WO2023152858A1

WO2023152858A1 - Compressor and refrigeration cycle device

Info

Publication number: WO2023152858A1
Application number: PCT/JP2022/005287
Authority: WO
Inventors: 秀明北川
Original assignee: 三菱電機株式会社
Priority date: 2022-02-10
Filing date: 2022-02-10
Publication date: 2023-08-17
Also published as: JPWO2023152858A1

Abstract

A compressor (100) is provided with: a closed container (1) having an oil reservoir space at the bottom thereof; a compression mechanism unit (2) that is disposed inside the closed container and compresses a refrigerant; an electric motor (16) that is disposed below the compression mechanism unit; a drive shaft (19) that transmits a rotating force of the electric motor to the compression mechanism unit; and a frame (37) that is disposed below the electric motor and supports the drive shaft. The compressor is provided with a plate-shaped annular member (50) that has a through-hole through which the drive shaft is passed, the plate-shaped annular member (50) being attached to a lower part of the frame with the drive shaft passing through the through-hole. The frame has a plurality of fixed leg parts (37b) that extend axially and radially of the drive shaft and are fixed to the closed container. The annular member has the same number of passage holes (52) as the plurality of fixed leg parts to allow the refrigerant over the annular member to be passed toward the underside of the annular member. The plurality of passage holes are formed adjacent to wall surfaces of the plurality of fixed leg parts on the side opposite to a rotating direction of the electric motor. In each of the plurality of fixed leg parts, the wall surface (37c1) on the side opposite to the rotating direction serves as a wind guiding wall that guides the refrigerant over the annular member to each of the plurality of passage holes.

Description

Compressor and refrigeration cycle equipment

The present disclosure relates to a compressor and a refrigeration cycle device having a sealed container having an oil reservoir space at the bottom.

Conventionally, a compression mechanism, an electric motor, and a drive shaft for transmitting the rotational force of the electric motor to the compression mechanism are provided in a closed container. There is a compressor that compresses the working gas. The compressor stores refrigerating machine oil (hereinafter referred to as oil) in an oil reservoir space at the bottom of the closed container. By sealing the , it is possible to compress the refrigerant in the compression mechanism. In this type of compressor, low-pressure refrigerant sucked into the sealed container from the suction pipe is compressed by the compression mechanism to become high-pressure refrigerant, and the high-pressure refrigerant is once discharged from the compression mechanism into the sealed container and then discharged into the discharge pipe. is discharged out of the closed container. The high-pressure refrigerant discharged from the compression mechanism contains oil, and the oil is discharged out of the sealed container together with the high-pressure refrigerant.

In the compressor described above, the rotation of the electric motor causes a swirling flow of the refrigerant in the closed container. The swirling flow may collide with the oil in the oil sump space and atomize the oil. The atomized oil is sometimes mixed with the gaseous refrigerant in the closed container and discharged out of the closed container in large amounts together with the refrigerant. When the amount of oil discharged from the compressor to the outside increases in this way, the oil in the oil sump space is depleted, resulting in insufficient supply of oil to the sliding parts, which lowers the reliability of the compressor.

Therefore, there is a compressor that suppresses the discharge of oil to the outside of the sealed container (see Patent Document 1, for example). In Patent Document 1, a plate-shaped annular member is arranged so as to cover an oil reservoir space, and a plurality of baffle plates having a large number of pores are erected and fixed to the annular member at intervals in the circumferential direction. are doing. With this configuration, Patent Document 1 discloses that the swirling flow collides with the baffle plate instead of the oil in the oil reservoir space to separate the oil from the refrigerant, and the separated oil is transferred to the gap between the annular member and the drive shaft. The amount of oil discharged to the outside of the sealed container is reduced by dropping the oil into the oil reservoir space.

JP 2012-202253 A

The compressor of Patent Document 1 has a configuration in which a plurality of baffle plates are fixed to an annular member, so there is a problem that the number of parts increases.

