Scroll Compressor

Abstract

A scroll compressor (100) is configured so as to rotate a turning scroll (12) by fitting an eccentric shaft (13a) to a turning bearing (13d) of the turning scroll (12). The turning bearing (13d) or the eccentric shaft (13a) is imparted with a tapered shape. Due to this configuration, in the turning scroll (12), the distance between a point at which a compression load is received and a point at which the eccentric shaft (13a) rotates while pressing on the turning bearing (13d) is decreased, and thus an upsetting moment of the turning scroll (12) is reduced and the behavior of the turning scroll is stabilized, thereby enabling provision of a scroll compressor that is highly efficient and reliable.

Description

[Technical field]

[0001] The present disclosure relates to a scroll compressor used in particular in an air conditioner, a water heater, or a refrigeration machine such as a refrigerator. [Background technology]

[0002] Patent Document 1 discloses a scroll compressor used in air conditioners, etc. This scroll compressor is configured such that a back pressure region is provided on the opposite wrap surface of the orbiting scroll end plate, and the orbiting scroll is pressed against the fixed scroll, thereby suppressing the overturning of the orbiting scroll, reducing leakage loss, and improving theoretical efficiency and heating / cooling capacity. [Prior art documents] [Patent documents]

[0003] [Patent Document 1] Patent No. 4892238 Summary of the Invention

[0004] The present disclosure provides a highly efficient and reliable scroll compressor by more reliably suppressing the overturning of the orbiting scroll.

[0005] The scroll compressor of the present disclosure is configured such that a back pressure region is formed on the opposite wrap surface of the end plate of the orbiting scroll, and the orbiting scroll is pressed against the fixed scroll. The wrap side of the orbiting bearing of the orbiting scroll is closed by the end plate, and the crankshaft side is open. The scroll compressor is configured such that the orbiting bearing of the orbiting scroll has a tapered shape in which the diameter gradually increases toward the open side of the orbiting bearing, or the eccentric shaft inserted into the orbiting bearing has a tapered shape in which the diameter gradually decreases toward the open side of the orbiting bearing. [Brief description of the drawings]

[0006] [Figure 1]FIG. 1 is a vertical sectional view of a scroll compressor according to a first embodiment. [Diagram 2] FIG. 2 is an enlarged cross-sectional view of a main portion showing a compression mechanism of the scroll compressor. [Figure 3A] FIG. 3A is a diagram showing a change in the volume of a compression chamber accompanying the orbital motion of the scroll compressor. [Figure 3B] FIG. 3B is another diagram showing a change in volume of a compression chamber accompanying the orbital motion of the scroll compressor. [Figure 3C] FIG. 3C is still another diagram showing a change in volume of a compression chamber accompanying the orbital motion of the scroll compressor. [Figure 3D] FIG. 3D is still another diagram showing a change in the volume of a compression chamber accompanying the orbital motion of the scroll compressor. [Figure 4A] FIG. 4A is a diagram showing the rotation shaft of the scroll compressor during compression operation. [Figure 4B] FIG. 4B is a diagram showing the inclination of the rotation axis of the scroll compressor during compression operation. [Figure 5A] FIG. 5A is a diagram showing an example of a tapered shape provided on an orbiting bearing of the scroll compressor and an inclination of a rotation axis. [Figure 5B] FIG. 5B is an explanatory diagram showing the load and overturning moment acting on the eccentric bearing during the gas compression process of the scroll compressor. [Figure 6A] FIG. 6A is an explanatory diagram showing the load and overturning moment acting on an eccentric bearing during a gas compression process in a scroll compressor having an orbiting bearing or an eccentric shaft with a taper. [Figure 6B] FIG. 6B is an explanatory diagram showing that the overturning moment is suppressed by a tapered shape provided on the orbiting bearing or the eccentric shaft of the scroll compressor. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0007] (The knowledge and other information that formed the basis of this disclosure) At the time when the inventors came up with the present disclosure, scroll compressors used back pressure to press the orbiting scroll against the fixed scroll to make the behavior of the orbiting scroll more stable. However, the inventors discovered that in such a configuration, when the overturning moment caused by the tangential gas load on the wrap side of the orbiting scroll becomes larger than the stabilizing moment caused by the back pressure applied to the orbiting scroll, the orbiting scroll separates from the fixed scroll. When the orbiting scroll separates from the fixed scroll, the performance of the scroll compressor is reduced due to leakage of refrigerant between adjacent compression chambers or between an intermediate pressure region and a compression chamber. In order to solve this problem, the inventors came up with the subject of the present disclosure.

