaft 33. The balance weight 18 is attached to the crankshaft 33.

[0015] The compression mechanism is composed of the fixed scroll 13, the orbiting scroll 14 which faces and meshes with the fixed scroll 13, and a frame 16 which fixes the fixed scroll 13 as basic elements. The frame 16 is fixed to the sealed container 28 and has a bearing support part in which a cylindrical roller bearing 31, which is a rolling bearing, is installed, and a support part which extends in the outer diameter direction from the upper part of the bearing support part and fixes the fixed scroll 13. The support part has a flat lower surface and is disposed above the discharge port 30 which is provided so as to penetrate the sealed container 28, and the outer peripheral surface of this support part is fixed to the inner peripheral surface of the sealed container 28 at a plurality of points in the circumferential direction by welding. The frame cover 32 covers the lower end surface of the frame 16 and is used to hold the cylindrical roller bearing 31.

[0016] The fixed scroll 13 includes a fixed scroll base plate 12 and a scroll wrap vertically provided below the fixed scroll base plate 12, and also includes a suction port 11 on the outer periphery of the fixed scroll base plate 12 and a discharge port 21 at the center of the fixed scroll base plate 12. The fixed scroll 13 is fixed to a frame 16 by a plurality of bolts, which are evenly arranged in the circumferential direction.

[0017] The orbiting scroll 14 includes an orbiting scroll base plate 27 and a scroll wrap vertically provided on the upper side of the orbiting scroll base plate 27. An orbiting boss is provided at the center of the orbiting scroll base plate 27 on the side opposite the scroll wrap so as to protrude vertically, and an orbiting bearing made of a plain bearing is press-fitted into the orbiting boss.

[0018] In the compression mechanism of the refrigerant compressor 1 of this embodiment, a compression chamber is formed by meshing the fixed scroll 13 and the orbiting scroll 14, and a compression process is performed in which the volume of the compression chamber is reduced by the orbiting motion of the orbiting scroll 14. That is, a suction pipe is provided so as to penetrate the lid cap 25 of the sealed container 28 and connect to the suction port 11, and refrigerant gas in a refrigeration cycle (not shown) is sucked into the compression chamber through the suction pipe and the suction port 11 as the orbiting motion of the orbiting scroll 14 occurs.

[0019] The refrigerant gas sucked into the compression chamber undergoes a compression process, is discharged from the discharge port 21 of the fixed scroll 13 into the discharge chamber 26 at the upper part of the sealed container 28, and then flows to the drive section through a communication passage (not shown) formed on the outer circumferential surface of the frame 16. The compressed refrigerant gas that has flowed into the drive section flows out from the discharge port 30 into the refrigeration cycle. With this configuration, the space within the sealed container 28 is maintained at discharge pressure.

[0020] The seal ring 15 is provided in a groove in the upper surface of the frame 16 facing the lower end surface of the orbiting boss. The seal ring 15 prevents refrigerant gas and oil at discharge pressure from flowing into the back pressure chamber formed on the back surface of the orbiting scroll 14. Therefore, the back pressure chamber is at an intermediate pressure between the discharge pressure and the suction pressure, and the orbiting scroll 14 is pressed against the fixed scroll 13 by the combined force of the intermediate pressure in the back pressure chamber and the discharge pressure acting on the inside of the seal ring 15.

[0021] The drive unit for causing the orbiting scroll 14 to orbit is composed of an electric motor 20 having a stator 20a and a rotor 20b, a crankshaft 33 that rotates integrally with the rotor 20b, and an Oldham ring 29 for preventing the orbiting scroll 14 from rotating on its axis.

[0022] The crankshaft 33 is composed of a shaft portion 33a of the cylindrical roller bearing 31 which is rotatably supported by the cylindrical roller bearing 31 provided in the bearing support portion of the frame 16, a shaft portion 33b of the ball bearing 34 which is rotatably supported by the ball bearing 34 which is provided below the electric motor 20 and attached to the sealed container 28 via a ball bearing portion side frame 35, and an eccentric pin portion which is provided on the upper end side of the shaft portion 33a of the cylindrical roller bearing 31 and is inserted into and engaged with the orbiting bearing of the orbiting scroll 14. The shaft portion 33a of the cylindrical roller bearing 31 and the shaft portion 33b of the ball bearing 34 are formed on the same axis, and the eccentric pin portion is provided eccentrically with respect to the shaft portion 33a of the cylindrical roller bearing 31. The eccentric pin portion is engaged with the orbiting bearing of the orbiting scroll 14 so as to be movable in the axial direction and rotatable.

