Compressors and air conditioners

Abstract

Provided is a compressor etc. having good performance and high reliability. This compressor (100) comprises a cylindrical oil ring (15) provided between a compressing mechanism part (2) and an electric motor (6). A balance weight (8) has an annular section (8a) that is fixed to a crank shaft (3) while the crank shaft (3) is inserted therethrough, an arcuate section (8b) that extends upward from the annular section (8a), and at least one protruding section (8c) that protrudes downward from the annular section (8a). The upstream end of a discharge pipe (P2) is positioned on the radially inner side of the oil ring (15), and the lower end of the oil ring (15) surrounds a winding section (61b) of a stator (61). The protruding section (8c) protrudes further downward than the height position on the inner circumferential edge of the lower surface of the annular section (8a).

Description

[Technical Field]

[0001] The present invention relates to a compressor and an air conditioner. [Background technology]

[0002] In the fields of refrigeration and air conditioning, HFC refrigerants, which have an ozone depletion potential (ODP) of approximately zero, are mainly used. However, because these HFC refrigerants have a relatively high global warming potential (GWP), there is a demand for a switch to HFO refrigerants, which have a low global warming potential. However, it has been pointed out that HFO refrigerants, which are expected to be new refrigerants, are prone to a self-decomposition reaction known as a disproportionation reaction. A technology that takes this into consideration is known, for example, as described in Patent Document 1.

[0003] That is, Patent Document 1 describes that when an HFO refrigerant is used, the flow velocity of the refrigerant flowing around the location where ignition energy is generated inside the compressor should be set to 1 m / s or more. [Prior art documents] [Patent documents]

[0004] [Patent Document 1] Japanese Patent Publication No. 2022-13931 Summary of the Invention [Problem to be solved by the invention]

[0005] The technology described in Patent Document 1 increases the flow velocity of the refrigerant not only around the location where ignition energy is generated but also throughout the compressor. As a result, the lubricating oil sealed in the compressor is more likely to leak out of the compressor along with the refrigerant, leaving room for improvement in terms of performance and reliability.

[0006] Therefore, an object of the present invention is to provide a compressor or the like with high performance and reliability. [Means for solving the problem]

[0007] In order to solve the above-mentioned problems, a compressor according to the present invention includes: a sealed container; an electric motor installed inside the sealed container and having a stator and a rotor; a drive shaft rotating integrally with the rotor; a compression mechanism that compresses a refrigerant as the drive shaft rotates; a discharge pipe that guides the refrigerant compressed by the compression mechanism to the outside of the sealed container; and a balance weight installed on the drive shaft. The compressor also includes a cylindrical first partition wall installed between the compression mechanism and the electric motor, the balance weight having an annular portion fixed to the drive shaft with the drive shaft inserted therethrough, an arc portion extending upward from the annular portion, and at least one convex portion protruding downward from the annular portion, the upstream end of the discharge pipe being located radially inside the first partition wall, the lower end of the first partition wall surrounding a winding portion of the stator, and the convex portion protruding downward below a height position of an inner circumferential edge of a lower surface of the annular portion. [Effects of the Invention]

[0008] According to the present invention, a compressor or the like with high performance and reliability can be provided. [Brief explanation of the drawings]

[0009] [Figure 1] 1 is a vertical cross-sectional view of a compressor according to a first embodiment. [Figure 2] 2 is a cross-sectional view of the compressor according to the first embodiment taken along line II-II in FIG. 1. FIG. [Figure 3A] FIG. 2 is a perspective view of the balance weight of the compressor according to the first embodiment, viewed obliquely from above. [Figure 3B] 2 is a perspective view of the balance weight of the compressor according to the first embodiment, viewed from diagonally below. FIG. [Figure 4] FIG. 2 is a plan view of a balance weight provided in the compressor according to the first embodiment. [Figure 5]FIG. 2 is a perspective view of an oil ring included in the compressor according to the first embodiment. [Figure 6A] FIG. 10 is a perspective view of an oil ring provided in a compressor according to a second embodiment, viewed obliquely from above. [Figure 6B] FIG. 10 is a perspective view of an oil ring provided in a compressor according to a second embodiment, viewed from diagonally below. [Figure 7] FIG. 10 is a perspective view of a compressor according to a second embodiment with a sealed container and the like removed. [Figure 8] FIG. 10 is a cross-sectional view of a compressor according to a second embodiment, taken along a plane including a recess. [Figure 9] FIG. 10 is a vertical cross-sectional view of a compressor according to a third embodiment. [Figure 10] FIG. 11 is a perspective view of a second oil ring included in the compressor according to the third embodiment. [Figure 11] FIG. 10 is a configuration diagram including a refrigerant circuit of an air conditioner according to a fourth embodiment. [Figure 12] FIG. 10 is a perspective view of a balance weight of a compressor according to a first modified example, viewed from diagonally below. [Figure 13] FIG. 10 is a perspective view of a balance weight of a compressor according to a second modified example, viewed from diagonally below. [Figure 14] FIG. 11 is a perspective view of a balance weight of a compressor according to a third modified example, viewed from obliquely below. DETAILED DESCRIPTION OF THE INVENTION

[0010] First Embodiment <Compressor configuration> FIG. 1 is a vertical cross-sectional view of a compressor 100 according to the first embodiment. The compressor 100 shown in Fig. 1 is a scroll compressor that compresses a gaseous refrigerant. The refrigerant used in the compressor 100 may be an HFO refrigerant, or a specified refrigerant other than an HFO refrigerant. As the HFO refrigerant (the refrigerant number is in parentheses), for example, one containing at least one of monofluoroethylene (R1141), trans-1,2-difluoroethylene (R1132(e)), cis-1,2-difluoroethylene (R1132(Z)), 1,1-difluoroethylene (R1132a), trifluoroethylene (R1123), and tetrafluoroethylene (R1114) is used.

[0011] 1, the compressor 100 includes a sealed container 1, a compression mechanism 2, a crankshaft 3 (drive shaft), a main bearing 4, a slewing bearing 5, an electric motor 6, and an Oldham ring 7. In addition to the components described above, the compressor 100 also includes balance weights 8 and 9, a sub-frame 10 (lower frame), an auxiliary bearing 11, an oil supply pump 12, a thrust bearing 13, legs 14, and an oil ring 15 (first partition wall).

