Compressor and refrigeration cycle device

Abstract

The present disclosure aims to obtain a compressor that suppresses stirring of refrigerant gas and refrigerant oil generated by a balance weight and improves the efficiency of separation of refrigerant oil from refrigerant. The compressor of the present disclosure includes a hermetic container, a compression mechanism portion provided in the hermetic container to compress refrigerant, an electric motor provided in the hermetic container to generate a driving force, and a rotating shaft to transmit the driving force generated by the electric motor to the compression mechanism portion. The electric motor includes a rotor, a stator, a first balance weight fixed to an end surface of the rotor opposite the compression mechanism portion, and a first cup-shaped member having a side wall surrounding an outer circumferential surface of the first balance weight. The first balance weight is formed by connecting a light portion in a circular arc shape and a heavy portion in a circular arc shape, and includes a separation portion that is a recess formed in the end surface opposite the rotor and that is open at the outer circumferential surface of the first balance weight. The separation portion is disposed opposite an opening of a through flow path, and the side wall of the first cup-shaped member includes a discharge port portion located radially outward of the separation portion.

Description

Technical Field

[0001] This disclosure relates to compressors and refrigeration cycle devices, and in particular to the construction of the refrigerant flow path inside the compressor. Background Technology

[0002] For example, a scroll compressor includes: a sealed container, a compression mechanism consisting of a fixed scroll and a oscillating scroll, and an electric motor that drives the oscillating scroll of the compression mechanism to rotate. If the high-pressure refrigerant gas compressed by the compression mechanism and discharged from the outlet of the fixed scroll is directly discharged outside the sealed container, the refrigerant gas contains refrigeration oil that lubricates the bearings of the drive unit. Therefore, the refrigeration oil stored at the bottom of the sealed container decreases, and due to insufficient oil supply, the bearings of the rotating shaft that drives the oscillating scroll may sinter, causing malfunctions in the scroll compressor.

[0003] As a technology to solve this problem, a scroll compressor has been proposed, which has a structure that reduces the amount of refrigerant oil flowing out of the sealed container (for example, see Patent Document 1). The scroll compressor disclosed in Patent Document 1 includes: a compression unit, an electric motor driving the compression unit, and a counterweight for counteracting the imbalance of centrifugal force and torque generated by the compression unit. The counterweight is fixed to the upper and lower ends of the rotor, and a cup portion is provided surrounding the counterweight. The cup portion prevents the refrigerant and refrigerant oil in the sealed container from being agitated by the counterweight.

[0004] The mixture of refrigerant gas and refrigeration oil discharged from the compressor section is guided to the lower part of the sealed container through the refrigerant flow path. Upon reaching the lower part of the sealed container, the mixture passes through the rotor's through-flow path and is discharged towards the compressor section, flowing into a discharge hood mounted on the end face of the compressor. During this process of the mixture passing through the refrigerant flow path and the through-flow path, the refrigeration oil contained in the mixture is separated, thereby reducing the amount of refrigeration oil in the mixture.

[0005] Patent Document 1: Japanese Patent Application Publication No. 2014-109194

[0006] Patent Document 1 discloses a scroll compressor with a fixed counterweight to counteract the force imbalance caused by the revolution of the oscillating scroll. This counterweight rotates like fan blades, thereby agitating the refrigerant oil and refrigerant gas discharged from below the rotor through a through-flow path. Therefore, the refrigerant and refrigerant oil discharged through the rotor's through-flow path are agitated again by the counterweight, resulting in the problem of suppressing refrigerant and refrigerant oil separation and failing to adequately prevent oil leakage. Summary of the Invention

[0007] This disclosure was made to solve the aforementioned problems, and aims to provide a compressor and a refrigeration cycle device that suppresses the mixing of refrigerant gas and refrigeration oil caused by the balance counterweight and improves the efficiency of separating refrigeration oil from the refrigerant.

[0008] The compressor disclosed herein comprises: a sealed container having an oil reservoir for storing refrigeration oil; a compression mechanism disposed within the sealed container for compressing refrigerant; an electric motor disposed within the sealed container for generating driving force; and a rotating shaft for transmitting the driving force generated by the electric motor to the compression mechanism, the electric motor comprising: a rotor fixed to the rotating shaft; a stator fixed to the sealed container and forming a refrigerant flow path for guiding refrigerant gas discharged from the compression mechanism to the lower part of the sealed container; and a first counterweight fixed to the rotor. The compression mechanism has an opposing end face; and a first cup-shaped component having a sidewall surrounding the outer peripheral surface of the first counterweight, the first counterweight being formed by connecting an arc-shaped lightweight portion and an arc-shaped heavy-duty portion, the first counterweight having a separation portion, the separation portion being a recess formed in the end face opposite to the rotor and opening in the outer peripheral surface of the first counterweight, the separation portion being disposed opposite to the opening of a through flow path provided axially through the rotor, the sidewall of the first cup-shaped component having a discharge port, the discharge port being located radially outward relative to the separation portion.

[0009] The refrigeration cycle apparatus disclosed herein includes the aforementioned compressor.

[0010] According to this disclosure, the compressor causes refrigeration oil, which flows through the rotor along with the refrigerant, to collide with a separation section and be discharged from a discharge port located on the side wall of a first cup-shaped component to the outside of the first cup-shaped component. The separation section is located on the end face of a first balancing weight located on the upper part of the rotor. This suppresses the agitation of the refrigeration oil by the first balancing weight, preventing the refrigeration oil from flowing into the opening of the discharge shroud connected to the discharge pipe along with the refrigerant. Consequently, the compressor and the refrigeration cycle device improve the efficiency of separating the refrigeration oil from the refrigerant. Attached Figure Description

[0011] Figure 1 This is a longitudinal sectional view of a scroll compressor 100, which is the compressor in Embodiment 1.

[0012] Figure 2 This is an example of a refrigeration cycle device using the scroll compressor 100 of Embodiment 1.

[0013] Figure 3 This indicates that it is set in Figure 1A cross-sectional view of the first passage 4f on the outer periphery of the guide bracket 4.

[0014] Figure 4 This is a cross-sectional view of the rotor 5a of the scroll compressor 100 according to Embodiment 1.

[0015] Figure 5 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 1.

[0016] Figure 6 This is an enlarged view of the peripheral structure of the first cup-shaped component 17 of the scroll compressor 100 according to Embodiment 1.

[0017] Figure 7 This is a cross-sectional view of the stator 5b of the motor 5 of the scroll compressor 100 in Embodiment 1.

[0018] Figure 8 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 2.

[0019] Figure 9 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 3.

[0020] Figure 10 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 4.

[0021] Figure 11 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4.

[0022] Figure 12 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4.

[0023] Figure 13 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4.

[0024] Figure 14 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 5.

[0025] Figure 15 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 5.

[0026] Figure 16 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 6.

[0027] Figure 17This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 6.

[0028] Figure 18 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 7.

[0029] Figure 19 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 8.

[0030] Figure 20 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 9. Detailed Implementation

[0031] Hereinafter, embodiments of the compressor of this disclosure will be described based on the accompanying drawings. Furthermore, the compressor described herein is shown as an example of a longitudinally mounted scroll compressor, but a transversely mounted compressor may also be used. Additionally, the compression mechanism may be a structure other than a scroll structure. (Further details include...) Figure 1 The following figures are schematic representations, and the relationship between the sizes of the structural components may differ from the actual situation.

[0032] Implementation method 1.

[0033] Figure 1 This is a longitudinal sectional view of a scroll compressor 100, which is the compressor in Embodiment 1. Figure 2 This is an example of a refrigeration cycle device using the scroll compressor 100 of Embodiment 1. The refrigeration cycle device 200 is used, for example, in various industrial machinery such as refrigerators, freezers, air conditioning units, refrigeration units, and water heaters. The scroll compressor 100 is one of the structural elements of the refrigeration cycle device 200.

