rotary compressor

Abstract

To provide a rotary compressor that ensures sufficient compressor capacity and resistance to high-pressure loads on the medium to be compressed. [Solution] In a rotary compressor (100) housed in a sealed container (C) and having a compression section (30) for compressing a medium to be compressed and a drive section (40) for driving the compression section (34), the sealed container (C) comprises a hollow first shell (10) having an opening that is open on at least one axial side, and a second shell (22) that closes the opening, wherein the diameter of the first shell (10) on one axial side that houses at least a part of the compression section (30) is larger than the diameter of the other axial side that houses at least a part of the drive section (40), and the axial side portion of the first shell (22) that houses at least a part of the compression section (30) is covered by the second shell (22) from the radially outside, and the first shell (10) and the second shell (22) are in contact with each other with a radial overlap to form a cover section (50).

Description

Technical Field

[0001] The present disclosure relates to a rotary compressor.

Background Art

[0002] Conventionally, as a rotary compressor that increases the compressor capacity without increasing the overall size of the apparatus, in an automotive scroll compressor that houses a compression mechanism portion composed of a fixed scroll and a swing scroll and an electric motor portion in a main shell, a configuration is disclosed in which the outer diameter of the main shell of the portion surrounding the compression mechanism portion is formed larger than the outer diameter of the portion surrounding the electric motor portion (see, for example, Patent Document 1).

Prior Art Documents

Patent Documents

[0003]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0004] In the above-described automotive scroll compressor as a conventional rotary compressor, in the main shell, the outer diameter of the portion surrounding the compression mechanism portion is enlarged compared to the outer diameter of the portion housing the electric motor portion. Therefore, the plate material of the main shell of the portion surrounding the compression mechanism portion stretches, and the wall thickness becomes thinner than the plate material before processing, resulting in a problem of insufficient pressure resistance against the high-pressure load from the compression mechanism portion. In addition, when the diameter of the compression mechanism portion is enlarged, the roundness of its inner diameter may deteriorate. Therefore, when processing is performed on the inner wall of the main shell to ensure roundness, the wall thickness of the main shell becomes even thinner, which also causes a problem of insufficient pressure resistance.

[0005] This disclosure provides technology to solve the above-mentioned problems, and aims to provide a rotary compressor that secures compressor capacity without increasing the overall size of the device, and ensures resistance of the compressed medium to high-pressure loads. [Means for solving the problem]

[0006] The rotary compressor of this disclosure is A rotary compressor having a compression unit housed in a sealed container and which compresses a medium to be compressed by the rotation of a main shaft along the axial direction, and a drive unit which rotates the main shaft to drive the compression unit, The sealed container comprises a hollow first shell having an opening on at least one axial side along the main axis, and a second shell that closes the opening. The first shell is configured such that the diameter on one axial side that accommodates at least a portion of the compression section is larger than the diameter on the other axial side that accommodates at least a portion of the drive section. A cover portion is formed in which the first shell, which houses at least a part of the compression section, is covered by the second shell from the radially outward side on one axial side, and the first shell and the second shell are in contact with each other in the radial direction with an overlap. It is. [Effects of the Invention]

[0007] According to the rotary compressor of this disclosure, a rotary compressor can be obtained that secures compressor capacity without increasing the overall size of the apparatus, and that ensures resistance of the medium to be compressed to high-pressure loads. [Brief explanation of the drawing]

[0008] [Figure 1] This is a cross-sectional view showing the configuration of a scroll compressor according to Embodiment 1. [Figure 2] This is an enlarged view of the main part of the scroll compressor according to Embodiment 1. [Figure 3] This is an enlarged view of the main part of the scroll compressor according to Embodiment 1. [Figure 4]This is an enlarged view of the main part of the scroll compressor according to Embodiment 1. [Figure 5] This is a cross-sectional view showing another configuration of the scroll compressor according to Embodiment 1. [Figure 6] This is an enlarged view of the main components of another part of the scroll compressor according to Embodiment 1. [Modes for carrying out the invention]