[0012] The sealed container 1 is a container that houses the compression mechanism 2, crankshaft 3, electric motor 6, oil ring 15, etc., and is substantially sealed. The sealed container 1 includes a cylindrical chamber 1a, a lid chamber 1b that closes the upper opening of the cylindrical chamber 1a, and a bottom chamber 1c that closes the lower opening of the cylindrical chamber 1a. A suction pipe P1 is inserted into and fixed to the lid chamber 1b of the sealed container 1. The suction pipe P1 is a tube that guides refrigerant to the suction chamber J1 of the compression mechanism 2.

[0013] A discharge pipe P2 is inserted and fixed into the cylindrical chamber 1a of the sealed container 1. The discharge pipe P2 is a pipe that guides the refrigerant compressed by the compression mechanism 2 to the outside of the compressor 100. Lubricating oil is sealed in the sealed container 1 to improve lubrication in the compressor 100, and is stored in an oil reservoir R1 at the bottom of the sealed container 1.

[0014] The compression mechanism 2 is a mechanism that compresses the refrigerant in accordance with the rotation of the crankshaft 3 (drive shaft). The compression mechanism 2 includes a fixed scroll 21, an orbiting scroll 22, and a frame 23, and is disposed in the upper space within the sealed container 1.

[0015] The fixed scroll 21 is a member that forms the compression chamber C1 together with the orbiting scroll 22. The fixed scroll 21 is installed on the upper side of the frame 23 and fixed to the frame 23 with bolts (not shown). As shown in FIG. 1, the fixed scroll 21 includes a base plate 21a and a fixed wrap 21b.

[0016] The base plate 21a is a thick member having a circular shape in a plan view. The base plate 21a is provided with a suction chamber J1 to which a refrigerant is introduced via a suction pipe P1. The fixed wrap 21b is spiral-shaped (see also FIG. 2) and extends downward from the base plate 21a. The lower surface of the portion of the base plate 21a outside the fixed wrap 21b is substantially flush with the tooth tips of the fixed wrap 21b.

[0017] The orbiting scroll 22 is a member that forms a compression chamber C1 between itself and the fixed scroll 21 by its orbit (movement). The orbiting scroll 22 includes a disk-shaped end plate 22a, a spiral orbiting wrap 22b standing on the end plate 22a, and a boss portion 22c that is fitted onto the eccentric portion 3b of the crankshaft 3. As shown in FIG. 1, the orbiting wrap 22b extends upward from the end plate 22a. On the other hand, the boss portion 22c extends downward from the end plate 22a.

[0018] The space between the rear side of the end plate 22a of the orbiting scroll 22 and the frame 23 functions as a back pressure chamber B1. A predetermined back pressure acts in the back pressure chamber B1 to press the orbiting scroll 22 against the fixed scroll 21.

[0019] FIG. 2 is a cross-sectional view of the compressor 100 taken along line II-II in FIG. As shown in Fig. 2, the spiral-shaped fixed wrap 21b of the fixed scroll 21 and the spiral-shaped orbiting wrap 22b of the orbiting scroll 22 mesh together to form a compression chamber C1 between the fixed wrap 21b and the orbiting wrap 22b. The compression chamber C1 is a space for compressing a gaseous refrigerant, and is formed on the outer line side and the inner line side of the orbiting wrap 22b. A discharge port J2 is provided near the center of the base plate 21a of the fixed scroll 21 (see Fig. 1) to guide the refrigerant compressed in the compression chamber C1 to an upper space in the sealed container 1.

[0020] As shown in Fig. 2, the compression mechanism 2 has a groove M1 that connects the upper side (one side) and the lower side (the other side) of the compression mechanism 2 in the axial direction of the crankshaft 3 (drive shaft). In the example of Fig. 2, the outer peripheral wall of the fixed scroll 21 is recessed radially inward to form two grooves M1 arranged in the upper and lower directions. The refrigerant compressed in the compression mechanism 2 is guided to the lower side of the compression mechanism 2 through a gap between the inner peripheral surface of the sealed container 1 and the grooves M1.

[0021] 1 is a member for supporting the fixed scroll 21 and for fixing the main bearing 4, and has a generally rotationally symmetrical shape. The frame 23 is fixed to the sealed container 1 and also fixed to the lower side of the fixed scroll 21. The frame 23 is provided with a hole (reference number not shown) through which the crankshaft 3 is inserted.

[0022] The crankshaft 3 (drive shaft) is a shaft that rotates integrally with the rotor 62 of the electric motor 6 and extends in the vertical direction. As shown in Fig. 1, the crankshaft 3 includes a main shaft portion 3a and an eccentric portion 3b that extends above the main shaft portion 3a.

[0023] The main shaft portion 3a is fixed coaxially to the rotor 62 of the electric motor 6 and rotates integrally with the rotor 62. The eccentric portion 3b is a shaft that rotates eccentrically with respect to the main shaft portion 3a, and as described above, is fitted into the boss portion 22c of the orbiting scroll 22. The eccentric rotation of the eccentric portion 3b causes the orbiting scroll 22 to orbit. An oil supply passage 3c through which lubricating oil flows is provided inside the crankshaft 3. The lubricating oil that flows through the oil supply passage 3c is guided to the compression mechanism portion 2, the main bearing 4, the orbiting bearing 5, the sub-bearing 11, etc.

[0024] The main bearing 4 rotatably supports the upper part of the main shaft portion 3a relative to the frame 23, and is installed on the peripheral wall surface of a hole (reference number not shown) in the frame 23. The orbiting bearing 5 rotatably supports the eccentric portion 3b relative to the boss portion 22c of the orbiting scroll 22, and is installed on the inner peripheral surface of the boss portion 22c.

[0025] The electric motor 6 is a driving source that rotates the crankshaft 3 and is installed inside the sealed container 1. The electric motor 6 includes a stator 61 and a rotor 62, and is installed between the frame 23 and the subframe 10. The stator 61 is fixed to the inner circumferential surface of the cylindrical chamber 1a by press-fitting or the like. The rotor 62 is rotatably disposed radially inside the stator 61. The stator 61 includes a core back 61a formed by laminating electromagnetic steel sheets, and a winding portion 61b wound in a predetermined manner around the core back 61a. When a predetermined current is applied to the winding portion 61b via a power supply terminal E1 (see FIG. 2), magnetic attractive and repulsive forces are generated, causing the rotor 62 to rotate.