[0023] An oil supply pump 24 is fixed by bolts to the lower end of the crankshaft 33. An oil supply passage 33c (see FIG. 2) is formed inside the crankshaft 33 so as to penetrate in the axial direction, and oil (refrigeration oil) in an oil reservoir 37 at the bottom of the sealed container 28 is supplied to the oil supply passage 33c via the oil supply pump 24. An oil supply hole 33d (see FIG. 2) is provided in the shaft portion 33b of the ball bearing 34, branching radially from the oil supply passage 33c and supplying oil to the ball bearing 34.

[0024] The oil supplied from oil supply pump 24 through oil supply passage 33c into the swivel boss at the end of the eccentric pin lubricates the swivel bearing, and then some of the oil passes through oil supply hole 33d and oil supply groove (not shown) formed in the lower end face of the swivel boss, straddling seal ring 15, and is supplied to the back pressure chamber. The remaining oil lubricates cylindrical roller bearing 31, and then is returned to oil reservoir 37 through oil drain pipe 19.

[0025] Next, a description will be given of the structure of the compressor, which is composed of the cylindrical roller bearing 31 and the ball bearing 34. The cylindrical roller bearing 31 is disposed above the electric motor 20 on the crankshaft 33. On the other hand, the ball bearing 34 is disposed below the electric motor 20. The cylindrical roller bearing 31 and the ball bearing 34 support the rotation of the crankshaft 33.

[0026] Ball bearing 34 is provided inside housing 23 which is attached by bolts to ball bearing side frame 35 which is fixed by welding to sealed container 28. Housing 23 has an opening on the drive unit side (upper side) for inserting ball bearing 34. Ball bearing 34 is inserted into the opening from above.

[0027] A housing cover 22 that covers the opening is provided above the ball bearing 34. The housing cover 22 is intended to prevent the oil supplied to the ball bearing 34 from scattering toward the drive unit, and is configured to cover the portion from the outer periphery of the crankshaft 33 to the outer ring of the ball bearing 34.

[0028] The sealed container 28 has a lid cap 25 and a bottom cap 36. The lid cap 25 and the bottom cap 36 are fitted to cover the outside of the central cylindrical portion of the sealed container 28. The fitted ends of the sealed container 28 and the lid cap 25 or the bottom cap 36 are heated and welded from diagonally below and above by a welding torch. In addition, legs are attached to the bottom surface of the sealed container 28. A magnet 38 is provided inside the bottom cap 36 to attract and collect dust inside the refrigerant compressor 1.

[0029] A hermetic terminal 17 is provided on the side surface of the sealed container 28 so as to supply power to the electric motor 20. The hermetic terminal 17 is provided penetrating the sealed container 28 and is located between the electric motor 20 and the frame 16.

[0030] Next, the configuration of the ball bearing 34 of this embodiment will be described with reference to Fig. 2. Fig. 2 is an enlarged cross-sectional view of the vicinity of the ball bearing 34 of the refrigerant compressor 1 of this embodiment.

[0031] First, as shown in Fig. 2, the refrigerant compressor 1 in this embodiment is configured by inserting the ball bearing 34 into the housing 23 from an upper opening of the housing 23. The ball bearing 34 can be inserted into the housing 23 by, for example, press-fitting, but this is not a particular limitation of the embodiment. Thereafter, the housing cover 22 is fitted into the opening of the housing 23 so as to cover the upper opening of the ball bearing 34, and the ball bearing 34 is fixed. Then, the ball bearing 34 is inserted into the shaft portion 33b of the ball bearing 34 of the crankshaft 33 together with the housing 23, and the housing 23 is attached to the ball bearing portion side frame 35 with bolts, and the ball bearing 34 is fixed.