[0009] Embodiment 1. The scroll compressor 100 in this embodiment 1 will be described below with reference to the figures. Figure 1 is a cross-sectional view showing the configuration of the scroll compressor 100 according to Embodiment 1. In the scroll compressor 100 shown in Figure 1, the direction along the main shaft 43 extending vertically on the plane of the paper is defined as the axial direction Y, and the direction on the plane perpendicular to this axial direction Y is defined as the radial direction X. Furthermore, "Y1," which represents one side of the axial direction, indicates the upper side of the axial direction Y on the plane of the paper, and "Y2," which represents the other side of the axial direction Y, indicates the lower side of the axial direction Y on the plane of the paper. Furthermore, "X2" indicates the outside of the radial direction X, and "X1" indicates the inside of the radial direction X. Furthermore, each drawing is schematic, and there may be differences in dimensional relationships and proportions between drawings.

[0010] The scroll compressor 100, shown in Figure 1 as a rotary compressor, compresses the refrigerant, which is the medium to be compressed, drawn in from outside the pressure vessel C, which is a sealed container, and discharges it outside the pressure vessel C. The scroll compressor 100 houses a compression mechanism 30, which compresses the refrigerant, at the upper axial side Y1 within the pressure vessel C, and an electric motor 40, which drives the compression mechanism 30, at the lower axial side Y2.

[0011] The pressure vessel C includes a middle shell 10 as a hollow cylindrical first shell with openings on both sides in the axial direction Y, an upper shell 22 as a second shell for closing the opening on the upper side Y1 in the axial direction of the middle shell 10, and a lower shell 23 as a third shell for closing the opening on the lower side Y2 in the axial direction.

[0012] The middle shell 10 is configured to have a first cylindrical portion 11 for accommodating the compression mechanism portion 30 on the upper side Y1 in the axial direction and a second cylindrical portion 12 for accommodating the electric motor 40 on the lower side Y2 in the axial direction. Here, it is not necessary for the middle shell 10 to accommodate the entire device of the compression mechanism portion 30 inside at the upper side Y1 in the axial direction. As shown in FIG. 1, it is sufficient to accommodate at least a part of the compression mechanism portion 30. Also, the middle shell 10 is not limited to accommodating the entire device of the electric motor 40 at the lower side Y2 in the axial direction, and it is sufficient to accommodate at least a part of the electric motor 40. Between the first cylindrical portion 11 and the second cylindrical portion 12, a diameter-expanded portion 13 is provided to gradually increase the inner diameter of the second cylindrical portion 12 as it goes toward the upper side Y1 in the axial direction. Thereby, the inner diameter of the first cylindrical portion 11 for accommodating the compression mechanism portion 30 is configured to be larger than the inner diameter of the second cylindrical portion 12 for accommodating the electric motor 40.

[0013] An intake pipe 14 for sucking refrigerant from the outside is attached to the side surface of the first cylindrical portion of the middle shell 10. Note that the intake pipe 14 may be attached to the second cylindrical portion 12 side. The upper shell 22 is provided with a discharge pipe 21 for discharging the compressed refrigerant to the outside. In FIG. 1, the middle shell 10 with openings on both sides in the axial direction Y is shown, but it is not limited thereto. The middle shell 10 may have a configuration with only the upper side Y1 in the axial direction being open, and in this case, the middle shell 10 and the lower shell 23 are integrated.

[0014] The compression mechanism portion 30 and the electric motor 40 are connected via a main shaft 43 extending in the axial direction Y and rotatably supported inside the pressure vessel C. The compression mechanism section 30 includes a fixed scroll 32 and a swing scroll 33, each having a spiral projection to form a compression chamber 3. Further, the compression mechanism section 30 includes a frame 34 that supports the fixed scroll 32 and the swing scroll 33. The swing scroll 33 is fixed to the main shaft 43 and performs a swinging motion with respect to the fixed scroll 32 as the main shaft 43 rotates. Also, a discharge valve 31 is provided at the discharge portion of the compression chamber 3.

[0015] The electric motor 40 includes a rotor 41 and a stator 42, and transmits the generated rotational force to the compression mechanism section 30 via the main shaft 43 to drive the compression mechanism section 30.