[0026] The Oldham ring 7 is a ring-shaped member that receives the eccentric rotation of the eccentric portion 3b and orbits the orbiting scroll 22 without rotating on its axis. The Oldham ring 7 is provided between the orbiting scroll 22 and the frame 23. The balance weight 8 is a member for suppressing vibration of the compressor 100 and increasing the flow rate of the refrigerant, and is attached to the crankshaft 3 (drive shaft). In the example shown in FIG. 1, the balance weight 8 is provided in the space between the compression mechanism 2 and the electric motor 6, radially inside the oil ring 15 (first partition wall). When the electric motor 6 is driven, the balance weight 8 rotates integrally with the crankshaft 3.

[0027] FIG. 3A is a perspective view of the balance weight 8 when viewed diagonally from above. As shown in FIG. 3A, the balance weight 8 is a metal member including an annular portion 8a, an arc portion 8b, and a protrusion 8c. The annular portion 8a is an annular portion fixed to the crankshaft 3 (see FIG. 1). In the annular portion 8a, a semicircular portion 81a connected to the arc portion 8b is wider in the radial direction than the remaining semicircular portion 82a (see also FIG. 4). The annular portion 8a has a hole 8h through which the crankshaft 3 (see FIG. 1) is inserted. With the crankshaft 3 inserted into the annular portion 8a, the annular portion 8a is fixed to the crankshaft 3 by press-fitting or the like.

[0028] The arc portion 8b is a portion that has an arc shape in a cross section and extends upward (to one axial side) from the annular portion 8a. Note that the "cross section" mentioned above means that the arc portion 8b is cut by a predetermined plane perpendicular to the central axis of the crankshaft 3 (see FIG. 1) and viewed from one axial side. By providing the arc portion 8b in this way, the balance weight 8 is able to suppress vibration of the compressor 100 (see FIG. 1).

[0029] FIG. 3B is a perspective view of the balance weight 8 when viewed from diagonally below. 3B is a portion that protrudes downward (to the other axial direction) from the annular portion 8a. As will be described in detail later, the protrusion 8c has the function of cooling the winding portion 61b (see FIG. 1) of the electric motor 6 by stirring the surrounding refrigerant and increasing the flow rate of the refrigerant. The protrusion 8c has a semicircular shape when viewed from below, and its circumferential range approximately coincides with the circumferential range of the arc portion 8b.

[0030] 3B is an example and is not limited thereto. For example, the circumferential range of the convex portion 8c may be included in the circumferential range of the arc portion 8b. By providing the convex portion 8c on the same side as the arc portion 8b in this way, the mass on the side of the arc portion 8b becomes relatively larger than that on the opposite side (the side where the arc portion 8b is not provided), and therefore vibration of the compressor 100 can be effectively suppressed.

[0031] In the example of FIG. 3B, the cross section perpendicular to the circumferential direction of the arc-shaped protrusion 8c is rectangular. In other words, the rectangular cross-section of the protrusion 8c extends in a semicircular shape in the circumferential direction. Furthermore, the protrusion 8c is provided at a position a predetermined distance radially outward from the inner circumferential edge of the annular portion 8a, and protrudes below the height of the inner circumferential edge of the lower surface of the annular portion 8a (see also FIG. 1). This configuration shortens the radial distance between the protrusion 8c and the winding portion 61b (see FIG. 1), and the movement of the protrusion 8c stirs the refrigerant, thereby accelerating the cooling of the winding portion 61b (see FIG. 1).

[0032] Therefore, even when an HFO refrigerant is used, it is possible to prevent disproportionation reactions from occurring around winding portion 61b, which is prone to high temperatures. A disproportionation reaction is a phenomenon in which, when a certain amount of ignition energy is applied in a high-temperature, high-pressure environment, a certain reaction proceeds in a chain reaction, generating a large amount of reaction heat and a sudden increase in pressure.

[0033] In addition, a protrusion 8c is provided at a position a predetermined distance radially inward from the outer circumferential edge of the annular portion 8a. This makes it easier to ensure an insulation distance between the protrusion 8c and the electric motor 6 (see FIG. 1). Furthermore, the protrusion 8c is provided between the inner circumferential edge and the outer circumferential edge of the annular portion 8a in the radial direction of the crankshaft 3. This increases the contact area between the balance weight 8 and the refrigerant compared to a configuration without the protrusion 8c. As a result, an increase in the flow rate of the refrigerant accompanying the movement of the balance weight 8 is promoted.

[0034] In the example of Fig. 1, the height position of the lower end of the protrusion 8c is approximately the same as the height position of the upper end of the winding portion 61b. As a result, while the balance weight 8 is moving, the refrigerant that is stirred by hitting the protrusion 8c easily comes into contact with the winding portion 61b, thereby facilitating cooling of the winding portion 61b. In addition, the height position of the lower surface of the annular portion 8a is higher than the height position of the upper end of the winding portion 61b. As a result, it is easy to ensure a predetermined insulation distance between the winding portion 61b and the balance weight 8.

[0035] 1, balance weight 8 is provided radially inside oil ring 15. This allows the refrigerant, whose flow rate is increased by the rotation of balance weight 8, to easily come into contact with winding portion 61b in the radially inside region of oil ring 15. This promotes cooling of winding portion 61b.

[0036] FIG. 4 is a plan view of the balance weight 8. As shown in FIG. In the example of FIG. 4, the arc portion 8b is provided over a range of approximately 180° in the circumferential direction with respect to the central axis Y1 of the crankshaft 3 (see FIG. 3). In other words, the central angle θ of the arc portion 8b when the central axis Y1 of the crankshaft 3 is used as the reference is approximately 180°. With this configuration, together with the other balance weight 9 (see FIG. 1) located on the opposite side of the balance weight 8 in the circumferential direction, vibration of the compressor 100 can be effectively suppressed. Furthermore, compared to when the outer shape is cylindrical (not shown), the end face of the arc portion 8b collides with the refrigerant, thereby increasing the flow rate of the refrigerant.

