Compressor and refrigeration cycle device

Abstract

A compressor according to the present invention comprises: a container that constitutes an outer shell and in which an oil reservoir for storing refrigerator oil is formed internally at a lower portion; an electric motor that has a stator which is fixed to the container and in which a stator passage through which a refrigerant passes is formed in a portion of the outer periphery, and a rotor which is disposed to the inside of the stator; a drive shaft that is attached to the rotor of the electric motor and transmits rotational force of the electric motor; a compression mechanism part that rotates in conjunction with rotation of the drive shaft and compresses the refrigerant; a frame that is fixed to a frame fixing part of the container below the electric motor and supports a bearing which supports the drive shaft; and an oil-rising suppression part that is placed on the frame and suppresses rising of refrigerator oil which has passed through the stator passage. The distance between the oil-rising suppression part and a lower end of the stator in the axial direction of the drive shaft is smaller than the distance between the frame fixing part and the oil-rising suppression part in the axial direction.

Description

Compressor and refrigeration cycle device

[0001] The present disclosure relates to a compressor that compresses a refrigerant and a refrigeration cycle device.

[0002] Conventionally, there has been known a compressor that includes a compression mechanism and an electric motor consisting of a rotor and a stator within a sealed container, and that compresses a refrigerant by driving the compression mechanism with the electric motor. Patent Document 1 discloses a scroll compressor in which refrigerant discharged from the compression mechanism into an upper space of the electric motor flows toward a lower space of the electric motor through a core cut formed in the outer peripheral surface of the stator of the electric motor.

[0003] In Patent Document 1, lubricating oil is pumped from an oil reservoir at the bottom of the casing, supplied to each sliding part, then discharged into a space below the motor and returned to the oil reservoir. However, the lubricating oil returning to the oil reservoir at the bottom of the casing may flow through the gap between the rotor and the stator toward the space above the motor due to the swirling flow of gaseous refrigerant caused by the rotation of the rotor of the motor. This can cause the lubricating oil to flow out of the casing along with the refrigerant through the discharge pipe, potentially increasing the oil flow rate. Patent Document 1 attempts to suppress the swirling of gaseous refrigerant by including a first oil separation plate fixed to the upper surface of the support leg between the oil reservoir at the bottom of the casing and the motor, a ring-shaped suppression plate fixed integrally with the first oil separation plate, and a second oil separation plate fixed to the lower surface of the support leg.

[0004] Japanese Patent Application Laid-Open No. 2023-5060

[0005] However, in the compressor of Patent Document 1, the space between the stator and the first oil separation plate is large, so the lubricating oil that flows into the space through the core cut of the stator of the motor is easily affected by the upflow of gaseous refrigerant, and therefore tends to rise through the gap between the rotor and the stator toward the space above the motor.

[0006] The present disclosure has been made to solve the above-mentioned problems, and provides a compressor and a refrigeration cycle device in which refrigeration oil is less likely to rise due to the swirling flow of the refrigerant and is less likely to be affected by the swirling flow.

[0007] The compressor according to the present disclosure comprises: a container forming an outer shell and having an oil reservoir formed at the bottom inside for storing refrigeration oil; a stator fixed to the container and having a stator passage formed on part of its outer periphery through which refrigerant passes; an electric motor having a rotor disposed within the stator; a drive shaft attached to the rotor of the electric motor and transmitting the rotational force of the electric motor; a compression mechanism that rotates with the rotation of the drive shaft to compress the refrigerant; a frame fixed to a frame fixing part of the container below the electric motor and supporting a bearing that supports the drive shaft; and an oil rise suppression part mounted on the frame and suppressing the refrigeration oil that has passed through the stator passage from rising, wherein the distance in the axial direction of the drive shaft between the lower end of the stator and the oil rise suppression part is smaller than the distance in the axial direction between the oil rise suppression part and the frame fixing part.

[0008] According to the present disclosure, the distance between the lower end of the stator and the oil rise suppression unit in the axial direction of the drive shaft is smaller than the distance between the oil rise suppression unit and the frame fixing unit in the axial direction. This reduces the space in which refrigeration oil is subjected to the swirling flow generated by the rotor rotation. This reduces the oil rise caused by the swirling flow of refrigeration oil that has passed through the stator passage. This also reduces the oil reservoir between the oil rise suppression unit and the bottom of the container. This increases the amount of refrigeration oil that is less susceptible to the swirling flow generated by the rotor rotation.

[0009] FIG. 1 is a circuit diagram showing a refrigeration cycle device according to embodiment 1 of the present disclosure. FIG. 2 is an axial cross-sectional view showing a compressor according to embodiment 1 of the present disclosure. FIG. 3 is a circumferential cross-sectional view showing a guide frame according to embodiment 1 of the present disclosure. FIG. 4 is an axial cross-sectional view showing a rotor according to embodiment 1 of the present disclosure. FIG. 5 is a circumferential cross-sectional view showing a rotor according to embodiment 1 of the present disclosure. FIG. 6 is a circumferential cross-sectional view showing a stator according to embodiment 1 of the present disclosure. FIG. 7 is an enlarged view of an axial cross-sectional view showing a compressor according to embodiment 1 of the present disclosure. FIG. 8 is a perspective view showing a subframe and an oil-leakage suppression unit according to embodiment 1 of the present disclosure. FIG. 9 is a top view showing the subframe and the oil-leakage suppression unit according to embodiment 1 of the present disclosure. FIG. 10 is a bottom view showing the subframe and the oil-leakage suppression unit according to embodiment 1 of the present disclosure.