[0034] (Refrigeration cycle unit 200)

[0035] The refrigeration cycle unit 200 is constructed by sequentially connecting a scroll compressor 100, a four-way switching valve 103, an indoor heat exchanger 106, a pressure reducer 105, and an outdoor heat exchanger 104 via piping. An intake silencer 101 is connected to the intake side of the scroll compressor 100 and is also connected to the four-way switching valve 103. The four-way switching valve 103 is also connected to the discharge side of the scroll compressor 100, switching the flow of refrigerant from the scroll compressor 100, thereby changing the direction of refrigerant flow within the circuit of the refrigeration cycle unit 200.

[0036] In Embodiment 1, the refrigeration cycle device 200 is exemplified as an air conditioning unit. The refrigeration cycle device 200 switches between cooling and heating operation by switching the four-way switching valve 103. Typically, for an air conditioning unit, the indoor heat exchanger 106 is mounted in the indoor unit, while the remaining components, such as the scroll compressor 100, the four-way switching valve 103, the outdoor heat exchanger 104, and the pressure reducer 105, are mounted in the outdoor unit.

[0037] For example, during the heating operation of an air conditioning unit, the four-way switching valve 103 and Figure 2 The solid line connects to the side. The high-temperature, high-pressure refrigerant compressed by the scroll compressor 100 flows to the indoor heat exchanger 106, which functions as a condenser, where it condenses and liquefies. The liquid refrigerant is compressed by the pressure reducer 105, becoming a low-temperature, low-pressure two-phase state, and flows into the outdoor heat exchanger 104. The gas-liquid two-phase refrigerant evaporates in the outdoor heat exchanger 104, which functions as an evaporator, and returns to the scroll compressor 100 via the four-way switching valve 103. That is, when the refrigeration cycle device 200 is in heating operation, the refrigerant... Figure 2 The cycle is as shown by the solid arrow. Through this cycle, the outdoor heat exchanger 104, which acts as an evaporator, exchanges heat with the outside air. The refrigerant delivered to the outdoor heat exchanger 104 absorbs heat, and the refrigerant after absorbing heat is delivered to the indoor heat exchanger 106, which acts as a condenser, to exchange heat with the indoor air and heat the indoor air.

[0038] When the air conditioning unit is in cooling operation, the four-way switching valve 103 and Figure 2 The dotted line connects to the outside. The high-temperature, high-pressure gaseous refrigerant, compressed by the scroll compressor 100, flows to the outdoor heat exchanger 104, which functions as a condenser, where it condenses and liquefies. The liquid refrigerant is compressed by the pressure reducer 105 into a low-temperature, low-pressure two-phase state and flows into the indoor heat exchanger 106. The gaseous-liquid two-phase refrigerant evaporates in the indoor heat exchanger 106, which functions as an evaporator, and returns to the scroll compressor 100 via the four-way switching valve 103.

[0039] That is, if the operation changes from heating to cooling, the indoor heat exchanger 106 changes from a condenser to an evaporator, and the outdoor heat exchanger 104 changes from an evaporator to a condenser. Therefore, the refrigerant... Figure 2 The refrigerant cycles as shown by the dashed arrow. Through this cycle, heat is exchanged with indoor air in the indoor heat exchanger 106, which acts as an evaporator. The refrigerant absorbs heat from the indoor air, thus cooling the indoor air. The refrigerant, after absorbing heat, is then transported to the outdoor heat exchanger 104, which acts as a condenser, to exchange heat with the outside air and dissipate heat to the outside air.

[0040] At this time, the refrigerant circulating in the refrigeration cycle unit 200 is usually R410A, R32, or R290 refrigerant.

[0041] (Scroll compressor 100)

[0042] As described above, the scroll compressor 100 draws in the refrigerant circulating in the refrigeration cycle unit 200, compresses it, and discharges it in a high-temperature, high-pressure state. The scroll compressor 100 has a compression mechanism 14 within the sealed container 10, which combines a fixed scroll member 1 and a oscillating scroll member 2 that revolves (oscillates) relative to the fixed scroll member 1. Furthermore, the scroll compressor 100 includes an electric motor 5 that drives the oscillating scroll member 2 via a rotating shaft 6. In Embodiment 1, a longitudinally mounted scroll compressor 100 will be described as an example. In the case of the longitudinally mounted scroll compressor 100, for example, the compression mechanism 14 is positioned at the top of the sealed container 10, and the electric motor 5 is positioned below the compression mechanism 14.

[0043] (Compression Mechanism Section 14)

[0044] The compression mechanism 14 includes a fixed scroll member 1, a swing scroll member 2, a flexible frame 3, and a guide support 4. The fixed scroll member 1 includes: a platform portion 1a; and plate-shaped vortex teeth 1b, which are the side of the platform portion 1a facing the side where the motor 5 is arranged. Figure 1 The vortex-shaped protrusions protrude from the lower middle side of the surface. Additionally, the oscillating vortex member 2 includes: a platform portion 2a; and plate-shaped vortex teeth 2b, which protrude from the surface of the platform portion 2a opposite to the fixed vortex member 1 (…). Figure 1 The upper middle surface is provided with a protruding spiral protrusion, which is substantially the same shape as the plate-shaped spiral tooth 1b. By making the plate-shaped spiral tooth 1b of the fixed spiral member 1 mesh with the plate-shaped spiral tooth 2b of the swing spiral member 2, a compression chamber 1f with a relative change in volume due to the revolution of the swing spiral member 2 is formed.

[0045] The scroll compressor 100 includes a guide bracket 4 that supports the compression mechanism 14 from below. The guide bracket 4 is fixed inside the sealed container 10, and the fixed scroll member 1 is fastened to the guide bracket 4 at its outer periphery by bolts (not shown). A suction pipe 13 for introducing refrigerant gas into the compression chamber 1f is provided at the outer periphery of the platform portion 1a of the fixed scroll member 1. The suction pipe 13 is connected to a suction port 1e equipped with a suction check valve 1g. A discharge port 1d is formed at the center of the platform portion 1a of the fixed scroll member 1 to discharge the refrigerant gas that has been compressed to high pressure. The compressed refrigerant gas is discharged into the upper space 10a inside the sealed container 10. The refrigerant gas discharged into the upper space 10a is guided to the oil separation mechanism through the refrigerant flow path as described later, and the refrigerant gas after separation of the refrigeration oil is discharged from the discharge pipe 12.

[0046] The oscillating scroll member 2 is prevented from rotating by the Euclidean mechanism 9, and is configured to revolve (oscillate) relative to the fixed scroll member 1 without rotating. Two pairs of Euclidean guide grooves 1c are formed almost in a straight line on the outer periphery of the platform portion 1a of the fixed scroll member 1. Two pairs of fixed side keys 9a of the Euclidean mechanism 9 are engaged with these Euclidean guide grooves 1c in a reciprocating sliding manner. Furthermore, on the outer periphery of the platform portion 2a of the oscillating scroll member 2, two pairs of Euclidean guide grooves 2c, having a 90-degree phase difference from the Euclidean guide grooves 1c of the fixed scroll member 1, are formed almost in a straight line. Two pairs of oscillating side keys 9b of the Euclidean mechanism 9 are engaged with these Euclidean guide grooves 2c in a reciprocating sliding manner. With the Euclidean mechanism 9 configured as described above, the oscillating scroll member 2 can oscillate (rotate) without rotating.

[0047] On the opposite side of the forming surface of the oscillating vortex component 2 and the plate-shaped vortex tooth 2b ( Figure 1 A hollow cylindrical protrusion 2d is formed at the center of the surface (the lower side). An eccentric shaft portion 6a, which is located at the upper end of the rotating shaft 6, is inserted into the protrusion 2d.