[0037] The circumferential range of the arc portion 8b is not limited to the example shown in Fig. 4. For example, the central angle θ of the arc portion 8b, when taken with respect to the central axis Y1 of the crankshaft 3, may be within a range of 135° or more and less than 225° (within a range of 180°±45°). Even with this configuration, it is possible to achieve both the function of reducing vibration of the compressor 100 (see Fig. 1) and the function of stirring the refrigerant inside the oil ring 15 (see Fig. 1).

[0038] Returning to Figure 1 again, the explanation will continue. The balance weight 9 is a metal member for suppressing vibration of the compressor 100 and increasing the flow rate of the refrigerant, and is installed below the rotor 62 of the electric motor 6. The balance weight 9 has a semicircular shape when viewed from below, and is located on the opposite side of the arc portion 8b of the other balance weight 8 in the circumferential direction.

[0039] The sub-frame 10 (lower frame) supports the lower part of the crankshaft 3 (drive shaft) and is fixed to the sealed container 1. The sub-bearing 11 is a bearing that supports the lower part of the crankshaft 3 and receives a radial load from the crankshaft 3. The sub-bearing 11 is fixed to the circumferential surface of a hole (reference number not shown) in the sub-frame 10 by press-fitting or the like.

[0040] The oil supply pump 12 is a pump for sucking up lubricating oil from the oil reservoir R1 in the sealed container 1, and is installed at the lower end of the crankshaft 3. For example, a trochoid pump is used as this oil supply pump 12. The lubricating oil sucked up from the oil reservoir R1 by the oil supply pump 12 is led to the oil supply passage 3c of the crankshaft 3. The thrust bearing 13 is a bearing that receives the axial load from the crankshaft 3, and is installed near the lower end of the crankshaft 3. The legs 14 support the sealed container 1 and are installed in the bottom chamber 1c.

[0041] The oil ring 15 (first partition) is a cylindrical partition that separates the refrigerant, etc., descending through the groove M1 (see FIG. 2) of the compression mechanism 2 from the refrigerant discharged through the discharge pipe P2. Note that the refrigerant mixed with mist-like lubricating oil is referred to as "refrigerant, etc." As shown in FIG. 1, the oil ring 15 is provided between the compression mechanism 2 and the electric motor 6. The oil ring 15 is fixed to the lower side of the frame 23 of the compression mechanism 2.

[0042] FIG. 5 is a perspective view of the oil ring 15. As shown in FIG. 5, the oil ring 15 includes a thin-walled cylindrical portion 15a and an annular fixing portion 15b extending radially inward from the upper end of the cylindrical portion 15a. The oil ring 15 may be made of metal or resin. For example, by making the oil ring 15 out of metal, the strength of the oil ring 15 can be increased and deformation thereof can be suppressed.

[0043] The fixed portion 15b is an annular portion fixed to the frame 23 (see FIG. 1). In the example of FIG. 5, four screw holes H1 are formed in the fixed portion 15b at equal intervals in the circumferential direction. A screw (not shown) is inserted into each screw hole H1 and further screwed into a screw hole (not shown) in the lower surface of the frame 23 (see FIG. 1). This causes the upper surface of the oil ring 15 to contact the lower surface of the frame 23 over the entire circumferential direction. Therefore, almost no gap is created between the oil ring 15 and the frame 23, and therefore, refrigerant and the like that flows out through the groove M1 (see FIG. 2) of the compression mechanism 2 can be prevented from entering the inside of the oil ring 15.

[0044] The cylindrical portion 15a is a tubular portion extending downward from the outer periphery of the annular fixed portion 15b. The cylindrical portion 15a is provided with a hole H2 for inserting the discharge pipe P2 (see FIG. 1). The upstream end of the discharge pipe P2 (see FIG. 1) is positioned radially inside the oil ring 15 (first partition wall). This prevents the refrigerant and the like that flows out through the groove M1 (see FIG. 2) of the compression mechanism 2 from directly heading toward the discharge pipe P2.

[0045] As shown in Fig. 1, a radial gap K1 (annular gap in plan view) is provided around the entire circumference of the cylindrical portion 15a between the outer peripheral surface of the oil ring 15 and the inner peripheral surface of the sealed container 1. The refrigerant and the like that descend through the groove M1 (see Fig. 2) of the compression mechanism 2 descends while swirling through the gap K1 between the cylindrical portion 15a and the sealed container 1. In this way, the oil ring 15 not only functions to suppress the outflow of lubricating oil (oil rising) from the discharge pipe P2, but also functions to guide the flow of the refrigerant and the like.

[0046] It is preferable that the diameter of the outer peripheral surface of the oil ring 15, relative to the central axis of the crankshaft 3, is equal to or smaller than the diameter of the bottom of the groove M1 (see FIG. 2) of the compression mechanism 2. With this configuration, the fixed portion 15b (see FIG. 5) of the oil ring 15 is hidden radially inside the groove M1 (see FIG. 2), so that the flow of the refrigerant and the like descending through the groove M1 is not obstructed by the fixed portion 15b.

[0047] The core back 61a of the stator 61 is provided with a plurality of grooves (not shown) that connect the upper side (one side) and the lower side (the other side) of the stator 61 in the axial direction. Specifically, a plurality of vertical grooves (not shown) that are recessed radially inward are provided in the outer peripheral wall of the core back 61a of the stator 61. The refrigerant and the like that flow through the annular gap K1 between the oil ring 15 and the sealed container 1 are guided to the lower side of the electric motor 6 via the grooves (not shown).

[0048] It is preferable that the diameter of the outer peripheral surface of the oil ring 15 is equal to or smaller than the diameter of the bottom of the groove (not shown) in the core back 61a, relative to the central axis of the crankshaft 3. With this configuration, the refrigerant and the like flowing through the annular gap K1 (see FIG. 1) between the oil ring 15 and the sealed container 1 is guided directly to the underside of the electric motor 6 via the groove (not shown) in the core back 61a. Furthermore, even if mist-like lubricating oil is blown up through the groove (not shown) in the core back 61a, the lubricating oil can be prevented from entering the inside of the oil ring 15.