[0016] The operation of the scroll compressor 100 configured as described above will be described. As the electric motor 40 rotates about the axial direction Y, the low-temperature and low-pressure refrigerant before compression is inhaled into the scroll compressor 100 through the suction pipe 14. The inhaled refrigerant flows into the compression chamber 3 through the frame 34.

[0017] Also, along with this main shaft 43, the swing scroll 33 performs a swinging motion with respect to the fixed scroll 32. As a result, the volume between the spiral projections of the fixed scroll 32 and the swing scroll 33 changes, and the refrigerant is compressed to a high temperature and high pressure in the compression chamber 3. When the compressed refrigerant reaches or exceeds the set pressure, the discharge valve 31 opens, and the compressed refrigerant is discharged into the muffler 35. The compressed refrigerant passes through the muffler 35 and is then discharged to the outside of the scroll compressor 100 through the discharge pipe 21.

[0018] Next, the detailed configuration of the main part of the scroll compressor 100 of the present embodiment will be described. FIG. 2 is an enlarged view of the portion of the scroll compressor 100 shown in FIG. 1 surrounded by the dotted line S1. FIG. 3 is an enlarged view of the portion of the scroll compressor shown in FIG. 2 surrounded by the dotted line S2. FIG. 4 is an enlarged view of the portion of the scroll compressor shown in FIG. 3 surrounded by the dotted line S3. Note that while Figures 3 and 4 only show the upper left portion of Figure 2, the areas described in Figures 3 and 4 are formed symmetrically in the upper right portion of the paper, as shown in Figures 1 and 2.

[0019] As shown within the dotted lines S2 and S3 in Figures 2 and 3, the cylindrical outer periphery of the upper shell 22 covers the outer periphery surface 11G1 of the first cylindrical portion 11 of the middle shell 10 from the radially outward X2, thereby closing the axial upper Y1 opening of the middle shell 10.

[0020] First, the detailed configuration of the first cylindrical portion 11 that constitutes the middle shell 10 will be described. As shown in Figure 4, the first cylindrical portion 11 has a stepped portion 11FF that serves as a support, formed by recessing the second inner circumferential surface 11N2, which is the inner wall on its axial upper side Y1, radially outward X2 than the first inner circumferential surface 11N1, which is the inner wall on its axial lower side Y2. Thus, the first cylindrical portion 11 has a thin-walled portion 11T formed on its upper axial side Y1, where the thickness in the radial direction X is reduced and the length in the axial direction Y is L1. Therefore, the first cylindrical portion 11 is configured such that the diameter H2 of the second inner circumferential surface 11N2 on its axial upper side Y1 is larger than the diameter H1 of the first inner circumferential surface 11N1 on its axial lower side Y2.

[0021] Furthermore, the diameter H3 of the outer circumferential surface 11G1 of the first cylindrical portion 11 is formed to be larger than the diameter H2 of the second inner circumferential surface 11N2 of the first cylindrical portion 11. Therefore, the wall thickness T1 of the thin-walled portion 11T of the first cylindrical portion 11 in the radial direction X is T1 = (H3 - H2) / 2. Also, the wall thickness T2 of the portion of the first cylindrical portion 11 other than the thin-walled portion 11T is T2 = (H3 - H1) / 2. From the above, T1 <T2となる。 Thus, the wall thickness T1 of the thin-walled section 11T is the smallest wall thickness in the middle shell 10, even when compared to the wall thicknesses of the second cylindrical section 12 and the enlarged diameter section 13.

[0022] Next, we will describe the detailed configuration of the upper shell 22. As shown in Figure 4, the upper shell 22 has a stepped portion 22NN formed by recessing the first inner circumferential surface 22N1, which is the inner wall on its axial lower side Y2, radially outward X2 than the second inner circumferential surface 22N2, which is the inner wall on its axial upper side Y1. Therefore, the upper shell 22 is configured such that the diameter H3 of the first inner circumferential surface 22N1 on its axially lower side Y2 is larger than the diameter H4 of the second inner circumferential surface 22N2 on its axially upper side Y1.