[0008] The present disclosure provides a highly efficient and reliable scroll compressor by suppressing overturning of the orbiting scroll.

[0009] Hereinafter, the embodiments will be described in detail with reference to the drawings. However, more detailed explanation than necessary may be omitted. For example, detailed explanation of already well-known matters or duplicate explanation of substantially the same configuration may be omitted. This is to avoid the following explanation becoming more redundant than necessary and to facilitate understanding by those skilled in the art.

[0010] It should be noted that the accompanying drawings and the following description are provided to enable those skilled in the art to fully understand the present disclosure, and are not intended to limit the subject matter described in the claims.

[0011] (Embodiment 1) Hereinafter, the first embodiment will be described with reference to FIGS. 1 to 6B.

[0012] [1-1. Configuration] As shown in FIG. 1, a scroll compressor 100 is configured by disposing a compression mechanism unit 10 that compresses a refrigerant and an electric mechanism unit 20 that drives the compression mechanism unit 10 in a sealed container 1.

[0013] The sealed container 1 is composed of a body 1a formed in a cylindrical shape extending in the vertical direction, a lower lid 1b that closes the lower opening of the body 1a, and an upper lid 1c that closes the upper opening of the body 1a. The sealed container 1 is provided with a refrigerant suction pipe 2 that introduces a refrigerant to the compression mechanism 10, and a refrigerant discharge pipe 3 that discharges the refrigerant compressed by the compression mechanism 10 to the outside of the sealed container 1.

[0014] The compression mechanism 10 has a fixed scroll 11, an orbiting scroll 12, and a rotation shaft 13 that drives the orbiting scroll 12 to orbit.

[0015] The electric mechanism 20 includes a stator 21 fixed to the sealed container 1, and a rotor 22 arranged inside the stator 21. The above-mentioned rotating shaft 13 is fixed to the rotor 22. An eccentric shaft 13a that is eccentric with respect to the rotating shaft 13 is formed at the upper end of the rotating shaft 13. An oil reservoir is formed in the eccentric shaft 13a by a recess that opens to the upper surface of the eccentric shaft 13a.

[0016] Below the fixed scroll 11 and the orbiting scroll 12, a main bearing 30 that supports the fixed scroll 11 and the orbiting scroll 12 is provided.

[0017] The main bearing 30 is configured with a bearing portion 31 that supports the rotating shaft 13, and a boss receiving portion 32. The main bearing 30 is fixed to the sealed container 1 by welding, shrink fitting, or the like.

[0018] The fixed scroll 11 includes a disk-shaped fixed scroll end plate 11a, a spiral-shaped fixed spiral wrap 11b standing upright from the fixed scroll end plate 11a, and an outer peripheral wall portion 11c standing upright so as to surround the periphery of the fixed spiral wrap 11b. A discharge port 14 is formed in the approximate center of the fixed scroll end plate 11a.

[0019] The orbiting scroll 12 includes a disk-shaped orbiting scroll end plate 12a, an orbiting spiral wrap 12b standing on one surface (wrap side end surface) of the orbiting scroll end plate 12a, and a cylindrical boss portion 12c formed on the other surface (opposite wrap side end surface) of the orbiting scroll end plate 12a. The other surface of the orbiting scroll end plate 12a is the surface opposite to the wrap side end surface of the orbiting scroll end plate 12a.

[0020] The orbiting bearing 13d is fitted into the cylindrical boss portion 12c as shown in Fig. 2. The wrap side of the orbiting bearing 13d is closed by the orbiting scroll end plate 12a, and the anti-wrap side is open. The eccentric shaft 13a of the rotating shaft 13 is inserted from the open side of the orbiting bearing 13d. In the following description, the end of the orbiting bearing 13d on the wrap side may be referred to as a first end 13da, and the end on the open side may be referred to as a second end 13db.