[0032] The arrows in Fig. 2 indicate the direction in which the lubricating oil flows. The oil supply pump 24 is connected to the lower end of the crankshaft 33 and fixed to the housing 23 with screws or the like. The crankshaft 33 is provided with an oil supply passage 33c formed to penetrate in the axial direction, and an oil supply hole 33d branching off from the oil supply passage 33c and formed in the radial direction. When the crankshaft 33 rotates and the oil supply pump 24 is driven, the oil supply pump 24 draws up the lubricating oil from the oil reservoir 37. The drawn-up lubricating oil is supplied to the insulating bush 344 via the oil supply passage 33c and the oil supply hole 33d.

[0033] Here, the structure of ball bearing 34 will be described with reference to Fig. 3. Fig. 3 is a cross-sectional view showing the structure of ball bearing 34 of this embodiment. Fig. 3(A) is a cross-sectional view of ball bearing 34, and Fig. 3(B) is a cross-sectional view of insulating bush 344 that constitutes ball bearing 34.

[0034] As shown in Fig. 3(A), ball bearing 34 of this embodiment is configured as a rolling bearing, and includes each of inner ring 341, outer ring 342, rolling element 343, and insulating bush 344. As shown in Fig. 3, rolling element 343 is provided between inner ring 341 and outer ring 342, and reduces friction when ball bearing 34 rotates.

[0035] In addition, as shown in Fig. 3(A), in the ball bearing 34 of this embodiment, an insulating bush 344 is fitted on the inner diameter side of the inner ring 341. The method of fitting the insulating bush 344 can be, for example, press-fitting, but this is not a particular limitation of the embodiment. As shown in Fig. 3(B), the insulating bush 344 is composed of a cylindrical resin member 344a and a metal member 344b. The resin member 344a is provided on the inner diameter of the metal member 344b and is fixed by a method such as adhesion.

[0036] As shown in Fig. 3, in this embodiment, an insulating bush 344 made of an insulating resin member 344a and a metal member 344b is disposed between the ball bearing 34 and the crankshaft 33. This makes it possible to block the axial current generated by inverter driving of the electric motor 20 from flowing through the crankshaft 33 into the ball bearing 34 made of a rolling bearing. Furthermore, providing the metal member 344b in the insulating bush 344 makes it possible to prevent the resin member 344a from falling off due to temperature changes. This makes it possible to prevent electrolytic corrosion occurring in the ball bearing 34 and suppress a decrease in the reliability of the refrigerant compressor 1.

[0037] Returning to Fig. 2 for the explanation, shaft portion 33b of ball bearing 34 in this embodiment has a groove formed along the axial direction on the surface of the portion where insulating bush 344 is disposed. Lubricating oil supplied from oil supply hole 33d to the back surface of insulating bush 344 passes through the groove and flows to the housing cover 22 side. The lubricating oil is guided between ball bearing 34 and housing cover 22, and then supplied to ball bearing 34.

[0038] Inside the housing 23, the gap between the housing cover 22 and the inner ring 341 is configured to be wide, forming a flow path through which the lubricating oil passes. The inner surface of the housing 23 is configured to be in contact with the outer ring 342 of the ball bearing 34. Therefore, the lubricating oil supplied through the oil supply hole 33d and the axial groove is supplied to the rolling elements 343 of the rolling bearing that constitutes the ball bearing 34 through the flow path formed between the housing cover 22 and the inner ring 341, and then discharged downward toward the oil reservoir 37.

[0039] In the embodiment described below, the ball bearing 34 is configured as a rolling bearing, but this is not a limitation of the embodiment. Therefore, a roller bearing may be used as the rolling bearing of the ball bearing 34, and in this case, the occurrence of electrolytic corrosion can be suppressed according to the configuration of this embodiment.

[0040] As described above, in the refrigerant compressor 1 of this embodiment, if the insulating bush 344 is provided on the ball bearing 34 to prevent electrolytic corrosion, the resin member 344a, which is softer than the metal crankshaft 33, may be damaged when assembling the ball bearing 34 and the crankshaft 33. In particular, when inserting the crankshaft 33 into the ball bearing 34 in an inclined state, the crankshaft 33 is likely to be damaged, which reduces the ease of insertion during the assembly work, and may be a factor in increasing costs due to reduced work efficiency.