[0023] The upper shell 22 is fixed to the outer surface 11G1 of the first cylindrical portion 11 by shrink fitting or press fitting, with a set interference fit, at its first inner surface 22N1. After the interference fit, the stepped surface 22N0, which is the axial lower end Y2 of the stepped portion 22NN, is in contact with the upper end surface 11F2 of the first cylindrical portion 11, and its second inner surface 22N2 is in contact with the outer surface 32G of the fixed scroll 32.

[0024] Thus, in the pressure vessel C, the cylindrical outer periphery of the upper shell 22 forms a covering portion 50 that covers the outer periphery surface 11G1 of the axial upper side Y1 of the first cylindrical portion 11 from the radially outer side X2. That is, the covering portion 50 is the area in the pressure vessel C where the upper shell 22 and the first cylindrical portion 11 overlap radially in the X direction with a set overlap.

[0025] The lower end surface 22F1 of the axially lower Y2 of the outer circumference of the upper shell 22 is fixed to the outer circumference surface 11G1 of the first cylindrical portion 11 by welding, forming a welded joint 99. The welded joint 99 is provided around the entire circumference along the outer circumference surface 11G1 of the first cylindrical portion 11. This maintains airtightness between the inside and outside of the pressure vessel C.

[0026] In this embodiment, the first stepped surface 11F1, which is the end face of the axial upper Y1 of the stepped portion 11FF of the first cylindrical portion 11, is formed along the radial direction X so as to be perpendicular (90°) to the first inner circumferential surface 11N1 and the second inner circumferential surface 11N2 which are aligned along the axial direction Y. However, the invention is not limited to this, and the first stepped surface 11F1 may be formed at an angle close to perpendicular (for example, 70° to 110°) with respect to the first inner surface 11N1 and the second inner surface 11N2.

[0027] Next, the detailed configuration of the frame 34 of the compression mechanism 30 will be described. As shown in Figure 4, the frame 34 has a projection 34P that protrudes radially outward X2 from the outer circumferential surface of the frame 34. This projection 34P is placed on the first stepped surface 11F1 of the stepped portion 11FF of the first cylindrical portion 11. Then, the second outer circumferential surface 34G2 of the radially outer X2 of the protruding portion 34P and the second inner circumferential surface 11N2 of the first cylindrical portion 11 are compressed and fitted together by shrink fitting or press fitting, and are fixed to each other with an overlap in the radial direction X. In this way, the compression mechanism portion 30 is fixed to the first cylindrical portion 11. Note that shrink fitting or press fitting are examples of assembly methods, and other means may be used to achieve a tight fit.

[0028] Here, the projection 34P of the frame 34 is formed axially downward Y2 by a set distance from the end face 34F3 on the axially upward Y1 of the frame 34. A gap K1 is ensured between the third outer circumferential surface 34G3 on the axially upward Y1 of the projection 34P and the second inner circumferential surface 11N2 of the first cylindrical portion 11, so that they do not touch each other. It is even better if the third outer circumferential surface 34G3 and the second inner circumferential surface 11N2 are formed parallel to each other along the axial direction Y.

[0029] Similarly, a gap K2 is maintained between the first outer circumferential surface 34G1 on the axially lower side Y2 of the protrusion 34P and the first inner circumferential surface 11N1 of the first cylindrical portion 11, so that they do not come into contact with each other. Furthermore, it is preferable that the first outer circumferential surface 34G1 and the first inner circumferential surface 11N1 are formed parallel to each other along the axial direction Y. By providing these gaps K1 and K2, the contact area between the first cylindrical portion 11 and the frame 34 is reduced, which can suppress deformation of the first cylindrical portion 11 caused by shrink fitting, press fitting, or other compression fitting of the frame 34.

[0030] Alternatively, a configuration may be made in which there is no gap K1 between the third outer peripheral surface 34G3 on the axial upper side Y1 of the protruding portion 34P and the second inner peripheral surface 11N2 of the first cylindrical portion 11. However, the configuration that secures this gap K1 is more effective in suppressing the deformation of the first cylindrical portion 11, as described above.