[0048] On the opposite side of the plate-shaped vortex tooth 2b in the platform portion 2a of the oscillating vortex member 2 ( Figure 1 The lower side of the middle section has a thrust surface 2f that can press and slide against the thrust bearing 3a of the flexible frame 3. In addition, an extraction hole 2g is provided in the platform portion 2a of the oscillating scroll member 2, which passes through the compression chamber 1f and the thrust surface 2f, so as to extract the refrigerant gas during compression and guide it to the thrust surface 2f.

[0049] The flexible frame 3 is housed within the guide support frame 4. The flexible frame 3 supports the oscillating scroll member 2 and the Euclid mechanism 9 from below, providing axial and radial support for the rotating shaft 6. Furthermore, the flexible frame 3 is supported by the guide support frame 4.

[0050] The flexible frame 3 has an upper cylindrical surface 3p and a lower cylindrical surface 3s on its outer periphery. The guide support frame 4 has an upper cylindrical surface 4c for fitting the upper cylindrical surface 3p of the flexible frame 3 and a lower cylindrical surface 4d for fitting the lower cylindrical surface 3s of the flexible frame 3 on its inner periphery. The guide support frame 4 radially supports the flexible frame 3 through the upper cylindrical surface 4c and the lower cylindrical surface 4d.

[0051] At the center of the lower cylindrical surface 3s of the flexible frame 3, there is a main bearing 3c and an auxiliary main bearing 3d that radially support the rotating shaft 6 driven by the rotor 5a of the electric motor 5.

[0052] A connecting hole 3e is provided, which extends axially through the outer periphery of the flexible frame 3 from within the plane of the thrust bearing 3a. The thrust bearing opening 3t, which opens at the upper end of the connecting hole 3e, is positioned face-to-face with the air extraction hole 2g of the platform portion 2a of the oscillating vortex member 2.

[0053] A reciprocating sliding surface 3b is formed on the outer periphery of the thrust bearing 3a of the flexible frame 3, allowing the annular portion 9c of the Euclid mechanism to reciprocate. Furthermore, the flexible frame 3 has a connecting hole 3f extending from the inner periphery to the outer periphery. The connecting hole 3f connects the outer periphery space 2k of the platform and the upper space 4a of the frame with the inner space of the annular portion 9c of the Euclid mechanism. The flexible frame 3 has an intermediate pressure adjusting valve 3g, an intermediate pressure adjusting valve pressing member 3h, and an intermediate pressure adjusting spring 3k disposed between the upper space 4a of the frame and the outer space 2n of the protrusion to adjust the pressure of the outer space 2n of the protrusion. The intermediate pressure adjusting spring 3k is shortened from its natural length and housed in the intermediate pressure adjusting valve space 3n. In embodiment 1, the flexible frame 3 and the guide support frame 4 are constructed independently, but this is not a limitation; they can also be integrated into a single structure.

[0054] The lower frame space 4b, formed by the inner side of the guide bracket 4 and the outer side of the flexible frame 3, is separated vertically by annular seals 7a and 7b. Here, annular sealing grooves for receiving the annular seals 7a and 7b are formed at two locations on the outer circumferential surface of the flexible frame 3; however, these sealing grooves can also be formed on the inner circumferential surface of the guide bracket 4. The lower frame space 4b is configured to communicate only with the connecting hole 3e of the flexible frame 3 and to seal in the refrigerant gas supplied from the extraction hole 2g during compression. Furthermore, the space on the outer periphery of the thrust bearing 3a, surrounded vertically by the platform portion 2a of the oscillating vortex member 2 and the flexible frame 3, i.e., the platform outer periphery space 2k, becomes a low-pressure space for the intake gas atmosphere (intake pressure).

[0055] Figure 3 It means in Figure 1 A cross-sectional view of the first passage 4f provided on the outer periphery of the guide support 4. (See attached image.) Figure 3As shown, the outer peripheral surface 40 of the guide support 4 is fixed to the sealed container 10 by hot pressing or welding. The outer peripheral portion of the guide support 4 and the outer peripheral portion of the fixed vortex member 1 are provided with notches, forming a first passage 4f. That is, a first passage 4f connecting the upper and lower spaces of the compression mechanism 14 is provided on the outer peripheral portion of the compression mechanism 14.

[0056] Refrigerant gas discharged from outlet 1d into the upper space 10a of the sealed container 10 flows downward through the first passage 4f. Refrigerant gas passing through the motor 5 located below the compressor unit 14 flows towards the bottom of the sealed container 10, where the oil storage section 10b is formed. The oil storage section 10b at the bottom of the sealed container 10 stores refrigeration oil 11.

[0057] The sealed container 10 is provided with a discharge pipe 12 for discharging the compressed refrigerant gas inside to the outside. The aforementioned first passage 4f is located on the opposite side of the discharge pipe 12, separated by the central axis. The guide support 4 has a first discharge passage 4g that communicates with the discharge pipe 12. The first discharge passage 4g has openings in the portion near the center of its lower end face and on its side, and is formed such that the space below the guide support 4 communicates with the discharge pipe 12 fixed to the sealed container 10.

[0058] A lower cylindrical portion 41 (the portion with the lower cylindrical surface 4d) is formed at the lower end of the guide bracket 4, supporting the lower cylindrical surface 3s of the flexible frame 3 radially outward. Furthermore, a discharge cover 16 is fixed to the end face of the guide bracket 4 opposite the motor 5, where the first discharge passage 4g is provided, in a manner that surrounds the lower cylindrical portion 41. The discharge cover 16 has an opening 16b formed at its central portion facing downward. A second discharge passage 16a formed by the discharge cover 16 and the end faces of the guide bracket 4 communicates with the first discharge passage 4g.

[0059] (Electric motor 5)

[0060] The electric motor 5 drives the rotating shaft 6 to rotate using the driving force generated by electricity, and includes a rotor 5a fixed to the rotating shaft 6 and a stator 5b fixed to the sealed container 10. The rotor 5a is fixed to the rotating shaft 6 by thermoforming or the like. When the stator 5b is energized, the rotor 5a is driven to rotate, causing the rotating shaft 6 to rotate. Furthermore, an eccentric shaft portion 6a is formed at the upper end of the rotating shaft 6, which rotatably engages with the oscillating bearing 2e of the oscillating scroll member 2. In addition, a rotating shaft counterweight 6f is fixed to the lower part of the eccentric shaft portion 6a by thermoforming or the like.

[0061] like Figure 1 As shown, a glass terminal 10c is provided on the side of the sealed container 10, and the glass terminal 10c is connected to the stator 5b of the motor 5 through a wire 5j.

[0062] On the lower side of the fixing part 6g, which is fixed with the eccentric shaft part 6a and the rotating shaft balance counterweight 6f, a main shaft part 6b is formed that can be rotatably engaged with the main bearing 3c and the auxiliary main bearing 3d of the flexible frame 3.

[0063] At the lower end of the rotating shaft 6, a secondary shaft portion 6c is formed, which rotatably engages with the secondary bearing 8a of the sub-frame 8 fixed to the lower part of the sealed container 10. The sub-frame 8 is fixed to the lower part of the sealed container 10 by means of thermoforming or the like, and an inflow hole 8b is provided so that the refrigeration oil 11 flows into the oil storage portion 10b formed at the lower end of the sealed container 10.

[0064] The rotor 5a of the motor 5 is fixed between the auxiliary shaft portion 6c at the lower end and the main shaft portion 6b at the upper end of the rotating shaft 6, for example, by thermoforming. The rotating shaft 6 has a through hole, i.e., an oil supply passage 6d, extending axially. An oil supply port 6e is installed at the lower end of the oil supply passage 6d. The oil supply port 6e is immersed in the refrigerant oil 11 stored at the bottom of the sealed container 10. Therefore, refrigerant oil 11 is drawn upward from the oil supply port 6e by an oil supply mechanism or pump mechanism provided at the lower part of the rotating shaft 6. The upper end of the oil supply passage 6d opens into the protrusion 2d of the oscillating vortex member 2, and the drawn-in refrigerant oil 11 flows out from the upper opening of the oil supply passage 6d to the oscillating bearing 2e, lubricating the eccentric shaft portion 6a and the oscillating bearing 2e.