[0049] As shown in FIG. 1, oil ring 15 is provided radially outside winding portion 61b of stator 61. The lower end of oil ring 15 (first partition wall) surrounds winding portion 61b of stator 61. That is, the height position of the lower end of oil ring 15 is lower than the height position of the upper end of winding portion 61b, and oil ring 15 extends downward so as to surround the vicinity of the upper end of winding portion 61b. With this configuration, the refrigerant stirred by convex portion 8c of balance weight 8 (see FIG. 3B) inside oil ring 15 is more likely to come into contact with winding portion 61b. As a result, winding portion 61b, which is at a high temperature and prone to disproportionation reaction, can be cooled. 1, the lower end of the oil ring 15 is spaced a predetermined distance in the vertical direction from the electric motor 6. This ensures an insulating distance when the oil ring 15 is made of metal.

[0050] Next, the positional relationship between the oil ring 15 and the balance weight 8 will be described. As shown in Fig. 1, it is preferable that the convex portion 8c of the balance weight 8 overlaps with the oil ring 15 (first partition wall) in the radial direction of the oil ring 15. In other words, it is preferable that the position of the lower end of the convex portion 8c is higher than the position of the lower end of the oil ring 15. With this configuration, the balance weight 8 is contained within the oil ring 15, and the refrigerant present inside the oil ring 15 is easily stirred by the convex portion 8c. As a result, the winding portion 61b is cooled by the refrigerant stirred by the convex portion 8c.

[0051] 1, the upstream end of the discharge pipe P2 is positioned higher in the vertical direction than the balance weight 8. With this configuration, even if the lubricating oil accumulated in the annular portion 8a of the balance weight 8 turns into mist again, the upstream end of the discharge pipe P2 is positioned above the balance weight 8, making it difficult for the mist of lubricating oil to enter the discharge pipe P2. As a result, it is possible to prevent the lubricating oil from leaking out through the discharge pipe P2.

[0052] <Effects> According to the first embodiment, the flow rate of the refrigerant around winding portion 61b can be increased by rotation of balance weight 8. Furthermore, because the upper end of winding portion 61b is surrounded by oil ring 15, the flow rate of the refrigerant is increased inside oil ring 15 as the refrigerant is stirred by balance weight 8. This allows winding portion 61b, which tends to become hot, to be cooled by the refrigerant, thereby suppressing the disproportionation reaction that occurs when an HFO refrigerant is used.

[0053] Furthermore, since the upstream end of the discharge pipe P2 is located inside the oil ring 15, it is possible to prevent the refrigerant (gas refrigerant mixed with mist-like lubricating oil) flowing out of the compression mechanism 2 from heading directly toward the discharge pipe P2. This makes it possible to prevent the lubricating oil from flowing out of the compressor 100. In this way, according to the first embodiment, it is possible to improve the performance and reliability of the compressor 100.

[0054] Second Embodiment The second embodiment differs from the first embodiment in that a plurality of recesses 15c (see FIG. 6A) are provided in an oil ring 15A (see FIG. 6A). The other configurations are the same as those of the first embodiment. Therefore, only the parts that are different from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0055] FIG. 6A is a perspective view of an oil ring 15A included in a compressor according to the second embodiment, viewed obliquely from above. 6A, the oil ring 15A (first partition wall) has a plurality of recesses 15c recessed radially inward. The thickness of the oil ring 15A is approximately the same between the recesses 15c and the portion other than the recesses 15c, but these thicknesses may be different.

[0056] In the example of FIG. 6A, four recesses 15c are provided at equal intervals in the circumferential direction. Furthermore, among the four screw holes H1, one recess 15c is provided between each pair of adjacent screw holes H1 in the circumferential direction. The recesses 15c are arc-shaped in plan view and are provided from a predetermined position on the oil ring 15A to the upper end in the vertical direction. Furthermore, the fixing portion 15b is also cut out in an arc-shaped manner at a location corresponding to the recesses 15c. By providing multiple recesses 15c in this manner, the volume of the oil ring 15A is reduced compared to the first embodiment (see FIG. 5). As a result, an increase in the refrigerant flow rate caused by the movement of the balance weight 8 (see FIG. 1) inside the oil ring 15A is promoted.

[0057] FIG. 6B is a perspective view of the oil ring 15A when viewed from diagonally below. As described above, recess 15c is provided in a portion of oil ring 15A above a predetermined location in the vertical direction. Electric motor 6 (see FIG. 1) is disposed in oil ring 15A below recess 15c. This prevents electric motor 6 (see FIG. 1) from interfering with oil ring 15A, while balance weight 8 (see FIG. 1) increases the flow rate of the refrigerant inside oil ring 15A. Furthermore, providing recess 15c creates a speed difference in the refrigerant flow in the circumferential direction, and turbulence is likely to occur due to the refrigerant impinging on recess 15c. This promotes cooling of winding portion 61b of stator 61 (see FIG. 1).

[0058] FIG. 7 is a perspective view of the compressor 100A with the sealed container and the like removed. The white arrows in Fig. 7 indicate the flow of mist-like lubricating oil mixed in the refrigerant. The arrow below the crankshaft 3 in Fig. 7 indicates the direction in which the crankshaft 3 rotates. As in the first embodiment (see also Fig. 2), the groove M1 shown in Fig. 7 is a flow path that guides the refrigerant compressed in the compression mechanism 2 to the lower side of the compression mechanism 2. The groove M2 shown in Fig. 7 is a flow path that guides the refrigerant descending through the annular gap K1 (see Fig. 1) between the oil ring 15A and the sealed container 1 (see Fig. 1) to the lower side of the electric motor 6.

[0059] As shown in Fig. 7, it is preferable that the circumferential position of the recess 15c is shifted from the circumferential position of the groove M1 of the compression mechanism part 2. This makes it difficult for mist-like lubricating oil swirling and descending through the annular gap K1 (see Fig. 1) between the oil ring 15A and the sealed container 1 (see Fig. 1) to enter the recess 15c, thereby preventing the lubricating oil from accumulating in the recess 15c. In the example of Fig. 7, the recess 15c is arranged in the opposite direction to the rotation direction of the crankshaft 3 and adjacent to the groove M1 of the compression mechanism part 2 in the circumferential direction. This makes it difficult for the lubricating oil flowing through the groove M1 to enter the recess 15c as it descends while swirling.