[0041] Therefore, in this embodiment, the shape of the shaft portion 33b of the ball bearing 34 of the crankshaft 33 is tapered. Fig. 4 is a diagram showing the structure of the crankshaft 33 of this embodiment.

[0042] Conventionally, the end of the shaft portion 33b of the ball bearing 34 of the crankshaft 33 is generally chamfered to prevent the occurrence of burrs. However, when the insulating bush 344 is provided in the ball bearing 34 as in this embodiment, there is a possibility that the insertability may decrease, as described above. Therefore, in this embodiment, the end of the shaft portion 33b of the ball bearing 34 of the crankshaft 33 is machined into a tapered shape as shown in FIG.

[0043] This allows the contact angle between the resin member 344a and the shaft portion 33b of the ball bearing 34 to be shallow during assembly. This makes it easier to insert the crankshaft 33 into the ball bearing 34. This prevents the resin member 344a from galling during assembly, and prevents a decrease in insertability. In order to further improve insertability, the end of the inner circumferential surface of the resin member 344a may be chamfered.

[0044] In this embodiment, from the viewpoint of improving insertability, the length L of the tapered portion of the shaft portion 33b of the ball bearing 34 can be set to 3 mm or more. Also, in this embodiment, from the viewpoint of improving insertability, the angle θ between the ridge line of the tapered portion of the shaft portion 33b of the ball bearing 34 and the rotation axis can be set to 15° or less.

[0045] Furthermore, when the insulating bush 344 is provided on the ball bearing 34, the resin member 344a may cling to the crankshaft 33 due to a rise in temperature during operation, due to the fact that the linear expansion coefficient of the resin member 344a is larger than that of the metal member 344b. Furthermore, by providing the insulating bush 344 on the ball bearing 34, the slits for supplying lubricating oil provided on the shaft portion 33b of the ball bearing 34 may be filled by the thermal expansion of the resin member 344a, which may impede the supply of oil.

[0046] Therefore, in this embodiment, a gap is provided between the shaft portion 33b of the ball bearing 34 of the crankshaft 33 and the resin member 344a of the insulating bush 344 to prevent sticking and a decrease in the amount of oil supplied due to thermal expansion. Fig. 5 is an enlarged cross-sectional view of the insulating bush 344 of this embodiment. The structure shown in Fig. 5 is an enlarged view of the area A indicated by the dashed line in Fig. 1.

[0047] As shown in FIG. 5, a radial gap is provided between the shaft portion 33b of the ball bearing 34 of the crankshaft 33 and the resin member 344a of the insulating bush 344. The insulating bush 344 thermally expands due to temperature changes during operation, but the force of the resin member 344a expanding outward is suppressed by the metal member 344b, so that the resin member 344a expands inward (toward the crankshaft 33). In this embodiment, as shown in FIG. 5, a gap is provided between the crankshaft 33 and the insulating bush 344, so that even if the resin member 344a of the insulating bush 344 expands, the resin member 344a does not stick to the crankshaft 33. In addition, the presence of a gap between the crankshaft 33 and the insulating bush 344 allows lubricating oil to be appropriately supplied from the oil supply hole 33d, ensuring lubrication.

[0048] Here, the gap between the crankshaft 33 and the insulating bush 344 (hereinafter, may be simply referred to as "gap") will be described with reference to Fig. 6. Fig. 6 is a diagram illustrating an example of the gap provided between the crankshaft 33 and the insulating bush 344 in this embodiment. Fig. 6(A) shows an example before the refrigerant compressor 1 is driven, i.e., before thermal expansion, and Fig. 6(B) shows an example after the refrigerant compressor 1 is driven, i.e., after thermal expansion.

[0049] The gap between the crankshaft 33 and the insulating bush 344 is preferably sized to prevent sticking while ensuring the function of reducing friction. Generally, the linear expansion coefficient of resin is about twice that of metal. The temperature of the insulating bush 344 during operation of the refrigerant compressor 1 generally rises from room temperature by about 85°C to about 115°C. Therefore, when the thermal expansion of the resin member 344a is calculated based on these general conditions, a change of about 0.12% to about 0.16% occurs.