[0010] Hereinafter, embodiments of a compressor and a refrigeration cycle apparatus according to the present disclosure will be described with reference to the drawings. Note that the present disclosure is not limited to the embodiments described below. Furthermore, in the following drawings, including FIG. 1, the dimensional relationships between components may differ from the actual ones. Furthermore, in the following description, terms indicating directions are used as appropriate to facilitate understanding of the present disclosure. However, these terms are for the purpose of explaining the present disclosure and do not limit the present disclosure. Examples of terms indicating directions include "up," "down," "right," "left," "front," and "rear."

[0011] Embodiment 1. Fig. 1 is a circuit diagram showing a refrigeration cycle apparatus 200 according to Embodiment 1. The refrigeration cycle apparatus 200 is an apparatus for conditioning air in an indoor space, and as shown in Fig. 1, includes an outdoor unit 201 and an indoor unit 202. The outdoor unit 201 includes, for example, a compressor 100, a flow path switching device 103, an outdoor heat exchanger 104, an outdoor fan 104a, and an expansion section 105. The indoor unit 202 includes, for example, an indoor heat exchanger 106 and an indoor fan 106a. In Embodiment 1, the refrigeration cycle apparatus 200 is illustrated as an air-conditioning apparatus, but may also be various types of industrial machinery such as a refrigerator, a freezer, a refrigeration unit, or a water heater.

[0012] The compressor 100, the flow path switching device 103, the outdoor heat exchanger 104, the expansion section 105, and the indoor heat exchanger 106 are connected by piping 204 to form a refrigerant circuit 203. The compressor 100 draws in low-temperature, low-pressure refrigerant from the suction muffler 101, compresses the drawn refrigerant, and discharges it into high-temperature, high-pressure refrigerant. The compressor 100 is, for example, a capacity-controllable inverter compressor or a scroll compressor. The flow path switching device 103 is, for example, a four-way valve, and switches the direction in which the refrigerant flows in the refrigerant circuit 203.

[0013] The outdoor heat exchanger 104 exchanges heat between, for example, outdoor air and a refrigerant. The outdoor heat exchanger 104 functions as a condenser during cooling operation and as an evaporator during heating operation. The expansion unit 105 is a pressure reducing valve or an expansion valve that reduces the pressure of the refrigerant to expand it. The expansion unit 105 is, for example, an electronic expansion valve whose opening is adjustable.

[0014] The indoor heat exchanger 106 exchanges heat between, for example, indoor air and a refrigerant. The indoor heat exchanger 106 acts as an evaporator during cooling operation and as a condenser during heating operation. The indoor fan 106a is a device that sends indoor air to the indoor heat exchanger 106.

[0015] (Operation Modes, Heating Operation) Next, the operation modes of the refrigeration cycle apparatus 200 will be described. First, the heating operation will be described. In the heating operation, the flow path switching device 103 is connected to the dashed line side in FIG. 1 , and the refrigerant flows along the dashed arrows. In the heating operation, the refrigerant drawn into the compressor 100 is compressed by the compressor 100 and discharged in a high-temperature, high-pressure gas state. The high-temperature, high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 103 and flows into the indoor heat exchanger 106, which functions as a condenser. Then, in the indoor heat exchanger 106, the refrigerant exchanges heat with indoor air sent by the indoor blower 106a, condensing and liquefying. At this time, the indoor air is heated, and heating is performed in the room.

[0016] The gaseous refrigerant returns to the compressor 100, while the liquid refrigerant flows to the expansion section 105. The liquid refrigerant flows into the expansion section 105, where it expands and is decompressed to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant. The two-phase gas-liquid refrigerant then flows into the outdoor heat exchanger 104, which functions as an evaporator, where it exchanges heat with outdoor air sent by the outdoor blower 104a, evaporating and gasifying. The evaporated low-temperature, low-pressure gaseous refrigerant passes through the flow path switching device 103 and is drawn into the compressor 100.

[0017] (Operation Mode, Cooling Operation) Next, the cooling operation will be described. In cooling operation, the flow path switching device 103 is connected to the solid line side in FIG. 1 , and the refrigerant flows along the solid arrows. In cooling operation, the refrigerant is drawn into the compressor 100, compressed by the compressor 100, and discharged in a high-temperature, high-pressure gas state. The high-temperature, high-pressure gas refrigerant discharged from the compressor 100 passes through the flow path switching device 103 and flows into the outdoor heat exchanger 104, which functions as a condenser. In the outdoor heat exchanger 104, the refrigerant exchanges heat with outdoor air sent by the outdoor blower 104a, condensing and liquefying it. The condensed liquid refrigerant flows into the expansion section 105, where it expands and decompresses to become a low-temperature, low-pressure, two-phase gas-liquid refrigerant.