[0060] FIG. 8 is a cross-sectional view of the compressor 100A taken along a plane including the recess 15c. In the example of Fig. 8, a plurality of grooves M2 are formed in the stator 61 in the circumferential direction. As described above, the refrigerant and the like that flows downward while swirling through the annular gap K1 (see Fig. 1) between the oil ring 15A and the sealed container 1 is guided to the underside of the electric motor 6 via the grooves M2. In Fig. 8, a portion of the recess 15c of the oil ring 15A overlaps the area of ​​the groove M2 in the circumferential direction, but this is not limiting. For example, the circumferential range of the recess 15c and the circumferential range of the groove M2 may be offset from each other.

[0061] <Effects> According to the second embodiment, the volume of the oil ring 15A can be reduced by the amount of the recesses 15c provided in the oil ring 15A. Therefore, the increase in the flow rate of the refrigerant due to the balance weight 8 (see FIG. 1) is promoted in the inner region of the oil ring 15A. Furthermore, turbulence is likely to occur when the refrigerant collides with the recesses 15c, which promotes cooling of the winding portion 61b (see FIG. 1).

[0062] Third Embodiment The third embodiment differs from the first embodiment in that the oil ring 15B (see FIG. 9) includes a first oil ring 151 (see FIG. 9) on the upper side of the electric motor 6 and a second oil ring 152 on the lower side of the electric motor 6. The other configurations are the same as those of the first embodiment. Therefore, only the parts that differ from the first embodiment will be described, and a description of the overlapping parts will be omitted.

[0063] FIG. 9 is a vertical cross-sectional view of a compressor 100B according to the third embodiment. As shown in Fig. 9, the oil ring 15B includes a first oil ring 151 (first partition wall) and a second oil ring 152 (second partition wall). The first oil ring 151 is a cylindrical member that prevents the refrigerant and the like from the compression mechanism 2 from directly heading toward the discharge pipe P2, and is provided between the compression mechanism 2 and the electric motor 6. The configuration and arrangement of the first oil ring 151 are similar to those of the oil ring 15 (see Fig. 5) described in the first embodiment.

[0064] The second oil ring 152 is a member for preventing the refrigerant, etc., descending through the groove M2 (see FIG. 8) of the electric motor 6 from mixing with the refrigerant from which the lubricating oil has been separated near the oil reservoir R1, and is provided below the electric motor 6. As shown in FIG. 9, the second oil ring 152 (second bulkhead) is fixed to the upper side of the subframe 10 (lower frame). The second oil ring 152 may be made of metal or resin.

[0065] By providing the second oil ring 152 below the electric motor 6 in this manner, the space near the inner circumferential surface of the sealed container 1 is substantially isolated from the space around the winding portion 61b. This prevents the mist of lubricating oil descending through the annular gap K1 from mixing with the refrigerant from which the lubricating oil has been separated near the oil reservoir R1. As a result, the outflow of lubricating oil through the discharge pipe P2 can be prevented.

[0066] FIG. 10 is a perspective view of the second oil ring 152. As shown in FIG. 10, the second oil ring 152 (second partition wall) includes a plate-shaped portion 152a, a small diameter portion 152b, a connecting portion 152c, and a large diameter portion 152d. Note that the respective portions of the second oil ring 152 may be integrally formed, or a plurality of members may be appropriately combined.

[0067] The plate-shaped portion 152a is a portion fixed to the sub-frame 10 (see FIG. 9) and has a thin, annular shape. In the example of FIG. 10, three screw holes H3 for fixing the second oil ring 152 to the sub-frame 10 are provided at equal intervals in the circumferential direction in the plate-shaped portion 152a. The crankshaft 3 (drive shaft: see FIG. 9) is inserted through the hole H4 in the plate-shaped portion 152a and the small-diameter portion 152b, and the plate-shaped portion 152a is fixed to the sub-frame 10 (see FIG. 9).

[0068] The small-diameter portion 152b has a thin cylindrical shape and extends upward from the inner circumferential edge of the plate-shaped portion 152a. The upper end of the small-diameter portion 152b is connected to the inner circumferential edge of the annular connecting portion 152c. The diameter of the hole H4 in the small-diameter portion 152b is longer than the outer diameter of the crankshaft 3 (see FIG. 9). The refrigerant, from which the lubricating oil has been separated at the bottom of the sealed container 1 (see FIG. 9), is guided to the upper side of the electric motor 6 through the annular gap between the crankshaft 3 (see FIG. 9) and the small-diameter portion 152b. In addition, because the gap between the crankshaft 3 and the small-diameter portion 152b is narrow, the flow rate of the refrigerant is increased as it ascends through this gap. This promotes cooling of the winding portion 61b (see FIG. 9) of the electric motor 6.

[0069] The connecting portion 152c is a portion that connects the upper end of the small diameter portion 152b and the lower end of the large diameter portion 152d, and is in the shape of a thin ring. The shape of the connecting portion 152c is the same as that of the plate-like portion 152a. The large diameter portion 152d is a cylindrical portion with a larger diameter than the small diameter portion 152b, and extends upward from the outer circumferential edge of the connecting portion 152c.

[0070] As shown in FIG. 9 , the large-diameter portion 152d is located radially outward of the winding portion 61b. The upper end of the large-diameter portion 152d surrounds the winding portion 61b. That is, the upper end of the large-diameter portion 152d is located higher than the lower end of the winding portion 61b. With this configuration, the second oil ring 152 surrounds the vicinity of the lower end of the winding portion 61b. Therefore, the refrigerant, whose flow velocity is increased as it rises through the annular gap between the crankshaft 3 and the small-diameter portion 152b, comes into contact with the winding portion 61b inside the second oil ring 152. Furthermore, the rotation of the lower balance weight 9 also agitates the refrigerant, increasing its flow velocity. As a result, cooling of the winding portion 61b is promoted, thereby suppressing the occurrence of disproportionation reactions.

[0071] Furthermore, a predetermined gap is provided between the large diameter portion 152d and the stator 61. In other words, there is no particular contact between the second oil ring 152 and the stator 61. This ensures a predetermined insulation distance between the stator 61 and the second oil ring 152, for example, when the second oil ring 152 is made of metal.

[0072] The large diameter portion 152d is preferably located radially inward of the groove M2 (see FIG. 8) of the stator 61. This makes it possible to prevent the refrigerant, etc. descending sequentially through the groove M2 and the annular gap K2 (the gap between the inner circumferential surface of the sealed container 1 and the second oil ring 152) from mixing with the refrigerant ascending in the space inside the second oil ring 152.