[0021] The fixed spiral wrap 11b of the fixed scroll 11 and the orbiting spiral wrap 12b of the orbiting scroll 12 are meshed with each other, and a plurality of compression chambers 15 are formed between the fixed spiral wrap 11b and the orbiting spiral wrap 12b.

[0022] The boss portion 12c is formed substantially at the center of the orbiting scroll end plate 12a. The boss portion 12c is accommodated in the boss accommodating portion 32 with the eccentric shaft 13a inserted into the boss portion 12c.

[0023] The fixed scroll 11 is fixed to the main bearing 30 at its outer circumferential wall portion 11c by a plurality of bolts (not shown). On the other hand, the movement of the orbiting scroll 12 relative to the fixed scroll 11 is restricted by a rotation restraining member 17 such as an Oldham ring. The rotation restraining member 17, which restrains the rotation of the orbiting scroll 12, is provided between the fixed scroll 11 and the main bearing 30. As a result, the orbiting scroll 12 orbits without rotating relative to the fixed scroll 11 as the eccentric shaft 13a of the rotating shaft 13 rotates by crank.

[0024] An oil reservoir 4 for storing lubricating oil is formed at the bottom of the sealed container 1. A lower end 13b of the rotating shaft 13 is journalled by a sub-bearing 18 arranged at the bottom of the sealed container 1.

[0025] A positive displacement oil pump 5 is provided at the lower end of the rotating shaft 13. The oil pump 5 is arranged so that its suction port is located inside the oil reservoir 4. The oil pump 5 is driven by the rotating shaft 13 and reliably draws up the lubricating oil in the oil reservoir 4 provided at the bottom of the sealed container 1 regardless of pressure conditions or operating speed, eliminating concerns about running out of oil.

[0026] A rotating shaft oil supply hole 13c is formed in the rotating shaft 13, which extends from the lower end 13b of the rotating shaft 13 to the eccentric shaft 13a. The lubricating oil pumped up by the oil pump 5 is supplied to the bearing of the sub-bearing 18, the bearing portion 31, and the boss portion 12c through the rotating shaft oil supply hole 13c formed in the rotating shaft 13.

[0027] The refrigerant sucked through the refrigerant suction pipe 2 is guided through the suction port 15a to the compression chamber 15. The compression chamber 15 moves from the outer periphery toward the center while reducing its volume. When the refrigerant reaches a predetermined pressure in the compression chamber 15, it is discharged from the discharge port 14 provided in the center of the fixed scroll 11 to the discharge chamber 6. A discharge reed valve (not shown) is provided in the discharge port 14. When the refrigerant reaches a predetermined pressure in the compression chamber 15, it pushes open the discharge reed valve, and the refrigerant is discharged into the discharge chamber 6. The refrigerant discharged into the discharge chamber 6 is led to the upper part of the sealed container 1 and discharged from the refrigerant discharge pipe 3.

[0028] 2, in the scroll compressor 100 of this embodiment, the boss accommodating portion 32 is a high pressure region A, and the outer periphery of the orbiting scroll 12 on which the rotation restraining member 17 is arranged is an intermediate pressure region B. The orbiting scroll 12 is pressed against the fixed scroll 11. The configuration will be described below.

[0029] The eccentric shaft 13a is inserted into the boss portion 12c via a swivel bearing 13d so as to be rotatable about the boss portion 12c. An oil groove 13e is formed on the outer circumferential surface of the eccentric shaft 13a.

[0030] A ring-shaped seal member 33 is provided on a thrust surface of the main bearing 30 that receives the thrust force from the orbiting scroll end plate 12a. The seal member 33 is disposed on the outer periphery of the boss accommodating portion 32.

[0031] The sealed container 1 is filled with the same high-pressure refrigerant as the refrigerant discharged to the discharge chamber 6. The rotating shaft oil supply hole 13c opens at the upper end of the eccentric shaft 13a. Therefore, the inside of the boss portion 12c becomes a high-pressure region A equivalent to the discharged refrigerant.

[0032] The lubricating oil introduced into the boss portion 12c through the rotating shaft oil supply hole 13c is supplied to the orbiting bearing 13d and the boss accommodating portion 32 by the oil groove 13e formed on the outer circumferential surface of the eccentric shaft 13a. A seal member 33 is provided on the outer periphery of the boss accommodating portion 32, so that the inside of the boss accommodating portion 32 becomes a high-pressure region A.