[0018] The gaseous refrigerant returns to the compressor 100, while the liquid refrigerant flows toward the indoor heat exchanger 106. The liquid refrigerant then flows into the indoor heat exchanger 106, which functions as an evaporator, where it exchanges heat with indoor air sent by the indoor blower 106a, evaporating and gasifying. At this time, the indoor air is cooled, and cooling is performed inside the room. The evaporated low-temperature, low-pressure gaseous refrigerant passes through the flow switching device 103 and is drawn into the compressor 100.

[0019] The refrigeration cycle apparatus 200 does not necessarily have to include the flow path switching device 103. In this case, the refrigeration cycle apparatus 200 becomes a dedicated heating or cooling machine. Examples of the refrigerant include a fluorine-based refrigerant or a hydrocarbon-based refrigerant with a low global warming potential (GWP). Examples of the refrigerant include a single refrigerant selected from R1234yf, R1234ze, R32, and R290, a mixed refrigerant of two or more of these, a mixed refrigerant of any of these with another refrigerant, a mixed refrigerant containing R1132(E), and a mixed refrigerant containing R1123. Further, examples of the refrigerant include mixed refrigerants of R516A, R445A, R444A, R454C, R444B, R454A, R455A, R457A, R459B, R452B, R454B, R447B, R447A, R446A, and R459A.

[0020] 2 is an axial cross-sectional view showing the compressor 100 according to the first embodiment of the present disclosure. Next, the compressor 100 will be described in detail. The compressor 100 is, for example, a sealed, vertically mounted scroll compressor that draws in and compresses refrigerant circulating through a refrigerant circuit 203, and discharges the refrigerant at a high temperature and high pressure. As shown in FIG. 2 , the compressor 100 includes a container 10, a compression mechanism 14, an electric motor 5, and a drive shaft 6.

[0021] The container 10 is a sealed member that constitutes the outer shell of the compressor 100. The container 10 has a cylindrical body 10e with an open top, an upper lid 10d that covers the upper surface of the body 10e, and a lower lid 10f that covers the lower surface of the body 10e. The upper end of the body 10e is joined to the upper lid 10d by welding, and the lower end of the body 10e is also joined to the lower lid 10f by welding. The body 10e and the upper lid 10d do not have to be separate members, but may be integrally formed from a plate-like member by deep drawing or spinning. The body 10e and the upper lid 10d constitute a main container portion 10g.

[0022] The container 10 accommodates the compression mechanism 14, the electric motor 5, and the drive shaft 6 and is pressure-resistant. The compression mechanism 14 is provided in the upper part of the container 10, and the electric motor 5 is provided in the lower part of the container 10. The lower part of the interior of the container 10 forms an oil reservoir 10b in which refrigerating machine oil 11 is stored. The oil reservoir 10b is a portion that stores the refrigerating machine oil 11. Here, the refrigerating machine oil 11 is an oil that lubricates the sliding parts of the components that make up the compression mechanism 14 and also assists in smooth refrigerant compression by sealing the compression mechanism 14.

[0023] The compression mechanism 14 compresses the refrigerant drawn into the container 10 through the suction pipe 13 and includes a fixed scroll 1 and an orbiting scroll 2. The compression mechanism 14 is located in the upper part of the container 10. The fixed scroll 1 is fixed to a guide frame 4 supported by the container 10 above the orbiting scroll 2 with bolts (not shown) or the like, and includes a fixed base plate 1a and a fixed scroll 1b. The fixed base plate 1a is a plate-shaped member and forms the upper surface of the compression mechanism 14. An inlet port 1e is formed on the outer periphery of the fixed base plate 1a, through which low-temperature, low-pressure refrigerant is drawn. A discharge port 1d is formed in the center of the fixed base plate 1a, through which compressed, high-pressure refrigerant is discharged. When the compressed, high-pressure refrigerant is discharged from the discharge port 1d, it is discharged into an upper space 10a within the container 10. The fixed scroll 1b is a spiral-shaped protrusion extending downward from the underside of the fixed base plate 1a. The orbiting scroll 2 has a oscillating base plate 2a and an orbiting scroll 2b. The oscillating base plate 2a is a plate-shaped member disposed above the drive shaft 6. The orbiting scroll 2b is a spiral-shaped protrusion extending upward from the upper surface of the oscillating base plate 2a.

[0024] The fixed scroll 1 and the orbiting scroll 2 are arranged so that the fixed scroll 1b and the orbiting scroll 2b face each other. The fixed scroll 1b and the orbiting scroll 2b are combined together, and a compression chamber 1f is formed between the fixed scroll 1b and the orbiting scroll 2b. The fixed scroll 1b and the fixed base plate 1a form suction volumes on the inward and outward facing sides of the orbiting scroll 2.