[0065] The rotating shaft 6 is provided with an oil supply hole 6h branching from the oil supply passage 6d. The oil supply hole 6h extends in a direction intersecting the oil supply passage 6d. Refrigeration oil 11 is supplied from the oil supply hole 6h to the auxiliary main bearing 3d, lubricating the auxiliary main bearing 3d and the main shaft portion 6b. Additionally, an oil supply hole (not shown) on the rotating shaft 6 supplies refrigeration oil 11 to the main bearing 3c. Figure 1 Illustrations omitted.

[0066] (Rotor 5a)

[0067] Figure 4 This is a cross-sectional view of the rotor 5a of the scroll compressor 100 according to Embodiment 1. Figure 4 (a) shows a longitudinal section containing the central shaft of rotor 5a. Figure 4 (b) shows a cross-section perpendicular to the central axis of the rotor 5a. The rotor 5a is cylindrical and has a shaft fixing hole 5h at the center where a rotating shaft 6 is fixed. Furthermore, a through flow path 5f is formed around the shaft fixing hole 5h, extending parallel to the central axis and penetrating the rotor 5a in the vertical direction. In Embodiment 1, the through flow path 5f is arranged at four locations around the central axis of the rotor 5a, each equidistant from the central axis.

[0068] A first counterweight 15a is fixed to the upper end face 52 of the rotor 5a. A second counterweight 15i is fixed to the lower end face 53 of the rotor 5a. When viewed along the axial direction of the rotation shaft 6, the first counterweight 15a and the second counterweight 15i are fixed symmetrically with respect to the central axis of the rotation shaft 6. In other words, the centers of gravity of the first counterweight 15a and the second counterweight 15i are eccentrically positioned with respect to the central axis of the rotation shaft 6, and their respective centers of gravity are located symmetrically with respect to the central axis.

[0069] Figure 5 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 1. Figure 5 (a) is a diagram showing the rotor 5a viewed axially. Figure 5 (b) shows Figure 5 The cross-section of part AA in (a). For example... Figure 5 As shown, the first counterweight 15a is an annular ring surrounding the central shaft, formed by connecting a lightweight portion 15b (also formed in an arc shape) and a heavy portion 15c (also formed in an arc shape). Furthermore, the first counterweight 15a is fixed to the upper end face of the rotor 5a. A first cup-shaped component 17 is sandwiched between the first counterweight 15a and the upper end face of the rotor 5a.

[0070] like Figure 5 As shown in (a), the lightweight part 15b includes: an arcuate portion 15p arranged along the outer periphery of the rotor 5a; and two protrusions 15q formed by the inner peripheral surface 15k of the arcuate portion 15p partially protruding towards the center. The protrusions 15q protrude to the vicinity of the shaft fixing hole 5h of the rotor 5a, and are formed with fixing holes 15d for fixing members 15h for fixing the first counterweight 15a to the rotor 5a to pass through.

[0071] The heavy-duty section 15c is formed in a semi-cylindrical shape and is thicker than the light-duty section 15b in the direction of the central axis of the rotor 5a. Furthermore, the heavy-duty section 15c includes: a contact section 15f, which has a fixing hole 15d for the fixing member 15h to pass through; and a separating section 15g, which faces the upper end of the rotor 5a of the heavy-duty section 15c and is recessed from the surface that abuts against the first cup-shaped member 17. Figure 5 As shown in (b), the separation portion 15g is a recess formed on the surface of the rotor 5a opposite to the upper end face. This recess opens on the outer peripheral surface of the first counterweight 15a. The separation portion 15g is formed at a position corresponding to the through flow path 5f of the rotor 5a. That is, the separation portion 15g is a recess partially formed on the lower end face of the first counterweight 15a, and is formed such that the space surrounded by this recess communicates with the outer peripheral surface of the first counterweight 15a and the outer space.

[0072] The first balancing counterweight 15a, together with the second balancing counterweight 15i fixed to the lower end face of the rotor 5a and the rotating shaft balancing counterweight 6f fixed to the upper end of the rotating shaft 6, counteract the imbalance of centrifugal force and torque generated by the oscillation of the oscillating vortex member 2. That is, the compression mechanism 14 is configured to achieve dynamic and static balance through the first balancing counterweight 15a, the second balancing counterweight 15i, and the rotating shaft balancing counterweight 6f.

[0073] (First cup-shaped component 17 and second cup-shaped component 18)

[0074] like Figure 1 As shown, a first cup-shaped component 17 is fixed to the upper end face of the rotor 5a, surrounding the outer peripheral surface of the first counterweight 15a radially outward. A second cup-shaped component 18 is fixed to the lower end face of the rotor 5a, surrounding the outer peripheral surface of the second counterweight 15i. The first cup-shaped component 17 and the second cup-shaped component 18 are formed in a bottomed cylindrical shape, with holes formed in the central portion through which the rotating shaft 6 is inserted, at a position corresponding to the through flow path 5f of the rotor 5a, and in the portion through which the fixing member 15h is inserted.

[0075] Figure 6 This is an enlarged view of the peripheral structure of the first cup-shaped component 17 of the scroll compressor 100 according to Embodiment 1. The opening 17a at the upper end of the first cup-shaped component 17 is disposed opposite to the opening 16b of the aforementioned discharge shroud 16. The front end of the side wall 17c of the first cup-shaped component 17 protrudes toward the compression mechanism portion 14 beyond the end face of the first counterweight 15a. In Embodiment 1, the front end of the side wall 17c of the first cup-shaped component 17 is located axially below the opening 16b of the discharge shroud 16, but it may also be located at the same position as the opening 16b or above the opening 16b. A discharge port 17b is formed on the side wall 17c of the first cup-shaped component 17 at a position overlapping with the radially opening separation portion 15g of the first counterweight 15a. The refrigerant passing through the through flow path 5f is configured to flow from the separation portion 15g through the discharge port 17b to the outside of the side wall 17c of the first cup-shaped component 17.

[0076] The relationship between the inner diameter D of the opening 16b of the discharge hood 16 and the inner diameter d of the opening 17a of the first cup-shaped member 17 is D < d. That is, the inner diameter D of the opening 16b of the discharge hood 16 is smaller than the inner diameter d of the opening 17a at the upper end of the first cup-shaped member 17. Therefore, the flow of refrigerant oil discharged to the outside of the first cup-shaped member 17 into the opening 16b, which is located inside the side wall 17c of the first cup-shaped member 17, is suppressed.

[0077] The second cup-shaped component 18 is mounted on the lower end face of the rotor 5a with its opening facing downwards. The second cup-shaped component 18 is formed as a bottomed cylindrical portion that surrounds the outer peripheral surface of the second counterweight 15i from the outside.

[0078] (through-flow path 5f)

[0079] like Figure 1 as well as Figure 4 As shown, the rotor 5a has multiple through flow paths 5f that extend axially. The multiple through flow paths 5f are arranged to avoid the contact portion 15f of the first counterweight 15a.

[0080] The opening of the through flow path 5f provided on the heavy portion 15c side of the first counterweight 15a is positioned to avoid facing the contact portion 15f of the first counterweight 15a. Furthermore, the opening of the through flow path 5f provided on the light portion 15b side of the first counterweight 15a is positioned to avoid the contact portion 15f of the first counterweight 15a, that is, to avoid the protrusion 15q of the light portion 15b of the first counterweight 15a.

[0081] (The relationship between the through flow path 5f and surrounding components)

[0082] Multiple through-flow paths 5f are arranged to avoid the location of the second counterweight 15i fixed to the lower end face of the rotor 5a. The bottoms of the first cup-shaped member 17 and the second cup-shaped member 18 have through holes at positions corresponding to the multiple through-flow paths 5f.