[0033] The orbiting scroll end plate 12a is provided with a first oil inlet hole 51 formed toward the inside of the boss portion 12c, a first oil outlet hole 52 opening into the outer periphery of the wrap side end face, and a first end plate oil communication passage 53 connecting the first oil inlet hole 51 and the first oil outlet hole 52.

[0034] The orbiting scroll end plate 12a is provided with a second oil introduction hole 61 that opens into the intermediate pressure region B in the outer periphery of the orbiting scroll 12, a second oil discharge hole 62 that opens into the compression chamber 15, and a second end plate oil communication passage 63 that communicates between the second oil introduction hole 61 and the second oil discharge hole 62. In the example of the present embodiment, the second oil introduction hole 61 is formed so as to open into the upper surface of the orbiting scroll end plate 12a.

[0035] With this configuration, the intermediate pressure region B and the compression chamber 15 are intermittently connected by the second oil outlet hole 62 of the orbiting scroll 12. This allows the intermediate pressure of the compression chamber 15 to be introduced into the intermediate pressure region B, and the orbiting scroll 12 can be pressed against the fixed scroll 11 with a minimum necessary load even under various operating conditions. This reduces friction loss in the compressor, prevents the orbiting scroll 12 from moving away from the fixed scroll 11, and improves the airtightness of the compression chamber 15.

[0036] 3A to 3D are diagrams showing a change in the volume of a compression chamber accompanying an orbital motion in the scroll compressor of this embodiment, and are diagrams showing a state in which the orbiting scroll 12 is engaged with the fixed scroll 11, as viewed from the back of the orbiting scroll 12. Fig. 3B shows a state after 90 degrees of rotation from Fig. 3A, Fig. 3C shows a state after a further 90 degrees of rotation from Fig. 3B, and Fig. 3D shows a state after a further 90 degrees of rotation from Fig. 3C.

[0037] A plurality of compression chambers 15 are formed by the fixed scroll 11 and the orbiting scroll 12. As shown in Fig. 3A, a first compression chamber 15A is formed on the outer wall side of the orbiting spiral wrap 12b, and as shown in Fig. 3C, a second compression chamber 15B is formed on the inner wall side of the orbiting spiral wrap 12b.

[0038] The outer peripheral end 11be of the fixed spiral wrap 11b is extended so that the outer peripheral end 11be of the fixed spiral wrap 11b and the outer peripheral end 12be of the orbiting spiral wrap 12b are at the same position when the fixed scroll 11 and the orbiting scroll 12 are engaged with each other. This allows the position where the refrigerant is trapped in the first compression chamber 15A and the position where the refrigerant is trapped in the second compression chamber 15B to be shifted by approximately 180 degrees. The suction volume of the first compression chamber 15A is configured to be larger than the suction volume of the second compression chamber 15B.

[0039] Here, in the scroll compressor 100 of this embodiment, the inner diameter surface 13dc of the orbiting bearing 13d has a tapered shape (first tapered shape T1) in which the diameter becomes larger toward the end point (second end 13db) on the open side as shown in Fig. 5A. Alternatively, in the scroll compressor 100, the eccentric shaft 13a may have a tapered shape (second tapered shape T2) in which the diameter becomes smaller toward the open side of the orbiting bearing 13d as shown in Fig. 5B. In a cross-sectional view of the swivel bearing 13d in a plane including the axis of the swivel bearing 13d, the angle θ formed by the first taper shape T1 or the second taper shape T2 and the axis of the swivel bearing 13d is equal to or greater than the maximum angle to which the rotating shaft 13 can be inclined, and may be set so as to satisfy the following relational expression when the distance between the upper end (first end 13da) of the swivel bearing 13d and the starting point of the taper is L, the diameter of the eccentric shaft is d, and the diameter of the inner wall of the eccentric bearing is D.

[0040]

number

[0041] In this embodiment, the maximum angle to which the rotating shaft 13 can be tilted is determined by the clearance between the main bearing 30 and the rotating shaft 13 and the clearance between the sub-bearing 18 and the rotating shaft 13, as shown in Figures 4A and 4B.