[0025] A pair of fixed-side Oldham ring grooves 1c are formed in a straight line on the outer periphery of the fixed scroll 1. A pair of fixed-side keys 9a of an Oldham ring 9 are installed in the fixed-side Oldham ring groove 1c so that they can slide back and forth. A cylindrical boss portion 2d is formed on the underside of the swing base plate 2a of the swing scroll 2. A swing bearing 2e is provided on the inner surface of the boss portion 2d. An eccentric shaft portion 6a of the drive shaft 6 is inserted into the swing bearing 2e, and the swing scroll 2 revolves as the eccentric shaft portion 6a rotates.

[0026] The surface of the orbiting base plate 2a of the orbiting scroll 2 on which the boss portion 2d is formed is formed with a thrust surface 2f that can slide against the thrust bearing 3a of the compliant frame 3. In addition, a pair of orbiting-side Oldham ring grooves 2c are formed in a straight line on the outer periphery of the orbiting scroll 2. The orbiting-side Oldham ring groove 2c has a phase difference of approximately 90 degrees with respect to the fixed-side Oldham ring groove 1c, and a pair of orbiting-side keys 9b of the Oldham ring 9 are provided therein so as to be reciprocally slidable.

[0027] A thrust surface 2f that slides and presses against the thrust bearing 3a of the compliant frame 3 is formed on the surface of the oscillating base plate 2a opposite the oscillating scroll 2b. A bleed hole 2g is formed in the oscillating base plate 2a, penetrating the compression chamber 1f to connect the thrust surface 2f. A portion of the refrigerant being compressed in the compression chamber 1f is guided to the thrust surface 2f through the bleed hole 2g.

[0028] The Oldham ring 9 has an annular Oldham ring portion 9c, a pair of fixed side keys 9a provided on the Oldham ring portion 9c, and a pair of swing side keys 9b provided on the Oldham ring portion 9c.

[0029] FIG. 3 is a circumferential cross-sectional view showing the guide frame 4 according to the first embodiment of the present disclosure. The guide frame 4 is attached to the container 10 at an upper portion within the container 10. The outer circumferential surface of the guide frame 4 is fixed to the container 10 by shrink fitting, welding, or the like. The inner circumferential portion of the guide frame 4 is formed with an upper guide upper cylindrical surface 4c and a lower guide cylindrical surface 4d below the upper guide upper cylindrical surface 4c. As shown in FIG. 3, a cutout first passage 4f is formed in the outer circumferential portions of the guide frame 4 and the fixed scroll 1. The refrigerant discharged from the discharge port 1d into the upper space 10a of the container 10 flows downward within the container 10 through the first passage 4f.

[0030] The compliant frame 3 is housed within the guide frame 4. The outer periphery of the compliant frame 3 is formed with a compliant upper cylindrical surface 3p that engages with the guide upper cylindrical surface 4c and a compliant lower cylindrical surface 3s that engages with the guide lower cylindrical surface 4d. The compliant frame 3 is radially supported within the guide frame 4 by the engagement of the guide upper cylindrical surface 4c with the compliant upper cylindrical surface 3p, and the guide lower cylindrical surface 4d with the compliant lower cylindrical surface 3s. Furthermore, a main bearing 3c and an auxiliary main bearing 3d are provided at the center of the compliant lower cylindrical surface 3s of the compliant frame 3, radially supporting a drive shaft 6 that is driven to rotate by a rotor 5a of an electric motor 5. A communication hole 3e is formed in the outer periphery of the compliant frame 3, penetrating in the axial direction from the thrust bearing 3a. A thrust bearing opening 3t, which is the upper end of the communication hole 3e, faces an air bleed hole 2g that penetrates the oscillating bed plate 2a.

[0031] A reciprocating sliding surface 3b is formed on the outer periphery of the thrust bearing 3a of the compliant frame 3, against which the Oldham annular portion 9c of the Oldham ring 9 slides reciprocatingly. A base plate outer periphery space 2k, which is the outer periphery of the oscillating base plate 2a, and a frame upper space 4a, which is the upper portion of the main frame, are connected by a communication hole 3f. The communication hole 3f is formed to communicate with the inside of the Oldham annular portion 9c. An intermediate pressure adjustment valve space 3n formed in the compliant frame 3 is provided with an intermediate pressure adjustment valve 3g, an intermediate pressure adjustment valve holder 3h, and an intermediate pressure adjustment spring 3k. The intermediate pressure adjustment valve 3g is provided between the frame upper space 4a and the boss outer space 2n, which is outside the boss portion 2d, and adjusts the pressure in the boss outer space 2n. The intermediate pressure adjustment valve holder 3h holds down the intermediate pressure adjustment valve 3g. The intermediate pressure adjustment spring 3k biases the intermediate pressure adjustment valve 3g and is stored in a state shortened from its natural length.

[0032] In the first embodiment, the compliant frame 3 and the guide frame 4 are separate bodies, but the compliant frame 3 and the guide frame 4 may be configured as an integrated body.