[0073] <Effects> According to the third embodiment, by providing the second oil ring 152 below the electric motor 6, it is possible to further suppress the outflow of lubricating oil through the discharge pipe P2 than in the first embodiment. In addition, the flow rate of the refrigerant is increased as it ascends through the annular gap between the crankshaft 3 and the small diameter portion 152b, which promotes cooling of the winding portion 61b. This prevents the winding portion 61b from becoming an ignition energy source for the disproportionation reaction, thereby improving the reliability of the compressor 100B.

[0074] Fourth Embodiment In the fourth embodiment, an air conditioner W1 (see FIG. 11) including the compressor 100 (see FIG. 1) described in the first embodiment will be described.

[0075] FIG. 11 is a configuration diagram including a refrigerant circuit Q1 of an air conditioner W1 according to the fourth embodiment. The solid arrows in FIG. 11 indicate the flow of the refrigerant in the heating cycle. On the other hand, the dashed arrows in FIG. 11 indicate the flow of refrigerant in the cooling cycle. The air conditioner W1 is a device that performs air conditioning such as cooling and heating. As shown in Fig. 11, the air conditioner W1 is equipped with a compressor 100, an outdoor heat exchanger 71, an outdoor fan 72, an expansion valve 73, a four-way valve 74, an indoor heat exchanger 75, and an indoor fan 76. In the example of Fig. 11, the compressor 100, the outdoor heat exchanger 71, the outdoor fan 72, the expansion valve 73, and the four-way valve 74 are provided in the outdoor unit U1. The indoor heat exchanger 75 and the indoor fan 76 are provided in the indoor unit U2.

[0076] The compressor 100 is a scroll compressor that compresses a gaseous refrigerant, and has the same configuration as the first embodiment (see FIG. 1). The outdoor heat exchanger 71 is a heat exchanger that exchanges heat between the refrigerant flowing through its heat transfer tubes (not shown) and the outside air sent in from the outdoor fan 72. The outdoor fan 72 is a fan that sends the outside air to the outdoor heat exchanger 71. The outdoor fan 72 is provided with an outdoor fan motor 72a that serves as a drive source, and is installed near the outdoor heat exchanger 71.

[0077] The indoor heat exchanger 75 is a heat exchanger in which heat is exchanged between the refrigerant flowing through its heat transfer pipes (not shown) and the indoor air (air in the air-conditioned room) sent in from the indoor fan 76. The indoor fan 76 is a fan that sends the indoor air to the indoor heat exchanger 75. The indoor fan 76 is provided with an indoor fan motor 76a that serves as a drive source, and is installed near the indoor heat exchanger 75.

[0078] The expansion valve 73 is a valve that reduces the pressure of the refrigerant condensed in the "condenser" (one of the outdoor heat exchanger 71 and the indoor heat exchanger 75). The refrigerant reduced in pressure by the expansion valve 73 is introduced to the "evaporator" (the other of the outdoor heat exchanger 71 and the indoor heat exchanger 75).

[0079] The four-way valve 74 is a valve that switches the refrigerant flow path depending on the operation mode of the air conditioner W1. For example, during cooling operation (see the dashed arrow in FIG. 11), the refrigerant circulates in the refrigerant circuit Q1 sequentially through the compressor 100, the outdoor heat exchanger 71 (condenser), the expansion valve 73, and the indoor heat exchanger 75 (evaporator). On the other hand, during heating operation (see the solid arrow in FIG. 11), the refrigerant circulates in the refrigerant circuit Q1 sequentially through the compressor 100, the indoor heat exchanger 75 (condenser), the expansion valve 73, and the outdoor heat exchanger 71 (evaporator).

[0080] <Effects> According to the fourth embodiment, the air conditioner W1 is equipped with a compressor 100 that has high performance and reliability, thereby improving the overall performance and reliability of the air conditioner W1.

[0081] <<Variations>> Although the compressor 100 and the air conditioner W1 according to the present invention have been described in the above in relation to the various embodiments, the present invention is not limited to these descriptions and various modifications can be made. For example, in each embodiment, the balance weight 8 (see FIG. 3B) has one protrusion 8c (see FIG. 3B), but this is not limiting. That is, as will be described next, the balance weight may have multiple protrusions.

[0082] FIG. 12 is a perspective view of a balance weight 8C of a compressor according to a first modified example, viewed obliquely from below. As shown in FIG. 12, the balance weight 8C has multiple protrusions 8d. When the annular portion 8a of the balance weight 8C is viewed from below, the multiple protrusions 8d are scattered. In the example of FIG. 12, five protrusions 8d extend downward from the annular portion 8a. These five protrusions 8d are rectangular parallelepiped-shaped and are equally spaced in the circumferential direction. In the example of FIG. 12, the protrusions 8d are positioned at equal radial positions. Providing multiple protrusions 8d in this manner facilitates turbulence around the winding portion 61b (see FIG. 1) as the balance weight 8C rotates. This promotes cooling of the winding portion 61b, thereby suppressing the disproportionation reaction. The number of protrusions 8d is not limited to five, and may be four or less, or six or more. That is, the balance weight 8C may have at least one protrusion 8d.

[0083] FIG. 13 is a perspective view of a balance weight 8D of a compressor according to a second modification, viewed obliquely from below. In the example of FIG. 13, balance weight 8C has five cylindrical protrusions 8e. When annular portion 8a of balance weight 8C is viewed from below, five protrusions 8e are scattered. In the example of FIG. 13, five protrusions 8e are provided at equal intervals in the circumferential direction and are positioned at equal radial positions. Even with this configuration, turbulence is generated around winding portion 61b (see FIG. 1), thereby facilitating cooling of winding portion 61b.

[0084] FIG. 14 is a perspective view of a balance weight 8E of a compressor according to a fourth modification, viewed obliquely from below. In the example of Figure 14, balance weight 8D has five cylindrical protrusions 8f. Among the five protrusions 8f, some are located at different radial positions. This makes it easier to generate turbulence around winding portion 61b (see Figure 1), thereby facilitating cooling of winding portion 61b. Note that protrusions 8f may have other shapes, such as a triangular prism or a polygonal prism, in addition to a cylindrical shape.