[0083] The first cup-shaped component 17 and the second cup-shaped component 18 are preferably non-magnetic materials. Alternatively, the through-flow path 5f may be formed through the second counterweight 15i, or it may be positioned away from the second cup-shaped component 18. Furthermore, multiple through-flow paths 5f are formed symmetrically or point-symmetrically with respect to the central axis of the rotor 5a.

[0084] (Stator 5b)

[0085] Figure 7 This is a cross-sectional view of the stator 5b of the motor 5 of the scroll compressor 100 in Embodiment 1. Figure 7 A cross-section perpendicular to the central axis of stator 5b is shown. The outer peripheral surface of stator 5b of motor 5 is fixed to the sealed container 10 by thermoforming or welding, etc. Figure 7 As shown, a plane 5r parallel to the central axis is formed on a portion of the outer peripheral surface of the stator 5b. In other words, a portion of the cylindrical outer peripheral portion of the stator 5b is cut off through the plane 5r. The second passage 5g is formed by the plane 5r formed on the stator 5b and the inner peripheral surface of the sealed container 10.

[0086] The first passage 4f formed on the outer peripheral surface of the aforementioned guide bracket 4 and the second passage 5g formed on the outer peripheral surface of the stator 5b constitute a refrigerant flow path that guides the refrigerant gas discharged from the outlet 1d of the compression mechanism 14 to the bottom of the sealed container 10.

[0087] (The operation of scroll compressor 100)

[0088] During startup and operation of the scroll compressor 100 in Embodiment 1, refrigerant is drawn in through the suction pipe 13 and enters the compression chamber 1f, which is formed by meshing the plate-shaped vortex teeth 1b of the fixed scroll member 1 and the plate-shaped vortex teeth 2b of the oscillating scroll member 2. The oscillating scroll member 2, driven by the electric motor 5, reduces the volume of the compression chamber 1f through eccentric rotary motion. This compression stroke raises the pressure of the drawn-in refrigerant. Furthermore, during the compression stroke, refrigerant gas at intermediate pressure is guided from the suction port 2g of the oscillating scroll member 2 through the connecting hole 3e of the flexible frame 3 to the lower space 4b of the frame. The lower space 4b of the frame is maintained at an intermediate pressure atmosphere through the suction port 2g and the connecting hole 3e.

[0089] Through the aforementioned compression stroke, a mixture of refrigerant and refrigeration oil is discharged from the outlet 1d of the fixed scroll member 1 into the upper space 10a of the sealed container 10. The mixture passes through a refrigerant flow path formed by a first passage 4f located on the outer periphery of the compression mechanism 14 and a second passage 5g located on the outer periphery of the stator 5b of the motor 5, and is guided to the bottom of the sealed container 10, a space below the motor 5. During this process, the refrigeration oil separates from the mixture as it is guided to the bottom of the sealed container 10.

[0090] The refrigerant gas separated from the refrigeration oil enters the interior of the second cup-shaped component 18 through the opening 18a of the second cup-shaped component 18 mounted on the lower end face of the rotor 5a of the motor 5, and flows into the through flow path 5f provided on the rotor 5a. A portion of the refrigerant gas and refrigeration oil that rises through the through flow path 5f, which corresponds to the separation portion 15g of the first counterweight 15a, collides with the separation portion 15g of the first counterweight 15a. The refrigerant gas and refrigeration oil that collide with the separation portion 15g flow radially outward and are discharged from the outlet 17b to the outside of the first cup-shaped component 17.

[0091] The refrigerant gas, passing through the through-flow path 5f which is not directly opposite the separation section 15g, rises inside the first cup-shaped component 17 and flows into the discharge hood 16. Furthermore, the refrigerant gas passes through the second discharge passage 16a within the discharge hood 16, then through the first discharge passage 4g, and further through the discharge pipe 12 to be released outside the sealed container 10.

[0092] Next, the discharge of refrigerant oil to the outside of the scroll compressor 100 will be explained. When the scroll compressor 100 is running, refrigerant oil is supplied to the bearings and sliding parts. Subsequently, the refrigerant oil circulates together with the refrigerant inside the sealed container 10, returns to the oil reservoir 10b, and is discharged to the outside of the sealed container 10 along with the refrigerant through the discharge pipe 12. If a large amount of refrigerant oil is discharged to the outside of the sealed container 10, the amount of refrigerant oil held in the oil reservoir 10b decreases. If the amount of refrigerant oil in the sealed container 10 decreases, the oil supply to the bearings and sliding parts decreases, eventually leading to oil depletion. This results in abnormal wear or adhesion in the bearings and sliding parts, causing compressor damage.

[0093] In order to reduce the amount of refrigerant oil 11 discharged to the outside of the sealed container 10, the scroll compressor 100 of Embodiment 1 causes the refrigerant and refrigerant oil flowing through the through-flow path 5f of the rotor 5a to collide with the separation portion 15g of the heavy part 15c of the first counterweight 15a and be guided radially outward. The separation portion 15g is formed at a position opposite to the through-flow path 5f. The refrigerant and refrigerant oil that pass through the through-flow path 5f and collide with the separation portion 15g have their flow direction changed and flow outward from the separation portion 15g due to centrifugal force. The side wall 17c of the first cup-shaped member 17 has a discharge port 17b. The discharge port 17b of the first cup-shaped member 17 is provided corresponding to the position on the outer peripheral surface of the first counterweight 15a where the separation portion 15g is provided, and is provided radially opposite to the separation portion 15g.

[0094] The first cup-shaped component 17 surrounds the first counterweight 15a at the upper end of the rotor 5a radially outward and has an opening at the top. However, since a discharge port 17b is provided on the side wall 17c of the first cup-shaped component 17, corresponding to the separation portion 15g, refrigeration oil and refrigerant gas are discharged from the discharge port 17b located on the side wall 17c to the outside of the first cup-shaped component 17.

[0095] The refrigerant gas and refrigeration oil flowing out from the outlet 17b of the first cup-shaped component 17 flow out to the outer side of the opening 16b of the discharge shroud 16, thus preventing them from easily flowing into the opening 16b of the discharge shroud 16. Furthermore, the refrigeration oil flows outward from the outlet 17b, and therefore flows downward into the sealed container 10 together with the refrigerant gas flowing downward from the top of the sealed container 10.

[0096] As described above, in the scroll compressor 100 of Embodiment 1, the refrigerant gas and refrigeration oil mixture compressed by the compression mechanism 14 separates the refrigeration oil 11 during the process of flowing downwards within the sealed container 10 and recirculating back upwards. Therefore, compared to conventional compressors, the scroll compressor 100 of Embodiment 1 significantly reduces the amount of refrigeration oil discharged to the outside of the sealed container 10. Consequently, the amount of refrigeration oil that the scroll compressor 100 can retain by the oil storage section 10b can be increased. Furthermore, a scroll compressor 100 and a refrigeration cycle device 200 with high reliability can be obtained, which suppresses the reduction of oil supply to the bearings and sliding parts within the scroll compressor 100.

[0097] Implementation method 2.

[0098] The scroll compressor 100 of Embodiment 2 will be described. The scroll compressor 100 of Embodiment 2 is a structure in which the construction of the first cup-shaped member 17 is changed compared to Embodiment 1.

[0099] Figure 8 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 2. Figure 8 (a) is a diagram showing the rotor 5a viewed axially. Figure 8 (b) indicates Figure 8 The cross-section of part AA in (a). In Embodiment 2, at least one outlet 17d is added to the sidewall 17c on the side of the lightweight portion 15b of the first counterweight 15a of the first cup-shaped member 17. In Embodiment 1, sometimes the refrigeration oil and the refrigerant gas flowing out from the through flow path 5f which is not opposite to the separation portion 15g of the first counterweight 15a flow together into the opening 16b of the discharge shroud 16. In Embodiment 2, by further providing the outlet 17d in the first cup-shaped member 17, the refrigerant gas and refrigeration oil flowing out from the through flow path 5f disposed on the lightweight portion 15b side are guided to the radially outer side of the first cup-shaped member 17. In addition, the outlet 17d is sometimes referred to as the second outlet.