[0033] The frame underspace 4b, formed between the inner surface of the guide frame 4 and the outer surface of the compliant frame 3, is partitioned above by an upper ring-shaped seal 7a and below by a lower ring-shaped seal 7b. Both the upper ring-shaped seal 7a and the lower ring-shaped seal 7b are housed in seal grooves formed in the inner peripheral surface of the guide frame 4. The seal grooves may also be formed in the outer peripheral surface of the compliant frame 3. The frame underspace 4b communicates only with the communication hole 3e of the compliant frame 3, and is filled with refrigerant in the process of being compressed and supplied from the bleed hole 2g. A base plate outer peripheral space 2k, which is the outer peripheral portion of the thrust bearing 3a and is surrounded above and below by the oscillating base plate 2a and the compliant frame 3, is a low-pressure space of the intake gas atmosphere (suction pressure).

[0034] A discharge pipe 12 is provided on the side of the container 10, discharging high-pressure refrigerant to the outside. The first passage 4f of the guide frame 4 is provided on the side opposite the side on which the discharge pipe 12 is provided. The guide frame 4 is provided with a first discharge passage 4g, which communicates from the center of the lower end to the side. The first discharge passage 4g is connected to the discharge pipe 12. A discharge cover 16, which has a cover opening 16b, is provided on the lower end of the guide frame 4, surrounding the portion on which the guide lower cylindrical surface 4d is formed. A second discharge passage 16a within the discharge cover 16 is connected to the first discharge passage 4g. A suction pipe 13, through which refrigerant is drawn into the container 10, is connected to the side of the container 10. A suction check valve 1g and a spring are provided inside the suction pipe 13. The suction check valve 1g is biased by the spring in a direction to close the suction pipe 13. This prevents refrigerant from backflowing from the suction pipe 13 to the outside of the container 10.

[0035] The electric motor 5 rotates the drive shaft 6, has a variable rotation speed, and generates a rotational force. The electric motor 5 is provided at the bottom inside the container 10. The electric motor 5 has a rotor 5a and a stator 5b. The rotor 5a is fixed to the drive shaft 6 by shrink fitting or the like, and is driven to rotate by passing electricity through the stator 5b, thereby rotating the drive shaft 6. A gap 60 is formed between the stator 5b and the rotor 5a.

[0036] The upper end of the drive shaft 6 is an eccentric shaft portion 6a that rotatably engages with the swing bearing 2e of the swing scroll 2. A main shaft balance weight 6f is shrink-fitted to the lower side of the eccentric shaft portion 6a. The lower side of the eccentric shaft portion 6a of the drive shaft 6 is a main shaft portion 6b that rotatably engages with the main bearing 3c and auxiliary main bearing 3d of the compliant frame 3. The lower end of the drive shaft 6 is a counter shaft portion 6c that rotatably engages with the counter bearing 8a of the sub-frame 8. A rotor 5a is shrink-fitted between the main shaft portion 6b and the counter shaft portion 6c.

[0037] An oil supply passage 6d is formed inside the drive shaft 6 and extends axially therethrough, and a shaft oil supply port 6e at the lower end of the oil supply passage 6d is immersed in refrigerating machine oil 11 stored at the bottom of a container 10. Refrigerating machine oil 11 is then pumped up by an oil supply mechanism (not shown) or a pump mechanism (not shown) provided at the bottom of the drive shaft 6. The upper end of the oil supply passage 6d opens at the boss portion 2d of the orbiting scroll 2, and the pumped-up refrigerating machine oil 11 flows from the opening at the upper end of the oil supply passage 6d to the orbiting bearing 2e, lubricating the eccentric shaft portion 6a and the orbiting bearing 2e. An oil supply hole 6g branching radially is formed in the oil supply passage 6d, and refrigerating machine oil 11 flows through the oil supply hole 6g to the auxiliary main bearing 3d, lubricating the auxiliary main bearing 3d and the main bearing 3c.

[0038] A first balance weight 15a is provided on the upper end surface of the rotor 5a, and a second balance weight 15b is provided on the lower end surface of the rotor 5a. The second balance weight 15b corresponds to the balance weight in the present disclosure. The first balance weight 15a and the second balance weight 15b are fixed at diagonally opposite eccentric positions. As described above, the main shaft balance weight 6f is fixed to the drive shaft 6 below the eccentric shaft portion 6a inside the boss outer space 2n. The main shaft balance weight 6f, the first balance weight 15a, and the second balance weight 15b offset the imbalance between the centrifugal force and the moment force generated when the orbiting scroll 2 oscillates via the eccentric shaft portion 6a of the drive shaft 6. This achieves static and dynamic balance.

[0039] A first cup-shaped member 17 containing a first balance weight 15a is fixed to the upper end surface of the rotor 5a, and a second cup-shaped member 18 containing a second balance weight 15b is fixed to the lower end surface of the rotor 5a. The first cup-shaped member 17 has a first cup opening 17a at its upper part facing the cover opening 16b of the discharge cover 16. The second cup-shaped member 18 is attached with its second cup opening 18a facing downward. The first cup-shaped member 17 and the second cup-shaped member 18 are preferably made of non-magnetic material.