The present disclosure has been made to solve the above-described problems, and an object of the present disclosure is to provide a compressor and a refrigeration cycle device that can reduce the number of parts and reduce the amount of oil discharged out of the sealed container. It is.

A compressor according to the present disclosure includes a closed container having an oil reservoir space at the bottom, a compression mechanism arranged in the closed container for compressing a refrigerant, an electric motor arranged below the compression mechanism, and rotation of the electric motor. A compressor comprising a drive shaft that transmits force to a compression mechanism and a frame that is disposed below the electric motor and supports the drive shaft, wherein a through hole is formed through which the drive shaft passes, and the drive shaft passes through the through hole A plate-shaped annular member is passed through and attached to the lower part of the frame, and the frame has a plurality of fixed legs extending in the axial direction of the drive shaft and in the radial direction of the drive shaft and fixed to the closed container. The annular member is formed with the same number of passage holes as the plurality of fixed legs for allowing the refrigerant above the annular member to pass below the annular member. On the other hand, the wall surface of each of the plurality of fixed legs, which is formed on the side opposite to the rotation direction of the electric motor and on the side opposite to the rotation direction, guides the refrigerant above the annular member to each of the plurality of passage holes. It is a wall.

A refrigeration cycle apparatus according to the present disclosure includes the compressor, condenser, pressure reducer, and evaporator.

According to the present disclosure, in the compressor, the annular member suppresses the scattering of the oil in the oil sump space, and the oil existing above the annular member is used as the air guide wall for the wall surface of the fixed leg and the annular member. can be positively led to the oil reservoir space by the through hole. Therefore, the compressor can reduce the amount of oil discharged to the outside of the sealed container. The annular member is formed from a plate member, and the frame has a conventionally existing structure. Therefore, the compressor can reduce the number of parts. In this way, the compressor can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.

1 is a schematic vertical cross-sectional view showing a compressor according to Embodiment 1; FIG. FIG. 2 is a partially enlarged view of FIG. 1; FIG. 4 is an explanatory diagram of flow paths formed between a guide frame and a closed container of the compressor according to Embodiment 1; 2 is a perspective view of a subframe and an annular member of the compressor according to Embodiment 1. FIG. 3 is a partial schematic cross-sectional view of a subframe and an annular member of the compressor according to Embodiment 1; FIG. 3 is a partial schematic perspective view of a subframe and an annular member of the compressor according to Embodiment 1. FIG. FIG. 2 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 2;

Embodiment 1.
FIG. 1 is a schematic vertical cross-sectional view showing a compressor according to Embodiment 1. FIG. 2 is a partially enlarged view of FIG. 1. FIG. FIG. 3 is an explanatory diagram of flow paths formed between the guide frame and the closed container of the compressor according to Embodiment 1. FIG. The configuration of the compressor 100 will be described below with reference to FIGS. 1 to 3. FIG.

The compressor 100 is a so-called vertical scroll compressor, and the axial direction of the compressor 100 is the Z direction, which is the vertical direction in FIG. The compressor 100 compresses and discharges a refrigerant, which is a working gas. As the refrigerant, for example, R407C refrigerant, R410A refrigerant, R32 refrigerant, or the like is used. The compressor 100 includes a closed container 1 having an oil reservoir space 5 at the bottom, a compression mechanism section 2 having a fixed scroll 4 and an orbiting scroll 3, an electric motor 16, and a drive shaft 19. This compressor 100 is one of the components of a refrigeration cycle used in various industrial machines such as refrigerators, freezers, air conditioners, refrigeration systems, and water heaters. In the following description, the direction in which the drive shaft 19 extends is called the axial direction, the direction perpendicular to the axial direction is called the radial direction, and the direction around the drive shaft is called the circumferential direction.

A compression mechanism 2, an electric motor 16, and a drive shaft 19 are accommodated in the closed container 1. As will be described later, the high-pressure refrigerant gas compressed by the compression mechanism 2 is discharged into the high-pressure gas atmosphere 6 inside the sealed container 1 . This refrigerant gas is configured to circulate through a refrigeration cycle circuit in which the compressor 100 is incorporated.