[0100] In the first cup-shaped member 17 of Embodiment 2, a discharge port 17d is provided on the side of the light portion 15b of the first counterweight 15a and near the boundary between the light portion 15b and the heavy portion 15c. However, the discharge port 17d provided on the side of the light portion 15b is not limited to this position. The discharge port 17d is provided on the portion other than the radially outer side of the separation portion 15g, and the separation portion 15g is not arranged on the imaginary straight line connecting the central axis and the discharge port 17d.

[0101] The scroll compressor 100 of Embodiment 2 can increase the amount of refrigerant oil discharged to the outside of the first cup-shaped member 17 by providing a new discharge port 17d to the first cup-shaped member 17. By discharging refrigerant oil to the outside of the first cup-shaped member 17, the amount of refrigerant oil flowing into the opening 16b of the discharge shroud 16 is reduced, and the scroll compressor 100 can suppress the amount of refrigerant oil discharged to the outside.

[0102] Implementation method 3.

[0103] The scroll compressor 100 of Embodiment 3 will be described. The scroll compressor 100 of Embodiment 3 is a structure in which the construction of the first cup-shaped member 17 and the first counterweight 15a is changed compared to Embodiment 1.

[0104] Figure 9 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 3. Figure 9 (a) is a diagram showing the rotor 5a viewed axially. Figure 9 (b) indicates Figure 9 The cross-section of BB section (a). In Embodiment 3, the scroll compressor 100 also has a radially outward opening separation section 15g in the contact portion 15f of the light portion 15b of the first balance counterweight 15a, similar to the separation section 15g of the heavy portion 15c. Moreover, the through flow path 5f of the rotor 5a is arranged opposite to the separation section 15g provided in the light portion 15b. A discharge port 17b is formed on the side wall 17c of the first cup-shaped member 17 located radially outward of the separation section 15g in the light portion 15b. In addition, the separation section 15g provided in the heavy portion 15c is sometimes referred to as the first separation section 15g, and the separation section 15g provided in the light portion 15b is referred to as the second separation section 15g.

[0105] For the scroll compressor 100, refrigerant gas and refrigeration oil rise upwards from the rotor 5a of the motor 5 through the through-flow path 5f. The refrigerant gas and refrigeration oil rising from the through-flow path 5f, which faces the separation portion 15g of the first counterweight 15a, are discharged to the outside of the first cup-shaped member 17 as described above. In Embodiment 1, the refrigerant gas and refrigeration oil, after passing through the through-flow path 5f on the lightweight section 15b side, flow directly toward the discharge hood 16. However, in Embodiment 3, the through-flow path 5f on the lightweight section 15b side faces the second separation portion 15g. Therefore, the refrigerant gas and refrigeration oil passing through the through-flow path 5f collide with the second separation portion 15g and flow radially outwards. The radially outer side of the second separation portion 15g opens on the outer peripheral surface of the first counterweight 15a, and a discharge port 17b is provided opposite to this opening.

[0106] The second separation section 15g, like the first separation section 15g provided in the heavy section 15c as described in Embodiment 1, changes the flow of refrigerant passing through the through flow path 5f and flows radially outward, flowing radially outward together with the refrigeration oil towards the first cup-shaped member 17. This prevents the refrigeration oil from flowing into the opening 16b of the discharge shroud 16, which is located inside the opening 17a of the first cup-shaped member 17.

[0107] Implementation method 4.

[0108] The scroll compressor 100 of Embodiment 4 will be described. The scroll compressor 100 of Embodiment 4 is a structure in which the construction of the separation section 15g and the discharge port section 17b is changed compared to Embodiment 1.

[0109] Figure 10 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 4. Figure 10 (a) is a diagram showing the rotor 5a viewed axially. Figure 10 (b) indicates Figure 10 The cross-section of section AA of (a). For the first balancing counterweight 15a in Embodiment 4, a separation section 15g is positioned opposite the two through-flow paths 5f of the rotor 5a located on the side of the heavy-duty section 15c. That is, the section formed in... Figure 5 In Embodiment 1 shown, the two separate portions 15g of the heavy part 15c of the first counterweight 15a are connected, changing it into a single separate portion 15g. This is achieved while ensuring the strength of the first counterweight 15a. Figure 10 As shown, by arranging a separation section 15g opposite to multiple through flow paths 5f, the construction of the first balancing counterweight 15a can be simplified.

[0110] Figure 10 The first cup-shaped component 17 shown has a discharge port 17b corresponding to a separation portion 15g provided in the heavy-duty portion 15c. That is, when viewed in the axial direction, the discharge port 17b is arranged on the extension line of the straight line connecting the central axis and the separation portion 15g.

[0111] As described above, the scroll compressor 100 according to embodiment 4 achieves the same effect as embodiment 1, and the construction of the first counterweight 15a and the first cup-shaped component 17 is simplified, thus making it easier to manufacture and reducing costs.

[0112] (Modified Example)

[0113] Figure 11 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4. Figure 11 (a) is a diagram showing the rotor 5a viewed axially. Figure 11 (b) indicates Figure 11 The cross-section of section AA in (a). The first cup-shaped component 17 of the scroll compressor 100 in Embodiment 4 can also be provided with a discharge port 17d near the boundary between the light portion 15b and the heavy portion 15c of the first counterweight 15a, similar to Embodiment 2. With this configuration, the scroll compressor 100 of Embodiment 4 achieves the same effect as that of Embodiment 2.

[0114] Figure 12 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4. Figure 12 (a) is a diagram showing the rotor 5a viewed axially. Figure 12 (b) indicates Figure 12 The cross section of part AA of (a). Figure 12 The first cup-shaped component 17 shown in (a) has a discharge port 17b corresponding to the separation portion 15g formed in the heavy-duty portion 15c, but it may also have discharge port portions 17b corresponding to the two through flow paths 5f respectively. That is, the two discharge port portions 17b may also be configured such that, when viewed in the axial direction, they are arranged on the extension line of the straight line connecting the central axis and the through flow path 5f. Figure 12 The first cup-shaped component 17 shown in (a) has a smaller area for each of its outlet portions 17b, thus enabling it to... Figure 10 (a) and Figure 11 The first cup-shaped component 17 shown in (a) further ensures strength. Furthermore, Figure 12 The first cup-shaped component 17 of (a) has two or more discharge ports 17b formed at a position overlapping with the separation section 15g, which also results in high discharge efficiency of refrigeration oil.

[0115] Figure 13 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 4. Figure 13 (a) is a diagram showing the rotor 5a viewed axially. Figure 13 (b) indicates Figure 13 The cross section of part AA of (a). Figure 13 The first cup-shaped component 17 shown in (a) can also have a discharge port 17d provided on the side of the light portion 15b of the first counterweight 15a and near the boundary between the light portion 15b and the heavy portion 15c, just like in Embodiment 2. With this configuration, the scroll compressor 100 of Embodiment 4 achieves the same effect as in Embodiment 2.

[0116] Implementation method 5.

[0117] The scroll compressor 100 of Embodiment 5 will be described. The scroll compressor 100 of Embodiment 5 is relative to... Figure 9 The structure of the separation section 15g and the discharge port section 17b has been changed in Embodiment 3 shown.

[0118] Figure 14 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 5. Figure 14 (a) is a diagram showing the rotor 5a viewed axially. Figure 14 (b) indicates Figure 14 The cross-section of BB section (a). The scroll compressor 100 of Embodiment 5, like that of Embodiment 3, also has a separation section 15g provided in the lightweight section 15b of the first balance counterweight 15a. The first balance counterweight 15a of Embodiment 5 is configured such that a separation section 15g provided in the lightweight section 15b is opposite to two through flow paths 5f.