[0031] In this embodiment, the upper stepped surface 34F2, which is the end face of the axial upper Y1 of the protruding portion 34P of the frame 34, is formed along the radial X direction so as to be perpendicular (90°) to the third outer peripheral surface 34G3 and the second outer peripheral surface 34G2 which are aligned along the axial Y direction. However, the method is not limited to this, and the upper stepped surface 34F2 may be formed at an angle close to perpendicular (for example, 70° to 110°) with respect to the third outer surface 34G3 and the second outer surface 34G2.

[0032] Similarly, the lower stepped surface 34F1, which is the axially lower end face Y2 of the projection 34P of the frame 34, is formed along the radial X direction so as to be perpendicular (90°) to the first outer peripheral surface 34G1 and the second outer peripheral surface 34G2 along the axial Y direction. However, the method is not limited to this, and the lower stepped surface 34F1 may be formed at an angle close to perpendicular (for example, 70° to 110°) with respect to the first outer peripheral surface 34G1 and the second outer peripheral surface 34G2. In other words, the shape of the protruding portion 34P of the frame 34 and the shape of the stepped portion 11FF of the first cylindrical portion 11 as a support portion are not limited in detail, as long as they are configured to support the frame 34 in the axial direction Y.

[0033] Here, the lower end surface 22F1 of the outer circumference of the upper shell 22 is configured to be located axially lower Y2 than the lower stepped surface 34F1 of the frame 34 and the first stepped surface 11F1 of the first cylindrical portion 11 on which the frame 34 rests. In other words, the stepped portion 11FF is provided as a support portion for the frame 34 within the range of the axial length Y L2 of the covering portion 50 where the upper shell 22 and the first cylindrical portion 11 overlap in the radial direction X. Therefore, the axial length Y L1 of the thin-walled portion 11T of the first cylindrical portion 11 is set to be longer than the axial length Y L2 of the covering portion 50.

[0034] In the compression mechanism 30, the refrigerant is compressed to high temperature and high pressure, thereby applying high pressure to the radially outer side X2 of the compression chamber 3. That is, at the point of contact between the frame 34 constituting the compression mechanism 30 in Figure 4 and the first cylindrical portion 11, pressure is applied to the radially outer side X2.

[0035] The contact area between the frame 34 and the first cylindrical portion 11 has a stepped portion 11FF formed therein, which allows the first cylindrical portion 11 to support the frame 34 in the axial direction Y, and is formed with a thin wall. However, in this embodiment, the radially outer X2 of the thin-walled portion 11T is covered by the upper shell 22, and the first cylindrical portion 11 and the upper shell 22 form a covering portion 50 with a wall thickness T3 that overlaps radially in the direction X. Therefore, even if the wall thickness T1 of the portion of the first cylindrical portion 11 that contacts the frame 34 is thin, the covering portion 50 ensures a sufficient wall thickness T3 that can withstand the pressure from the compression mechanism 30.

[0036] Furthermore, in this embodiment, the cover portion 50 includes a portion in which the first inner circumferential surface 22N1 of the upper shell 22 and the outer circumferential surface 11G1 of the first cylindrical portion 11 are fixed together with an overlap by shrink fitting or press fitting. By being fixed with a clamping allowance, a compressive stress acts from the outer circumferential surface 11G1 of the first cylindrical portion 11 toward the radially inward X1. Therefore, when the scroll compressor 100 operates, the load due to the internal pressure acting radially outward X2 from the compression mechanism 30 can be reduced by this compressive stress applied toward the radially inward X1.

[0037] Thus, even when the diameter of the portion of the middle shell 10 surrounding the compression mechanism 30 is increased compared to the diameter of the portion housing the electric motor 40 in order to secure the compressor capacity, a scroll compressor 100 that can withstand the high-pressure load from the compression mechanism 30 can be obtained.