The sealed container 1 is formed, for example, in a cylindrical shape and has pressure resistance. The sealed container 1 is formed to extend vertically. A suction pipe 7 is connected to the side surface of the sealed container 1 for taking the refrigerant into the sealed container 1 . A discharge pipe 11 for discharging the compressed refrigerant from the closed container 1 to the outside is connected to the other side surface of the closed container 1 . A suction check valve 9 and a spring 10 are arranged inside the suction pipe 7 . The suction check valve 9 is urged by a spring 10 in a direction to close the suction pipe 7 and prevents the refrigerant from flowing backward.

The sealed container 1 has a high-pressure gas atmosphere 6 filled with high-pressure gas compressed by the compression mechanism 2 inside the closed container 1 . The sealed container 1 also has an oil reservoir space 5 for storing refrigerating machine oil (hereinafter referred to as oil) at the bottom of the sealed container 1 . The oil sump space 5 is located within a high-pressure gas atmosphere 6 . The oil sump space 5 is a space below the sub-frame 37 that supports the lower end of the drive shaft 19 in the closed container 1 . The drive shaft 19 is supported by a thrust bearing 28 provided on the lower end surface of the drive shaft 19 . Thrust bearing 28 is fixed to holder 29 fixed to sub-frame 37 . An annular member 50 for reducing the amount of oil discharged out of the closed container is attached to the lower portion of the sub-frame 37 by, for example, a fastener (not shown). The details of the ring member 50 will be explained again.

The compression mechanism section 2 is a section that compresses the refrigerant sucked into the sealed container 1 from the intake pipe 7 and has an orbiting scroll 3 and a fixed scroll 4 . As shown in FIG. 1, the fixed scroll 4 is arranged on the upper side and the orbiting scroll 3 is arranged on the lower side. The fixed scroll 4 has a fixed base plate 4b and a fixed spiral body 4a formed on the fixed base plate 4b. The orbiting scroll 3 has an orbiting bed plate 3b and an orbiting spiral body 3a formed on the orbiting bed plate 3b.

The fixed scroll 4 and the orbiting scroll 3 are arranged so that the fixed spiral body 4a and the orbiting scroll body 3a face each other. A compression chamber 2b is formed between the fixed spiral body 4a and the oscillating spiral body 3a by combining the fixed spiral body 4a and the oscillating spiral body 3a in opposite directions. Further, the fixed spiral body 4a of the fixed scroll 4 and the outer peripheral space of the base plate outside the orbiting scroll 3 (hereinafter referred to as the suction side space 8) are a low-pressure space of suction gas atmosphere of suction pressure.

The fixed scroll 4 is fixed with bolts (not shown) or the like to a guide frame 30 fixedly supported by the sealed container 1 . A pair of two fixed-side Oldham ring grooves 15 a are formed in a straight line on the outer peripheral portion of the fixed scroll 4 . A pair of two fixed-side keys 42a of the Oldham ring 40 are installed in the fixed-side Oldham ring groove 15a so as to be reciprocally slidable.

A cylindrical boss portion 3c is formed on the other surface of the oscillating base plate 3b of the oscillating scroll 3 opposite to the one surface on which the oscillating spiral body 3a is formed. A swing bearing 26 is provided on the inner surface of the boss portion 3c. The swing shaft 21 of the drive shaft 19 is inserted into the swing bearing 26 , and the rotation of the swing shaft 21 causes the swing scroll 3 to revolve with respect to the fixed scroll 4 .