[0119] Figure 14 The first cup-shaped component 17 shown has a discharge port 17b on the radially outer side of the separation portion 15g, which is respectively provided in the light-weight portion 15b and the heavy-weight portion 15c. Each discharge port 17b is formed with a width corresponding to the circumferential width of the separation portion 15g. That is, when viewed axially, the discharge port 17b is arranged on the extension line of the straight line connecting the central axis and the separation portion 15g. With this configuration, the efficiency of separating refrigeration oil from the refrigerant flowing out of the through flow path 5f is improved for the first counterweight 15a and the first cup-shaped component 17 of the scroll compressor 100 of Embodiment 5, and a simple structure can be achieved.

[0120] (Modified Example)

[0121] Figure 15 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 5. Figure 15 (a) is a diagram showing the rotor 5a viewed axially. Figure 15 (b) indicates Figure 15 The cross-section of BB section (a). In embodiment 5, the first cup-shaped member 17 can also be configured such that the outlet portion 17b corresponds to one of the plurality of through flow paths 5f. That is, as... Figure 15 As shown in (a), the first cup-shaped component 17 can also be configured with two outlet portions 17b corresponding to a separation portion 15g. In this case, when viewed axially, each of the plurality of outlet portions 17b is arranged on the extension line of the straight line connecting the central axis and each of the plurality of through flow paths 5f.

[0122] Implementation method 6.

[0123] The scroll compressor 100 of Embodiment 6 will be described. The scroll compressor 100 of Embodiment 6 is relative to... Figure 5 The structure of the outlet portion 17b of the first cup-shaped component 17 is changed in Embodiment 1 shown.

[0124] Figure 16 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 6. Figure 16 (a) is a diagram showing the rotor 5a viewed axially. Figure 16 (b) indicates Figure 16 The cross-section of section AA in (a). For the scroll compressor 100 of embodiment 6, although... Figure 5 The first counterweight 15a in Embodiment 1 has the same construction, but the construction of the discharge port 17b of the first cup-shaped member 17 is different. In Embodiment 6, a discharge port 17b is provided relative to the two separate parts 15g provided on the heavy part 15c. This construction can also achieve the same effect as the scroll compressor 100 in Embodiment 1, and simplifies the construction of the first cup-shaped member 17.

[0125] (Modified Example)

[0126] Figure 17 This is an explanatory diagram of the structure of the upper part of the rotor 5a of a modified example of the scroll compressor 100 of Embodiment 6. Figure 17 (a) is a diagram showing the rotor 5a viewed axially. Figure 17 (b) indicates Figure 17 The cross-section of section AA in (a). The first cup-shaped component 17 of the scroll compressor 100 in Embodiment 6 can also be provided with a discharge port 17d near the boundary between the light portion 15b and the heavy portion 15c of the first counterweight 15a, similar to Embodiment 2. With this configuration, the scroll compressor 100 of Embodiment 6 achieves the same effect as that of Embodiment 2.

[0127] Implementation method 7.

[0128] The scroll compressor 100 of Embodiment 7 will be described. The scroll compressor 100 of Embodiment 7 is relative to... Figure 9 The structure of the outlet portion 17b of the first cup-shaped component 17 is changed in Embodiment 3 shown.

[0129] Figure 18 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 7. Figure 18 (a) is a diagram showing the rotor 5a viewed axially. Figure 18 (b) indicates Figure 18The cross-section of BB section (a). For the scroll compressor 100 of embodiment 7, compared to... Figure 9 The first counterweight 15a in Embodiment 3 has the same construction, but the construction of the discharge port 17b of the first cup-shaped member 17 is different. In Embodiment 7, a discharge port 17b is provided relative to the two separate parts 15g provided on the heavy part 15c. Even with this construction, the scroll compressor 100 of Embodiment 7 can achieve the same effect as Embodiment 3, and the construction of the first cup-shaped member 17 can be simplified.

[0130] (Modified Example)

[0131] Figure 18 The first cup-shaped component 17 shown in (a) can also have its outlet portion 17b corresponding to the separation portion 15g of either the light portion 15b or the heavy portion 15c changed to multiple outlet portions 17b. That is, it is also possible to... Figure 18 One of the two outlet portions 17b of the first cup-shaped component 17 in (a) is changed to Figure 15 The multiple discharge outlets 17b shown in (a)

[0132] Implementation method 8.

[0133] The scroll compressor 100 of Embodiment 8 will be described. The scroll compressor 100 of Embodiment 8 is a structure in which the shape of the first balancing counterweight 15a of Embodiment 1 is modified.

[0134] Figure 19 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 8. Figure 19 This is a diagram showing the rotor 5a viewed axially. The scroll compressor 100 of Embodiment 8 is relative to... Figure 5 The shape of the lightweight portion 15b is changed by the first counterweight 15a in Embodiment 1. In Embodiment 8, the lightweight portion 215b of the first counterweight 215a has two arcuate portions 215p that are respectively connected to both ends of the heavy portion 15c. That is, the first counterweight 215a becomes an arcuate shape surrounding the central axis by the heavy portion 15c, which constitutes half a circumference around the central axis, and the arcuate portions 215p, which constitute less than 1 / 4 circumference, respectively connected to its two ends. Figure 19 As shown, in the scroll compressor 100 of embodiment 8, the through flow path 5f provided on the lightweight section 215b side is configured in the part where the arc section 215p is not provided.

[0135] In the scroll compressor 100 of Embodiment 8, the discharge port 17d may be provided on the lightweight portion 215b side of the first cup-shaped member 17, similar to Embodiment 2. Alternatively, the separation portion 15g on the heavy-duty portion 15c side may be changed to be connected to... Figure 10 The illustrated embodiment 4 also corresponds one separation section 15g to multiple through flow paths 5f. The discharge port 17b can also be... Figure 16 Similarly, in Embodiment 6, one discharge port 17b corresponds to multiple separation ports 15g. The same effect as in Embodiment 1 can be obtained in the scroll compressor 100 of Embodiment 8.

[0136] In embodiment 8, the lightweight portion 215b can also be formed with the same thickness and the same inner and outer diameter dimensions as the heavy portion 15c. In this case, the first counterweight 215a becomes an arc shape and is configured such that the center of gravity is eccentric relative to the central axis, which simplifies the construction.

[0137] Implementation method 9.

[0138] The scroll compressor 100 of Embodiment 9 will be described. The scroll compressor 100 of Embodiment 9 is a modification... Figure 14 The structure of the first balancing counterweight 15a in Embodiment 5 shown.

[0139] Figure 20 This is an explanatory diagram of the structure of the upper part of the rotor 5a of the scroll compressor 100 in Embodiment 9. Figure 20 This is a diagram showing the rotor 5a viewed axially. The scroll compressor 100 of Embodiment 9, relative to... Figure 14 The shape of the lightweight portion 15b is changed by the first counterweight 15a of Embodiment 5 shown. The lightweight portion 15b of the first counterweight 315a has two arcuate portions 215p and 315p that are respectively connected to both ends of the heavy portion 15c. That is, the first counterweight 315a becomes an arcuate shape surrounding the central axis by the heavy portion 15c, which constitutes half a circumference around the central axis, and the arcuate portions 215p and 315p that are respectively connected to its two ends.

[0140] like Figure 20 As shown, in the scroll compressor 100 of Embodiment 9, the through flow path 5f provided on the lightweight section 215b side is correspondingly arranged with the separation section 15g provided on the arc section 315p. Furthermore, in Embodiment 9, the arrangement of the separation section 15g and the through flow path 5f can be appropriately changed. That is, a portion of the multiple through flow paths 5f can be arranged below the arc section 315p, and the remaining portion can be arranged below the arc section 215p, with the separation section 15g formed on both the arc sections 315p and 215p. In the scroll compressor 100 of Embodiment 9, the same effects as in the scroll compressor 100 of Embodiment 3 can be obtained.