[0040] FIG. 4 is an axial cross-sectional view of the rotor 5a according to the first embodiment of the present disclosure, and FIG. 5 is a circumferential cross-sectional view of the rotor 5a according to the first embodiment of the present disclosure. As shown in FIGS. 4 and 5 , the rotor 5a is formed with a plurality of through-flow passages 5f penetrating therethrough in the axial direction. As shown in FIG. 1 , the through-flow passages 5f are formed by penetrating the bottoms of the first cup-shaped member 17 and the second cup-shaped member 18 while avoiding the installation positions of the first balance weight 15a and the second balance weight 15b. Note that the through-flow passages 5f may be formed by penetrating the first balance weight 15a and the second balance weight 15b, or may be formed by avoiding the installation positions of the first cup-shaped member 17 and the second cup-shaped member 18. Here, the plurality of through-flow passages 5f are formed in line-symmetric or point-symmetric positions with respect to the axis.

[0041] 6 is a circumferential cross-sectional view showing a stator 5b according to the first embodiment of the present disclosure. As shown in FIG. 6, the outer peripheral surface of the stator 5b is fixed to the container 10 by shrink fitting, welding, or the like. A stator passage 5g is formed between the stator 5b and the container 10 in a portion of the outer periphery of the stator 5b. The stator passage 5g is formed over the entire axial length of the stator 5b. The first passage 4f of the guide frame 4 and the stator passage 5g of the stator 5b form a refrigerant flow path 30 that guides the gaseous refrigerant discharged from the discharge port 1d to the bottom of the container 10.

[0042] FIG. 7 is an enlarged axial cross-sectional view of the compressor 100 according to the first embodiment of the present disclosure. As shown in FIG. 7 , the subframe 8 is fixed to a frame fixing portion 8e of the container 10 and supports the countershaft portion 6c of the drive shaft 6. The subframe 8 corresponds to the frame in the present disclosure. The frame fixing portion 8e is, for example, a welded portion. The subframe 8 includes a support portion 8b that supports a counterbearing 8a that supports the countershaft portion 6c, and a plurality of fixing legs 8c that extend radially from the support portion 8b and are fixed to the frame fixing portion 8e. The fixing legs 8c correspond to the bearings in the present disclosure. The support portion 8b is located on the inner periphery and has a cylindrical shape extending in the height direction. The fixing legs 8c extend radially from the lower portion of the support portion 8b. The radially outer ends of the fixing legs 8c extend upward, and their end faces are fixed to the frame fixing portion 8e of the body portion 10e of the container 10 by welding or the like. An oil leakage suppressing portion 8d is placed on the upper surface of the support portion 8b. Here, the axis of the drive shaft 6 is denoted by O.

[0043] Figure 8 is a perspective view showing the subframe 8 and the oil-leakage suppression portion 8d according to the first embodiment of the present disclosure. As shown in Figure 8, three fixing legs 8c are provided at equal intervals in the circumferential direction of the subframe 8. Note that the number of fixing legs 8c is not limited to three, and may be two, four or more, as long as a plurality of fixing legs are provided.

[0044] 7 and 8, the oil-leakage suppression unit 8d is placed on the upper surface of the support portion 8b of the subframe 8. The oil-leakage suppression unit 8d suppresses the refrigeration oil 11 that has passed through the stator passage 5g from rising, and has a circular, plate-like outer shape. The oil-leakage suppression unit 8d has a partition wall portion 8db facing the subframe 8, which is placed on the support portion 8b of the subframe 8 and has an insertion hole 8dc formed therein. A through-hole 8da, into which the drive shaft 6 is inserted, is formed in the center of the partition wall portion 8db.

[0045] FIG. 9 is a top view showing the subframe 8 and the oil-leakage suppression portion 8d according to the first embodiment of the present disclosure, and FIG. 10 is a bottom view showing the subframe 8 and the oil-leakage suppression portion 8d according to the first embodiment of the present disclosure. As shown in FIGS. 9 and 10 , the insertion holes 8dc are formed in positions facing the gap 60 formed between the stator 5b and the rotor 5a, and are arc-shaped with the center of the partition wall portion 8db as the center. In the first embodiment, three insertion holes 8dc are formed, but two or less, or four or more, may be formed. Furthermore, the insertion holes 8dc are formed in positions facing each other between the fixing legs 8c.

[0046] 1 and 7, the distance L1 between the lower end of the stator 5b and the oil leakage suppressing portion 8d in the axial direction of the drive shaft 6 is smaller than the distance L2 between the oil leakage suppressing portion 8d and the frame fixing portion 8e in the axial direction. In addition, the lower end of the stator 5b is located lower than the lower end of the second balance weight 15b.

[0047] The material of the oil leakage suppression portion 8d is, for example, SPCC material (iron), but resin may also be used. A space of, for example, about 2.9 mm is provided between the outer diameter of the oil leakage suppression portion 8d and the inner circumferential surface of the container 10. The space is at least 1.4 mm. The width of the arc-shaped insertion hole 8dc is, for example, 4 mm. Furthermore, the distance between the oil leakage suppression portion 8d and the winding portion of the stator 5b must be 2.5 mm in accordance with the Den-An Act. In the first embodiment, this distance is 4 mm, but the median is 4.3 mm, making it at least 2.8 mm. Since the motor 5 has a distributed winding configuration, the lower end of the stator 5b is located lower than the lower end of the rotor 5a.