[0050] Here, as shown in Fig. 6(A), consider the case where the diameter of shaft portion 33b of ball bearing 34 of crankshaft 33 is 25 mm. In this case, taking into consideration the thermal expansion of resin member 344a of insulating bushing 344 during driving, it is preferable to provide a gap that is approximately 0.12% to 0.16% larger than the diameter. That is, when shaft portion 33b of ball bearing 34 has a diameter of 25 mm, insulating bushing 344 is provided with a dimension that provides a gap of approximately 0.029 mm to 0.040 mm, as shown in Fig. 6(A).

[0051] By providing the insulating bush 344 with such dimensions, when the refrigerant compressor 1 is driven and the resin member 344a thermally expands in the inner diameter direction, the shaft portion 33b of the ball bearing 34 and the resin member 344a do not stick to each other as shown in Fig. 6(B), and the lubricating oil can be appropriately supplied. Therefore, the lubrication of the crankshaft 33 can be ensured, and the reliability of the refrigerant compressor 1 can be improved.

[0052] According to this embodiment, the refrigerant compressor 1 is realized with improved reliability while preventing electrolytic corrosion. In addition, since the insulating bush 344 is used to prevent electrolytic corrosion, it is possible to prevent electrolytic corrosion at a lower cost than in the conventional auxiliary bearing that uses ceramic rolling elements.

[0053] According to the embodiment of the present invention described above, it is possible to provide a refrigerant compressor with improved reliability in a configuration in which an insulating bush is provided in an auxiliary bearing, and an air conditioner using the same.

[0054] Although the present invention has been described above with reference to an embodiment, the present invention is not limited to the above-described embodiment, and as long as the functions and effects of the present invention are achieved within the scope of embodiments that a person skilled in the art can imagine, they are included in the scope of the present invention. [Explanation of symbols]

[0055] 1...Refrigerant compressor, 11…intake port, 12...Fixed scroll base plate, 13…Fixed scroll, 14...Rotating scroll, 15…Seal ring, 16…Frame, 17...Herme terminal, 18…Balance weight, 19…Oil drain pipe, 20...Electric motor, 20a…stator, 20b...rotor, 21...Discharge port, 22…Housing cover, 23…Housing, 24…Fuel pump, 25…Lid cap, 26...discharge chamber, 27...Turning scroll base plate, 28...sealed container, 29…Oldham Ring, 30...Discharge port, 31...Cylindrical roller bearing, 32…Frame cover, 33…Crankshaft, 33a...Axle portion of cylindrical roller bearing, 33b...ball bearing shaft portion, 33c…Fuel passage, 33d…Oil hole, 34...Ball bearing, 341…Inner circle, 342…Outer ring, 343...Rolling elements, 344…insulating bush, 344a…Resin member, 344b…Metal parts, 35...Ball bearing side frame, 36…Bottom cap, 37...Oil reservoir, 38…Magnet

Claims

1. A refrigerant compressor that compresses a refrigerant in a refrigeration cycle, A crankshaft that rotates integrally with an electric motor that includes a stator and a rotor; a bearing for supporting the compression mechanism side and the bottom side of the crankshaft; Equipped with the bearing includes an insulating bushing made of a resin member provided on an inner diameter side and a metal member provided on an outer diameter side, a portion of the crankshaft that is inserted into the bearing has a tapered shape, a gap is provided between the cylindrical portion of the crankshaft and the resin member, The crankshaft is characterized in that a hole is provided to supply lubricating oil to the gap. Refrigerant compressor.

2. 2. The refrigerant compressor according to claim 1, wherein the length of the tapered portion is 3 mm or more.

3. 2. The refrigerant compressor according to claim 1, wherein an angle formed between a ridge line of the tapered portion and a rotation axis of the crankshaft is 15 degrees or less.

4. 2. The refrigerant compressor according to claim 1, wherein an end portion of an inner circumferential surface of the resin member is chamfered.

5. 2. The refrigerant compressor of claim 1, wherein the bearing is a rolling bearing.

6. 2. The refrigerant compressor according to claim 1, wherein the gap is 0.12% to 0.16% larger than a diameter of the crankshaft.

7. 7. The refrigerant compressor according to claim 6, wherein the crankshaft has a diameter of 25 mm, and the gap is between 0.029 mm and 0.040 mm.

8. An air-conditioning apparatus comprising the refrigerant compressor according to any one of claims 1 to 7.

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