[0042] The tapered shape of the swivel bearing 13d or the tapered shape of the eccentric shaft 13a may be configured to start from a position midway in the sliding range between the inner wall 13dc of the eccentric bearing 13d and the outer periphery 13ab of the eccentric shaft 13a, which are the sliding surfaces of each other in the axial direction of the eccentric bearing 13d, as shown in Figures 5A and 5B. The tapered shape formed on the swivel bearing 13d or the eccentric shaft 13a may be configured by a straight line, a continuous curve, or a combination of these.

[0043] [1-2. Operation] The operation and function of the scroll compressor 100 configured as above will be described below.

[0044] 4A and 4B show the rotating state of the rotating shaft 13 that rotates the orbiting scroll. FIG. 4A shows a state where there is no compression load, and FIG. 4B shows a state where there is a compression load. In the scroll compressor 100, when gas is compressed, the eccentric shaft 13a located at the end of the rotating shaft 13 rotates while pressing the orbiting bearing 13d of the orbiting scroll 12. At this time, the orbiting scroll 12 is kept pressed against the fixed scroll 11 by the back pressure applied to the opposite wrap surface of the orbiting scroll end plate 12a of the orbiting scroll 12. Therefore, as shown in FIG. 4B, the eccentric shaft 13a receives a force in a direction substantially opposite to the direction in which the refrigerant is compressed, and the rotating shaft 13 tries to rotate in a state in which it is tilted by the clearance between the main bearing 30 and the sub bearing 18.

[0045] The load and overturning moment applied to the slewing bearing 13d during the gas compression process are as shown in Figures 6A and 6B. Figure 6A shows the case where the slewing bearing 13d has no taper, and Figure 6B shows the case where the slewing bearing 13d has a taper. The lower left corners of Figures 6A and 6B show the magnitude of the reaction force of gas compression applied to the slewing bearing 13d (bearing load) in each case.

[0046] In the case of Fig. 6B in which the orbiting bearing 13d has a tapered shape, even if the rotating shaft 13 rotates in a state inclined with respect to the axis, it is possible to prevent the reaction force of the gas compression force from concentrating on the lower end (second end 13db) of the orbiting bearing 13d. Therefore, the overturning moment Z that tends to overturn the orbiting scroll 12 can be suppressed. In other words, the distance between the force point at which the orbiting scroll 12 receives the tangential gas load on the orbiting scroll wrap side and the point at which the orbiting scroll 12 receives the reaction force is reduced, so that the overturning moment that tends to overturn the orbiting scroll 12 can be suppressed. Therefore, the behavior of the orbiting scroll 12 is stabilized, so that the reliability of the compressor is improved and a highly efficient scroll compressor can be obtained.

[0047] In the case of FIG. 6A, the reaction force of gas compression is concentrated at the lower end (second end 13db) of the revolving bearing 13d, so the clearance between the eccentric shaft 13a and the revolving bearing 13d becomes larger toward the upper end (first end 13da) of the revolving bearing 13d. This makes it difficult to uniformly form an oil film between the eccentric shaft 13a and the revolving bearing 13d. On the other hand, in the case of FIG. 6B, an appropriate clearance is formed between the eccentric shaft 13a and the revolving bearing 13d, so that metal contact can be prevented and the formation of an oil film in the sliding portion can be promoted. In other words, the gap between the inclined eccentric shaft 13a and the revolving bearing 13d can be appropriately set, and localized metal contact can be prevented by forming an oil film in the gap. This results in a compressor with even higher efficiency.

[0048] In this embodiment, the tapered shape of the swivel bearing 13d or the eccentric shaft 13a starts halfway between their sliding surfaces, so the gap between the eccentric shaft 13a and the swivel bearing 13d can be made smallest at the taper start point. This makes it possible to prevent the surface pressure from becoming locally high at the lower end (second end 13db) of the open side of the swivel bearing 13d, and promotes the formation of an oil film on the sliding portion.

[0049] The tapered shape formed on the orbiting bearing 13d or the eccentric shaft 13a may be a straight line, a continuous curve, or a combination of these. This makes it possible to further disperse localized surface pressure, thereby providing a scroll compressor that is highly efficient with lower input power.