[0048] According to the first embodiment, the distance between the lower end of the stator 5b and the oil-leakage suppressing portion 8d in the axial direction of the drive shaft 6 is smaller than the distance between the oil-leakage suppressing portion 8d and the frame fixing portion 8e in the axial direction. This reduces the space in which the refrigerating oil 11 receives the swirling flow generated by the rotation of the rotor 5a. This reduces the amount of oil that bubbles up due to the swirling flow generated by the refrigerating oil 11 passing through the stator passage 5g. This prevents the refrigerating oil 11 from foaming and rising due to the swirling flow. This means that the refrigerating oil 11 that flows below the stator 5b through the stator passage 5g from flowing upward through the gap 60 formed between the rotor 5a and the stator 5b due to the swirling flow.

[0049] The space where the swirl flow of refrigerating machine oil 11 is received is the space surrounded by drive shaft 6, rotor 5a, stator 5b, and oil-flight suppression unit 8d. In compressor 100 using a refrigerant that dissolves well in refrigerating machine oil, if the temperature of refrigerating machine oil 11 stored in oil reservoir 10b of container 10 is low, a large amount of refrigerant dissolves in refrigerating machine oil 11. At this time, when compressor 100 starts, the refrigerant rapidly evaporates, causing refrigerating machine oil 11 to foam, and the oil level of refrigerating machine oil 11 drops. This phenomenon is called oil foaming, and it can cause poor lubrication due to insufficient oil supply to compressor 100.

[0050] A conventional compressor has been known that has a first oil separation plate fixed to the upper surface of a support leg between an oil reservoir at the bottom of the casing and the electric motor, a ring-shaped suppression part fixed integrally with the first oil separation plate, and a second oil separation plate fixed to the lower surface of the support leg. In this case, the space in the oil reservoir formed by the first oil separation plate and the bottom of the casing is small, so the amount of lubricating oil that is not easily affected by the swirling flow generated by the rotation of the rotor is small.

[0051] In contrast, in the first embodiment, the distance between the lower end of the stator 5b and the oil leakage suppressing portion 8d in the axial direction of the drive shaft 6 is shorter than the distance between the oil leakage suppressing portion 8d and the frame fixing portion 8e in the axial direction. This makes it possible to enlarge the oil reservoir portion 10b between the oil leakage suppressing portion 8d and the bottom of the container 10. This makes it possible to increase the amount of refrigeration oil 11, which is less susceptible to the swirling flow generated by the rotation of the rotor 5a.

[0052] The outer periphery of the oil-leakage suppressing portion 8d is circular, so that the distance between the outer periphery of the oil-leakage suppressing portion 8d and the container 10 can be made uniform around the entire circumference of the container 10. Therefore, the balance between the effect of suppressing the swirl-up of gaseous refrigerant and the effect of returning refrigeration oil 11 from the space above the oil-leakage suppressing portion 8d to the oil reservoir 10b can be made uniform around the entire circumference of the container 10.

[0053] The oil leakage suppression unit 8d has an insertion hole 8dc formed at a position facing the gap 60 and a partition wall portion 8db facing the subframe 8. As described above, the container 10 has a container main portion 10g having a body portion 10e and an upper cover portion 10d, and a lower cover portion 10f fixed to the container main portion 10g. When assembling the compressor 100, a rod-shaped jig is inserted into the insertion hole 8dc of the oil leakage suppression unit 8d with the subframe 8, to which the compression mechanism unit 14, the electric motor 5, and the oil leakage suppression unit 8d are fixed, inserted into the container main portion 10g. The rod-shaped jig is then inserted into the gap 60 formed between the rotor 5a and the stator 5b. This makes it possible to check whether the gap 60 between the rotor 5a and the stator 5b is properly secured with the subframe 8, to which the oil leakage suppression unit 8d is fixed, attached. Furthermore, the partition wall portion 8db can suppress the swirl-up of gaseous refrigerant when the compressor 100 is in operation.

[0054] The insertion holes 8dc are formed at positions facing each other between the fixed legs 8c. This allows a rod-shaped jig to be inserted into the insertion holes 8dc at a position corresponding to the gap between each of the fixed legs 8c. Therefore, with the subframe 8 to which the oil leakage suppression unit 8d is fixed attached, it can be confirmed whether the gap 60 between the rotor 5a and the stator 5b is properly secured.

[0055] The insertion hole 8dc has an arc shape centered on the center of the partition wall portion 8db. Therefore, a rod-shaped jig can be inserted into the gap 60 between the rotor 5a and the stator 5b through the insertion hole 8dc and then slid along the arc-shaped insertion hole 8dc. Therefore, with the subframe 8 to which the oil leakage prevention portion 8d is fixed attached, it can be confirmed whether the gap 60 between the rotor 5a and the stator 5b is properly secured.