[0038] Furthermore, if the diameter of the middle shell 10 that houses the compression mechanism 30 is enlarged, the enlargement rate of the enlarged portion becomes large, which may worsen the roundness of the inner diameter. In the scroll compressor 100 of this embodiment, if the roundness of the inner diameter of the first cylindrical portion 11 of the middle shell 10 deteriorates, the cutting allowance of the inner diameter of the first cylindrical portion 11 can be increased in order to secure the width in the radial direction X of the first stepped surface 11F1 on which the lower stepped surface 34F1 of the protruding portion 34P is placed. Therefore, a configuration can be made that can withstand the high-pressure load from the compression mechanism 30 while ensuring the roundness of the middle shell 10. In this case, the thickness T3 of the covering portion 50 may be less than or equal to the thickness T2 of the cylindrical portion.

[0039] Furthermore, the covering portion 50 is not limited to covering the entire axial Y range of the compression mechanism portion 50. As long as the covering portion 50 is configured on at least a part of the portion of the first cylindrical portion 11 that houses the compression mechanism portion 50, the load due to internal pressure acting radially outward X2 from the compression mechanism portion 30 can be reduced. Furthermore, while the scroll compressor was shown above as an example of a rotary compressor, it is not limited to this; for example, a rotary compressor could also be used. Furthermore, although the configuration shown involves the first cylindrical portion 11 of the middle shell 10 supporting the compression mechanism 30 in the axial direction Y, the invention is not limited to this configuration. The same effects can be achieved even if the inner wall of the first cylindrical portion 11 and the outer circumference of the compression mechanism 30 are merely in contact.

[0040] The following describes a different scroll compressor 100A from the one described above. Figure 5 is a cross-sectional view showing the configuration of a scroll compressor 100A with a different configuration than that shown in Figure 1. Figure 6 is an enlarged view of the portion of the scroll compressor 100A shown in Figure 5 enclosed by the dotted line S4.

[0041] In this scroll compressor 100A, the axial lower end Y2 of the first cylindrical section 11 is positioned above the upper end of the enlarged diameter section 13, that is, above the boundary line J between the first cylindrical section 11 and the enlarged diameter section 13 in the axial direction Y. Therefore, compared to the scroll compressor 100 shown in Figure 1, the axial lower Y2 end of the first cylindrical section 11 is located further axially lower Y2.

[0042] At boundary line J, since there is a corner R, when the scroll compressor 100A is operated, internal pressure may concentrate at the corner R, and the first cylindrical portion 11 and the enlarged diameter portion 13 may deform in the radially outward direction X2. By forming the upper shell 22 as described above, the lower end surface 22F1 of the upper shell 22 approaches the enlarged diameter portion 13, thereby suppressing radial outward deformation X2 of the first cylindrical portion 11 and the enlarged diameter portion 13.

[0043] With this configuration, the welded joint 99, which fixes the lower end surface 22F1 of the upper shell 22 and the outer circumferential surface 11G1 of the first cylindrical portion 11 by welding, contracts, and the outer circumferential surface 11G1 of the first cylindrical portion 11 receives a force radially inward X1. As a result, deformation radially outward X2 of the first cylindrical portion 11 and the enlarged diameter portion 13 can be suppressed. Furthermore, the position of the welded portion 99 can be moved away from the second outer surface 34G2 of the frame 34, which is used to fix the frame 34 and the first cylindrical portion 11 by shrink fitting or press fitting. This reduces the effect of thermal shrinkage due to welding on the second outer surface 34G2. As a result, deformation of the frame 34 can be suppressed, and the compression mechanism 30 of the scroll compressor 100A can be manufactured with high precision.

[0044] The rotary compressor of this embodiment, configured as described above, A rotary compressor having a compression unit housed in a sealed container and which compresses a medium to be compressed by the rotation of a main shaft along the axial direction, and a drive unit which rotates the main shaft to drive the compression unit, The sealed container comprises a hollow first shell having an opening on at least one axial side along the main axis, and a second shell that closes the opening. The first shell is configured such that the diameter on one axial side that accommodates at least a portion of the compression section is larger than the diameter on the other axial side that accommodates at least a portion of the drive section. A cover portion is formed in which the first shell, which houses at least a part of the compression section, is covered by the second shell from the radially outward side on one axial side, and the first shell and the second shell are in contact with each other in the radial direction with an overlap. It is.