[0050] [1-3. Effects, etc.] As described above, the scroll compressor in this embodiment includes the compression mechanism 10 that compresses the refrigerant, the electric mechanism 20 that drives the compression mechanism 10, and the sealed container 1 that houses the compression mechanism 10 and the electric mechanism 20. The compression mechanism 10 includes the fixed scroll 11, the orbiting scroll 12, and the rotating shaft 13 that drives the orbiting scroll 12 to orbit. The fixed scroll 11 includes a disk-shaped fixed scroll end plate 11a and a fixed spiral wrap 11b that is erected on the fixed scroll end plate 11a, and the orbiting scroll 12 includes a disk-shaped orbiting scroll end plate 12a and an orbiting spiral wrap 12b that is erected on the wrap side end surface of the orbiting scroll end plate 12a. The fixed spiral wrap 11b and the orbiting spiral wrap 12b are mutually meshed, and a plurality of compression chambers 15 are formed between the fixed spiral wrap 11b and the orbiting spiral wrap 12b. The compression chamber 15 has a first compression chamber 15A formed on the outer wall side of the orbiting spiral wrap, and a second compression chamber 15B formed on the inner wall side of the orbiting spiral wrap 12b. The orbiting scroll 12 is pressed against the fixed scroll 11 by the back pressure formed on the opposite wrap surface side of the orbiting scroll end plate 12a. The wrap side of the orbiting bearing 13d of the orbiting scroll 12 is closed by the end plate, and the eccentric shaft 13a side of the rotating shaft 13 is open. The scroll compressor 100 is configured so that the orbiting bearing 13d has a tapered shape in which the diameter gradually increases toward the open side of the orbiting bearing 13d, or the eccentric shaft 13a of the rotating shaft 13 inserted into the orbiting bearing 13d has a tapered shape in which the diameter gradually decreases toward the open side of the orbiting bearing 13d.

[0051] According to this embodiment, the orbiting bearing 13d or the eccentric shaft 13a has a tapered shape, so that the distance between the force point when the tangential gas load is received by the orbiting scroll wrap side surface and the point receiving the reaction force of the orbiting bearing is small, and the overturning moment that tends to overturn the orbiting scroll 12 can be suppressed. Therefore, the behavior of the orbiting scroll 12 is stabilized, and a highly efficient scroll compressor can be obtained. Note that, in the case where the behavior of the orbiting scroll 12 is likely to become unstable due to a configuration in which the suction volume of the first compression chamber 15A is larger than the suction volume of the second compression chamber 15B, as in this embodiment, the behavior of the orbiting scroll 12 can be more effectively stabilized.

[0052] In this embodiment, the tapered shape of the swivel bearing 13d or the eccentric shaft 13a starts halfway along the sliding surface between the swivel bearing 13d and the eccentric shaft 13a. This prevents the surface pressure from becoming locally high at the lower end (second end 13db) of the open side of the swivel bearing 13d, and promotes the formation of an oil film between the sliding parts.

[0053] In this embodiment, the tapered shape formed on the orbiting bearing 13d or the eccentric shaft 13a is formed of a straight line, a continuous curve, or a combination of these. This makes it possible to further disperse localized surface pressure, thereby providing a scroll compressor that is highly efficient with a lower input.

[0054] The scroll compressor 100 of this embodiment is configured such that the diameter of the tapered shape provided on the revolving bearing 13d increases toward the open side of the revolving bearing 13d. In addition, in the cross section of the revolving bearing 13d in a plane including the axis of the eccentric bearing 13d, the angle θ between the tapered shape and the axis of the revolving bearing 13d is set to satisfy the following relational expression, where L is the distance between the upper end (first end 13da) of the revolving bearing 13d and the taper start point, d is the diameter of the eccentric shaft, and D is the diameter of the revolving bearing.

[0055]

number

[0056] This provides an appropriate clearance between the eccentric shaft and the slewing bearing, preventing metal-to-metal contact and promoting the formation of an oil film in the sliding portion.

[0057] The present disclosure has been described above using the above-mentioned embodiments. However, since the above-mentioned embodiments are intended to illustrate the technology in the present disclosure, various modifications, substitutions, additions, omissions, etc. can be made within the scope of the claims or their equivalents.