[0056] 1 Fixed scroll, 1a Fixed base plate, 1b Fixed scroll, 1c Fixed side Oldham ring groove, 1d Discharge port, 1e Suction port, 1f Compression chamber, 1g Suction check valve, 2 Oscillating scroll, 2a Oscillating base plate, 2b Oscillating scroll, 2c Oscillating side Oldham ring groove, 2d Boss portion, 2e Oscillating bearing, 2f Thrust surface, 2g Bleed hole, 2k Base plate outer peripheral space, 2n Boss portion outer space, 3 Compliant frame, 3a Thrust bearing, 3b Reciprocating sliding surface, 3c Main bearing, 3d Auxiliary main bearing, 3e Communicating hole, 3f Communicating hole, 3g Intermediate pressure regulating valve, 3h Intermediate pressure regulating valve holder, 3k Intermediate pressure regulating spring, 3n Intermediate pressure regulating valve space, 3p Compliant upper cylindrical surface, 3s Compliant lower cylindrical surface, 3t Thrust bearing opening, 4 Guide frame, 4a frame upper space, 4b frame lower space, 4c guide upper cylindrical surface, 4d guide lower cylindrical surface, 4f first passage, 4g first discharge passage, 5 electric motor, 5a rotor, 5b stator, 5f through passage, 5g stator passage, 5h lead wire, 6 drive shaft, 6a eccentric shaft portion, 6b main shaft portion, 6c counter shaft portion, 6d oil supply passage, 6e shaft oil supply port, 6f main shaft balance weight, 6g oil supply hole, 7a upper ring-shaped seal material, 7b lower ring-shaped seal material, 8 subframe, 8a counter bearing, 8b support portion, 8c fixed leg portion, 8d oil rise suppression portion, 8da through hole, 8db partition portion, 8dc insertion hole, 8e frame fixed portion, 9 Oldham ring, 9a fixed side key, 9b swing side key, 9c Oldham annular portion, 10 container, 10a upper space, 10b oil reservoir portion, 10c glass terminal, 10d upper cover portion, 10e body portion, 10f lower cover portion, 10g container main portion, 11 refrigerating machine oil, 12 discharge pipe, 13 suction pipe, 14 compression mechanism portion, 15a first balance weight, 15b second balance weight, 16 discharge cover, 16a second discharge passage, 16b cover opening, 17 first cup-shaped member, 17a first cup opening, 18 second cup-shaped member, 18a second cup opening, 30 refrigerant flow path, 60 gap, 100 compressor, 101 suction muffler, 103 flow path switching device, 104 outdoor heat exchanger, 104a outdoor fan, 105 expansion portion, 106 indoor heat exchanger, 106a indoor fan, 200 Refrigeration cycle device, 201 outdoor unit, 202 indoor unit, 203 refrigerant circuit,204 Piping.

Claims

1. A compressor comprising: a container that forms an outer shell and has an oil reservoir formed at the bottom inside for storing refrigeration oil; a stator fixed to the container and having a stator passage formed on part of its outer periphery through which refrigerant passes, and a rotor placed within the stator; a drive shaft attached to the rotor of the motor and transmitting the rotational force of the motor; a compression mechanism that rotates in conjunction with the rotation of the drive shaft to compress the refrigerant; a frame fixed to a frame fixing part of the container below the motor and supporting a bearing that supports the drive shaft; and an oil rise suppression part placed on the frame and suppressing the rise of refrigeration oil that has passed through the stator passage, wherein the distance between the lower end of the stator and the oil rise suppression part in the axial direction of the drive shaft is shorter than the distance between the oil rise suppression part and the frame fixing part in the axial direction.

2. The compressor according to claim 1, further comprising a balance weight fixed to the lower end of the rotor to adjust the rotation balance of the motor, the lower end of the stator being positioned lower than the lower end of the balance weight.

3. A compressor according to claim 1 or 2, wherein the outer periphery of the oil leakage prevention portion is circular.

4. A compressor according to any one of claims 1 to 3, wherein a gap is formed between the stator and the rotor, and the oil leakage suppression section has an insertion hole formed in a position facing the gap and a partition section facing the frame.

5. A compressor according to claim 4, wherein the frame has a support portion that supports the bearing, and a plurality of fixed legs that extend radially from the support portion and are fixed to the frame fixing portion, and the insertion holes are formed at opposing positions between the fixed legs.

6. A compressor according to claim 4 or 5, wherein the insertion hole is arc-shaped with its center at the center of the partition wall.

7. A compressor according to any one of claims 1 to 6, wherein the container has a body portion having open top and bottom surfaces, an upper lid portion covering the top surface of the body portion, and a lower lid portion covering the bottom surface of the body portion.

8. The compressor according to any one of claims 1 to 7, wherein the refrigerant is any one of R1234yf, R1234ze, R32, and R290, a mixed refrigerant of two or more of these, a mixed refrigerant of any one of these refrigerants with another refrigerant, a mixed refrigerant including R1132(E), or a mixed refrigerant including R1123.

9. A refrigeration cycle device comprising a refrigerant circuit in which the compressor, outdoor heat exchanger, expansion section and indoor heat exchanger according to any one of claims 1 to 8 are connected by piping, and through which the refrigerant flows.

Images