[0045] In this way, a covering portion is formed in which at least a part of the middle shell, which is the first shell, that houses the compression section is covered from the radially outer side by the upper shell, which is the second shell. Furthermore, in this covering portion, the middle shell and the upper shell are in contact with each other in the radial direction with an overlap, thereby creating a configuration that can withstand high pressure loads from the compression section.

[0046] Furthermore, in the rotary compressor of this embodiment configured as described above, The support portion that supports the compression portion in the axial direction is formed on the inner wall of the first shell radially inward within the axial range of the cover portion. It is.

[0047] Thus, even in a rotary compressor where the middle shell supports the compression section, by positioning the support section that supports the compression section within the axial range where the cover exists, it is possible to ensure pressure resistance at the support section to which the high-pressure load from the compression section is applied.

[0048] Furthermore, in the rotary compressor of this embodiment configured as described above, The support portion is a stepped portion formed by recessing at least a part of the inner wall on one axial side of the first shell radially outward compared to the inner wall on the other axial side. The compression portion has a projection that protrudes radially outward from the outer circumferential surface of the compression portion. The protrusion is placed on one axial side surface of the stepped portion, and the radially outer end of the protrusion and the inner wall of the first shell are in contact with each other with a radial overlap. It is.

[0049] Thus, by providing a stepped portion in the middle shell that supports the compression mechanism in the axial direction, and by further configuring the protruding portion of the compression mechanism and the first shell to have a interference fit, for example, by shrink fitting or press fitting, a compressive stress is further applied from the first cylindrical portion 11 toward the radially inward X1, making it possible to create a configuration that can withstand high-pressure loads from the compression section.

[0050] Furthermore, in the rotary compressor of this embodiment configured as described above, The axial length of the covering portion is configured to be longer than the axial length of the thin-walled portion that constitutes the stepped portion, which is formed by recessing the inner wall on one axial side of the first shell radially outward. It is.

[0051] In this way, by positioning the thin-walled section of the middle shell, which has a thinner wall thickness, within the area where the covering is present, resistance to high-pressure loads from the compression section can be improved.

[0052] Furthermore, in the rotary compressor of this embodiment configured as described above, On the radially outer surface of the compression portion, the portion excluding the protrusion is configured to have a gap between it and the inner wall of the first shell. It is.

[0053] By reducing the contact area between the middle shell and the compression mechanism in this way, deformation of the middle shell caused by shrink fitting, press fitting, and other compression fitting processes can be suppressed, thereby improving reliability.

[0054] The rotary compressor of this embodiment, configured as described above, The axial end of the second shell, which constitutes the cover, is positioned at the upper end of the enlarged diameter portion, which encloses at least a portion of the compression portion of the first shell, and encloses at least a portion of the compression portion of the first shell, and encloses at least a portion of the axial diameter of the other axial diameter portion, which encloses at least a portion of the drive portion. It is.

[0055] This makes it possible to suppress radial outward deformation of the first cylindrical section and the enlarged diameter section, enabling the high-precision manufacturing of the compression mechanism of the scroll compressor.

[0056] While this disclosure describes exemplary embodiments, the various features, aspects, and functions described in the embodiments are not limited to the application of any particular embodiment, but can be applied individually or in various combinations to the embodiments. Accordingly, countless variations not illustrated are conceivable within the scope of the art disclosed in this specification. These include, for example, modifications, additions, or omissions of at least one component.

[0057] The various aspects of this disclosure are summarized below as an appendix.