[0058] The refrigerant for the scroll compressor of the present disclosure can be R32, carbon dioxide, or a refrigerant having a double bond between carbon atoms. [Industrial Applicability]

[0059] INDUSTRIAL APPLICABILITY The scroll compressor according to the present disclosure can achieve high efficiency and is therefore useful in various refrigeration cycle devices such as hot water heating systems, air conditioners, water heaters, or refrigerators. [Explanation of symbols]

[0060] 1. Airtight container 1a Torso 1b Lower lid 1c top lid 2 Refrigerant suction pipe 3 Refrigerant discharge pipe 4 Oil storage section 5. Oil pump 6 Discharge chamber 10 Compression mechanism 11 Fixed Scroll 11a Fixed scroll head plate 11b Fixed spiral wrap 11be Outer edge 12 Swivel Scroll 12a Rotating scroll head plate 12b Swirling Spiral Wrap 12be Outer edge 12c Boss part 13 Rotation axis 13a Eccentric shaft 13ab Outer circumference 13b Bottom end 13c Rotating shaft oil supply hole 13d Swivel bearing 13da First end 13db second end 13dc Inner wall (inner diameter surface) 13e Oil groove 14 Discharge port 15 Compression chamber 15A First Compression Chamber 15B Second compression chamber 15a Intake port 17 Rotation restraint member 18 Sub-bearing 20 Electric mechanism section 21 Stator 22 Rotor 30 Main bearing 31 Bearing section 32 Boss housing 33 Sealing material 51 First oil inlet 52 First oil outlet hole 53 First head plate oil passage 61 Second oil inlet 62 Second oil outlet hole 63 Second end plate oil passage 100 Scroll Compressor

Claims

1. A compression mechanism unit that compresses a refrigerant, the compression mechanism unit having a fixed scroll, a rotating scroll, and a rotating shaft having an eccentric shaft and driving the rotating scroll to rotate; an electric mechanism that drives the compression mechanism; A scroll compressor including a sealed container in which the compression mechanism and the electric mechanism are housed, The fixed scroll has a disk-shaped fixed scroll end plate and a fixed spiral wrap provided upright on the fixed scroll end plate, The orbiting scroll includes a disk-shaped orbiting scroll end plate, an orbiting spiral wrap provided on one surface of the orbiting scroll end plate, a cylindrical boss portion disposed on the other surface of the orbiting scroll end plate, and an orbiting bearing fitted into the boss portion and receiving the eccentric shaft, the fixed spiral wrap and the orbiting spiral wrap are intermeshed with each other to form a plurality of compression chambers between the fixed spiral wrap and the orbiting spiral wrap, The orbiting scroll is configured to be pressed against the fixed scroll by a back pressure from the other surface side of the orbiting scroll end plate, The orbiting bearing has a first end disposed on the side of the orbiting scroll end plate, a second end disposed on the opposite side of the first end and into which the eccentric shaft is inserted, and a taper starting point formed between the first end and the second end, The scroll compressor comprises: The inner wall of the slewing bearing has a cylindrical shape from the first end to the taper start point, The first taper shape has a diameter that increases from the taper start point toward the second end. Scroll compressor.

2. The first tapered shape is composed of a straight line, a continuous curve, or a combination thereof.

2. The scroll compressor according to claim 1.

3. The first tapered shape, in a cross-sectional view taken along a plane including an axis of the slewing bearing, an angle θ between the surface of the first tapered shape and the axis is greater than an angle at which the rotation shaft can be tilted; and The present invention is configured to satisfy the following relational expression when the distance between the first end of the slewing bearing and the taper starting point of the first tapered shape is L, the diameter of the eccentric shaft is d, and the diameter of the inner wall of the slewing bearing is D: The scroll compressor according to claim 1 or 2. [0010]

4. The scroll compressor has a main bearing and an auxiliary bearing that support the rotating shaft, The angle at which the rotation shaft can be tilted is determined by a clearance between the main bearing and the rotation shaft and between the auxiliary bearing and the rotation shaft. The scroll compressor according to claim 3.

5. The plurality of compression chambers include a first compression chamber arranged on an outer wall side of the orbiting spiral wrap and a second compression chamber arranged on an inner wall side of the orbiting spiral wrap, The suction volume of the first compression chamber is greater than the suction volume of the second compression chamber. The scroll compressor according to any one of claims 1 to 4.

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