[0085] In the second embodiment, four recesses 15c (see FIG. 6A) are provided in the oil ring 15A (see FIG. 6A), but this is not limiting. That is, the number of recesses 15c may be three or less, or may be five or more. That is, at least one recess 15c may be provided in the oil ring 15A.

[0086] In addition, in each embodiment, the height position of the lower end of the protrusion 8c (see FIG. 1) of the balance weight 8 is described as coinciding with the height position of the upper end of the winding portion 61b, but this is not limiting. For example, the height position of the lower end of the protrusion 8c may be lower than the height position of the upper end of the winding portion 61b. This allows the refrigerant stirred by hitting the protrusion 8c to more easily come into contact with the winding portion 61b, thereby facilitating cooling of the winding portion 61b.

[0087] Furthermore, the respective embodiments can be combined as appropriate. For example, the second embodiment and the third embodiment may be combined to provide a configuration in which the first oil ring 151 (see FIG. 9) has a plurality of recesses 15c (see FIG. 6A) (second embodiment), and further include a second oil ring 152 (see FIG. 9) (third embodiment). Furthermore, it is also possible to combine the second embodiment with the fourth embodiment to configure an air conditioner (fourth embodiment) that includes a compressor having an oil ring 15A (see FIG. 6A) provided with a plurality of recesses 15c (see FIG. 6A) and also includes an outdoor heat exchanger 71, an expansion valve 73, an indoor heat exchanger 75, etc. In addition, various combinations are possible, such as the third embodiment and the fourth embodiment.

[0088] Furthermore, in each embodiment, a configuration in which the compressor 100 is installed vertically has been described, but this is not limiting. For example, each embodiment can also be applied to a configuration in which the compressor 100 is installed horizontally or obliquely. In such a case, one axial side of the compressor 100 (the side of the lid chamber 1b) is the "upper side," and the other axial side of the compressor 100 (the side of the bottom chamber 1c) is the "lower side." In addition, in each embodiment, the compressor 100 is described as being of a scroll type, but this is not limiting. That is, each embodiment can also be applied to other types of compressors, such as a rotary type.

[0089] Furthermore, in the fourth embodiment, a configuration has been described in which the air conditioner W1 (see FIG. 11) is provided with a four-way valve 74, but this is not limiting. That is, the four-way valve 74 may be omitted, and the air conditioner may be dedicated to cooling or heating. Furthermore, the air conditioner W1 (see FIG. 11) described in the fourth embodiment can be applied to various types of air conditioners, such as room air conditioners, package air conditioners, and multi-air conditioners for buildings.

[0090] Furthermore, in the fourth embodiment, the air conditioner W1 (see FIG. 11) including the compressor 100 has been described, but the present invention is not limited to this. For example, the fourth embodiment can also be applied to other refrigeration cycle devices such as a refrigerator, a water heater, an air-conditioning water heater, and a chiller.

[0091] Furthermore, each embodiment has been described in detail to clearly explain the present invention, and is not necessarily limited to having all of the configurations described. Furthermore, part of the configuration of each embodiment can be appropriately added to, deleted from, or replaced with other configurations. Furthermore, the mechanisms and configurations described above are those that are considered necessary for the explanation, and do not necessarily represent all mechanisms and configurations of the product. [Explanation of symbols]

[0092] 1. Airtight container 2 Compression mechanism 3 Crankshaft (drive shaft) 6 Electric motor 8,8C,8D,8E balance weight 8a Annular section 8b Arc section 8c, 8d, 8e convex parts 100 Compressor 10 Subframe (lower frame) 15,15A Oil ring (first bulkhead) 15c recess 61 Stator 61a Core Back 61b Winding section 62 Rotor 71 Outdoor heat exchanger 73 Expansion valve 75 Indoor heat exchanger 100, 100A, 100B compressor 151 First oil ring (first bulkhead) 152 Second oil ring (second bulkhead) 152a Plate-shaped part 152b Small diameter section 152c connection 152d Large diameter section P1 suction pipe P2 discharge pipe M1 groove W1 Air Conditioner

Claims

1. A sealed container and an electric motor installed inside the sealed container and having a stator and a rotor; a drive shaft that rotates integrally with the rotor; a compression mechanism that compresses a refrigerant as the drive shaft rotates; a discharge pipe that guides the refrigerant compressed by the compression mechanism to the outside of the sealed container; a balance weight installed on the drive shaft; a cylindrical first partition wall provided between the compression mechanism and the electric motor, the balance weight has an annular portion fixed to the drive shaft with the drive shaft inserted therethrough, an arc portion extending upward from the annular portion, and at least one protrusion protruding downward from the annular portion, an upstream end of the discharge pipe is located radially inside the first partition wall, a lower end of the first partition wall surrounds a winding portion of the stator, The convex portion protrudes downward from a height position of an inner peripheral edge of a lower surface of the annular portion.

2. the protrusion overlaps the first partition wall in the radial direction of the first partition wall; The compressor according to claim 1 .

3. The circumferential range of the convex portion is included in the circumferential range of the arc portion. The compressor according to claim 1 .

4. The cylindrical first partition wall has a plurality of recesses recessed radially inward. The compressor according to claim 1 .

5. the compression mechanism has a groove that communicates one side and the other side of the compression mechanism in the axial direction of the drive shaft, The circumferential position of the recess is shifted from the circumferential position of the groove. The compressor according to claim 4,

6. The balance weight has a plurality of the protrusions, When the annular portion is viewed from below, the plurality of protrusions are arranged in a scattered manner. The compressor according to claim 1 .

7. a second partition wall provided below the electric motor; a lower frame that supports a lower portion of the drive shaft, The second partition is fixed to the upper side of the lower frame. The compressor according to claim 1 .

8. the second partition wall has an annular plate-shaped portion fixed to the lower frame with the drive shaft inserted therethrough, a cylindrical small-diameter portion extending upward from an inner peripheral edge of the plate-shaped portion, and a cylindrical large-diameter portion having a diameter larger than that of the small-diameter portion, and also has an annular connecting portion connecting an upper end of the small-diameter portion and a lower end of the large-diameter portion. The compressor according to claim 7,

9. The upper end of the large diameter portion surrounds the winding portion. The compressor according to claim 8,

10. The compressor according to any one of claims 1 to 9 is provided, An air conditioner comprising an outdoor heat exchanger, an expansion valve, and an indoor heat exchanger.

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