[0141] In embodiment 9, the two arcuate portions 215p and 315p of the lightweight portion 315b can also be formed with the same thickness and the same inner and outer diameter dimensions as the heavy portion 15c. In this case, the first counterweight 315a becomes arcuate in shape and is configured such that the center of gravity is eccentric relative to the central axis, which simplifies the construction.

[0142] As described above, embodiments 1 to 9 of this disclosure have been presented. However, each embodiment is an example, and the embodiments and their variations can be combined with each other, as well as with other known technologies. Furthermore, some structural modifications may be omitted without departing from the spirit of this disclosure.

[0143] Explanation of reference numerals in the attached figures

[0144] 1... Fixed scroll component; 1a... Platform section; 1b... Plate-shaped vortex teeth; 1c... Euclidean guide groove; 1d... Discharge port; 1e... Suction port; 1f... Compression chamber; 1g... Suction check valve; 2... Oscillating scroll component; 2a... Platform section; 2b... Plate-shaped vortex teeth; 2c... Euclidean guide groove; 2d... Protrusion; 2e... Oscillating bearing; 2f... Thrust surface; 2g... Air extraction port; 2k... Space around the outer periphery of the platform; 2n... Space outside the protrusion; 3... Flexible frame; 3a... Thrust bearing; 3b... Reciprocating sliding surface; 3c... Main bearing; 3d... Auxiliary main bearing; 3e... Connecting hole; 3f... Connecting... Hole; 3g... intermediate pressure adjusting valve; 3h... intermediate pressure adjusting valve press; 3k... intermediate pressure adjusting spring; 3n... intermediate pressure adjusting valve space; 3p... upper cylindrical surface; 3s... lower cylindrical surface; 3t... thrust bearing opening; 4... guide bearing; 4a... upper frame space; 4b... lower frame space; 4c... upper cylindrical surface; 4d... lower cylindrical surface; 4f... first passage; 4g... first discharge passage; 5... motor; 5a... rotor; 5b... stator; 5f... through flow path; 5g... second passage; 5h... shaft fixing hole; 5j... wire; 5r... plane; 6... rotating shaft; 6a... eccentric shaft ; 6b...Main shaft section; 6c...Secondary shaft section; 6d...Oil supply passage; 6e...Oil supply port; 6f...Spinning shaft counterweight; 6g...Fixing section; 6h...Oil supply hole; 7a...Annular seal; 7b...Annular seal; 8...Subframe; 8a...Secondary bearing; 8b...Inlet hole; 9...Euclidean mechanism; 9a...Fixed side key; 9b...Swinging side key; 9c...Annular section of Euler mechanism; 10...Sealed container; 10a...Upper space; 10b...Oil reservoir; 10c...Glass terminal; 11...Refrigeration oil; 12...Discharge pipe; 13...Suction pipe; 14...Compression mechanism section; 15a...First flat 15b... Lightweight part; 15c... Heavyweight part; 15d... Fixing hole; 15f... Contact part; 15g... Separation part; 15h... Fixing member; 15i... Second counterweight; 15k... Inner circumferential surface; 15p... Arc part; 15q... Protrusion; 16... Discharge hood; 16a... Second discharge passage; 16b... Opening; 17... First cup-shaped component; 17a... Opening; 17b... Discharge outlet; 17c... Side wall; 17d... Discharge outlet; 18... Second cup-shaped component; 18a... Opening; 40... Outer circumferential surface; 41... Lower cylindrical part; 52... Upper end face; 53...Lower end face; 100...Scroll compressor; 101...Suction muffler; 103...Four-way switching valve; 104...Outdoor heat exchanger; 105...Pressure regulator; 106...Indoor heat exchanger; 200...Refrigeration cycle unit; 215a...First counterweight; 215b...Lightweight section; 215p...Arc section; 315a...First counterweight; 315b...Lightweight section; 315p...Arc section; D...Inner diameter; d...Inner diameter.

Claims

1. A compressor, characterized in that, have: A sealed container having an oil reservoir for storing refrigeration oil; A compression mechanism, which is disposed inside the sealed container, compresses the refrigerant; An electric motor, disposed within the sealed container, generates driving force; and The rotating shaft transmits the driving force generated by the electric motor to the compression mechanism. The electric motor has the following features: A rotor, which is fixed to the rotating shaft; The stator is fixed to the sealed container and forms a refrigerant flow path that guides the refrigerant gas discharged from the compression mechanism to the lower part of the sealed container. A first counterweight is fixed to the end face of the rotor opposite to the compression mechanism; and The first cup-shaped component has sidewalls surrounding the outer peripheral surface of the first counterweight. The first counterweight is formed by connecting the arc-shaped lightweight part and the arc-shaped heavy part. The first counterweight has a separation portion, which is a recess formed on the end face opposite to the rotor and opens onto the outer peripheral surface of the first counterweight. The separation section is positioned opposite the opening of the through flow path that extends axially through the rotor. The sidewall of the first cup-shaped component has a discharge port, which is located radially outward relative to the separating portion and is radially opposite to the opening of the separating portion. The heavy-duty part and the light-duty part surround the rotating shaft. The separation section includes a first separation section formed in the heavy-duty section. When viewed axially from the rotating shaft, the outlet is located radially outside the first separating portion. When viewed along the axial direction of the rotating shaft, the sidewall of the first cup-shaped component has a second outlet portion in the portion excluding the radially outer side of the first separating portion. When viewed along the axial direction, the separation portion is not positioned on the imaginary straight line connecting the central axis of the rotating shaft and the second outlet.

2. The compressor according to claim 1, characterized in that, The separation section further includes a second separation section formed in the lightweight section. The outlet is located radially outside the second separation section.

3. The compressor according to claim 1 or 2, characterized in that, When viewed along the axial direction, the outlet is positioned on the extension of the straight line connecting the central axis and the through flow path.

4. The compressor according to claim 1 or 2, characterized in that, When viewed along the axial direction, the outlet is positioned on the extension of the straight line connecting the central axis and the separation portion.

5. The compressor according to claim 1 or 2, characterized in that, The through flow path of the rotor includes multiple through flow paths. The separation section is connected to at least one of the plurality of through flow paths.

6. The compressor according to claim 5, characterized in that, The discharge port section includes multiple discharge ports. When viewed axially, the plurality of outlets are respectively arranged on the extension of the straight line connecting the central axis and the plurality of through flow paths.

7. The compressor according to any one of claims 1, 2, and 6, characterized in that, The heavy-duty section is thicker than the light-duty section in the axial direction.

8. The compressor according to any one of claims 1, 2, and 6, characterized in that, When viewed axially, the center of gravity of the first counterweight is eccentric to the side of the heavy part than the center axis.

9. The compressor according to any one of claims 1, 2, and 6, characterized in that, The sidewall of the first cup-shaped component protrudes towards the compression mechanism than the first counterweight.

10. The compressor according to any one of claims 1, 2, and 6, characterized in that, The first counterweight is formed in an annular shape that connects the heavy part and the light part and surrounds the rotation axis.

11. The compressor according to any one of claims 1, 2, and 6, characterized in that, The first counterweight is formed in an arc shape that connects the heavy part and the light part and surrounds the rotation axis.

12. The compressor according to claim 11, characterized in that, The lightweight part has two arcuate portions that connect to both ends of the heavy-duty part.

13. The compressor according to any one of claims 1, 2, 6, and 12, characterized in that, It is equipped with a discharge hood, which is installed on the end face of the compression mechanism opposite to the motor. The discharge hood has an opening opposite to the rotor. When viewed axially along the rotation axis, the opening is located inside the sidewall of the first cup-shaped component.

14. A refrigeration cycle device, characterized in that, The compressor is provided with any one of claims 1 to 13.

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