[0058] (Note 1) A rotary compressor having a compression unit housed in a sealed container and which compresses a medium to be compressed by the rotation of a main shaft along the axial direction, and a drive unit which rotates the main shaft to drive the compression unit, The sealed container comprises a hollow first shell having an opening on at least one axial side along the main axis, and a second shell that closes the opening. The first shell is configured such that the diameter on one axial side that accommodates at least a portion of the compression section is larger than the diameter on the other axial side that accommodates at least a portion of the drive section. A cover portion is formed in which the first shell, which houses at least a part of the compression section, is covered by the second shell from the radially outward side on one axial side, and the first shell and the second shell are in contact with each other in the radial direction with an overlap. Rotary compressor. (Note 2) The support portion that supports the compression portion in the axial direction is formed on the inner wall of the first shell radially inward within the axial range of the cover portion. The rotary compressor described in Appendix 1. (Note 3) The support portion is a stepped portion formed by recessing at least a part of the inner wall on one axial side of the first shell radially outward compared to the inner wall on the other axial side. The compression portion has a projection that protrudes radially outward from the outer circumferential surface of the compression portion. The protrusion is placed on one axial side surface of the stepped portion, and the radially outer end of the protrusion and the inner wall of the first shell are in contact with each other with a radial overlap. The rotary compressor described in Appendix 2. (Note 4) On the radially outer surface of the compression portion, the portion excluding the protrusion is configured to have a gap between it and the inner wall of the first shell. The rotary compressor described in Appendix 3. (Note 5) The axial length of the covering portion is configured to be longer than the axial length of the thin-walled portion that constitutes the stepped portion, which is formed by recessing the inner wall on one axial side of the first shell radially outward. A rotary compressor as described in Appendix 3 or Appendix 4. (Note 6) The axial end of the second shell, which constitutes the cover, is positioned at the upper end of the enlarged diameter portion, which encloses at least a portion of the compression portion of the first shell, and encloses at least a portion of the compression portion of the first shell, and encloses at least a portion of the axial diameter of the other axial diameter portion, which encloses at least a portion of the drive portion. A rotary compressor as described in any one of the appendices 1 through 5. [Explanation of Symbols]

[0059] C Pressure vessel (sealed container), 10 Middle shell (first shell), 11T Thin-walled section, 11FF Step section (support section), 13 Enlarged diameter section, 22 Upper shell (second shell), 30 Compression mechanism (compression section), 34P Protruding section, 40 Electric motor (drive section), 43 Main shaft, 50 Covering section, K1, K2 Gap, 100, 100A scroll compressor (rotary compressor).

Claims

1. A rotary compressor having a compression unit housed in a sealed container and which compresses a medium to be compressed by the rotation of a main shaft along the axial direction, and a drive unit which rotates the main shaft to drive the compression unit, The sealed container comprises a hollow first shell having an opening on at least one axial side along the main axis, and a second shell that closes the opening. The first shell is configured such that the diameter on one axial side that accommodates at least a portion of the compression section is larger than the diameter on the other axial side that accommodates at least a portion of the drive section. A cover portion is formed in which the first shell, which houses at least a part of the compression section, is covered from the radially outer side by the second shell, and the first shell and the second shell are in contact with each other with an overlap in the radial direction. Rotary compressor.

2. The support portion that supports the compression portion in the axial direction is formed on the inner wall of the first shell radially inward within the axial range of the cover portion. The rotary compressor according to claim 1.

3. The support portion is a stepped portion formed by recessing at least a part of the inner wall on one axial side of the first shell radially outward compared to the inner wall on the other axial side. The compression portion has a projection that protrudes radially outward from the outer circumferential surface of the compression portion, The protrusion is placed on one axial side surface of the stepped portion, and the radially outer end of the protrusion and the inner wall of the first shell are in contact with each other with a radial overlap. The rotary compressor according to claim 2.

4. On the radially outer surface of the compression portion, the portion excluding the protruding portion is configured to have a gap between it and the inner wall of the first shell. The rotary compressor according to claim 3.

5. The axial length of the covering portion is configured to be longer than the axial length of the thin-walled portion that constitutes the stepped portion, which is formed by recessing the inner wall on one axial side of the first shell radially outward. The rotary compressor according to claim 4.

6. The axial end of the second shell, which constitutes the cover, is positioned at the upper end of the enlarged diameter portion, which encloses at least a portion of the compression portion of the first shell, and encloses one axial diameter portion larger than the axial diameter of the other axial diameter portion that encloses at least a portion of the drive portion. A rotary compressor according to any one of claims 1 to 5.

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