A compliant frame 31 is arranged in contact with the other surface of the rocking base plate 3b of the rocking scroll 3. A thrust surface 33 of the compliant frame 31 and a thrust surface 3 d that can slide are formed on the other surface of the rocking base plate 3 b of the rocking scroll 3 . A pair of rocking-side Oldham ring grooves 15b are formed in a straight line on the outer peripheral portion of the rocking scroll 3 . The rocking-side Oldham ring groove 15b has a phase difference of about 90 degrees from the fixed-side Oldham ring groove 15a, and a pair of rocking-side keys 42b of the Oldham ring 40 are installed so as to be reciprocally slidable. . The swing-side key 42 b reciprocates on a reciprocating sliding surface 41 formed on the outer periphery of the thrust surface 33 of the compliant frame 31 .

The rocking bed plate 3b is formed with an air bleed hole 3e penetrating from one surface on which the rocking spiral body 3a is provided to the other surface of the rocking bed plate 3b. As shown in FIG. 2, the air bleed holes 3e are composed of an air bleed inlet 3ei formed on the upper surface, which is one surface of the rocking base plate 3b, and an air bleed outlet formed on the lower surface, which is the other surface of the rocking base plate 3b. 3eo. The bleed inlet 3ei opens into the compression chamber 2b. The extraction outlet 3eo intermittently communicates with the gas introduction passage 14 provided in the compliant frame 31 . The extraction outlet 3eo intermittently communicates with the gas introduction passage 14, so that intermediate-pressure gas refrigerant in the middle of compression in the compression chamber 2b flows through the extraction hole 3e and the gas introduction passage 14 into an intermediate pressure space 32b, which will be described later. (See FIG. 1). The intermediate pressure refers to a pressure higher than the suction pressure and lower than the discharge pressure. In this manner, the air bleed hole 3e intermittently bleeds air from the compression chamber 2b in the middle of compression to the intermediate pressure space 32b as the orbiting scroll 3 revolves.

A guide frame 30 and a sub-frame 37 that holds the drive shaft 19 are fixed inside the sealed container 1 . The guide frame 30 is positioned below the compression mechanism 2 and above the electric motor 16 . The subframe 37 is positioned below the electric motor 16 . A compliant frame 31 is housed inside the guide frame 30 .

Between the outer peripheral surface of the guide frame 30 and the inner wall of the sealed container 1, a flow path 30c is formed through which the high-pressure gas refrigerant flowing out from the discharge port 12 formed in the fixed scroll 4 passes (FIGS. 1 and 3). 3). The high-pressure gas refrigerant that has flowed out from the discharge port 12 is guided below the compression mechanism section 2 through the flow path 30c. A high-pressure gas atmosphere 6 is formed in the sealed container 1 by guiding the high-pressure gas refrigerant downward from the compression mechanism section 2 .

An upper fitting cylindrical surface 30a is formed on the inner peripheral surface of the guide frame 30 on the compression mechanism 2 side. The upper fitting cylindrical surface 30 a is engaged with an upper fitting cylindrical surface 35 a formed on the outer peripheral surface of the compliant frame 31 . On the other hand, a lower fitting cylindrical surface 30 b is formed on the inner peripheral surface of the guide frame 30 on the electric motor 16 side, and the lower fitting cylindrical surface 30 b is formed on the outer peripheral surface of the compliant frame 31 . It is engaged with the mating cylindrical surface 35b.

An upper annular seal member 36 a and a lower annular seal member 36 b are arranged at two locations on the outer peripheral surface of the compliant frame 31 . An upper annular seal member 36 a and a lower annular seal member 36 b partition between the inner surface of guide frame 30 and the outer surface of compliant frame 31 . An intermediate pressure space 32b is formed by a space partitioned by the upper annular seal member 36a and the lower annular seal member 36b. Although the upper annular seal member 36a and the lower annular seal member 36b are arranged at two locations on the outer peripheral surface of the compliant frame 31 in FIG. 1, the positions of these seal members are limited to the example of FIG. can't These sealing members may be arranged, for example, at two locations on the inner peripheral surface of the guide frame 30 .

The compliant frame 31 supports the orbiting scroll 3 in the axial direction. The compliant frame 31 has a thrust surface 33 that axially supports the thrust force acting in the axial direction of the orbiting scroll 3 . The compliant frame 31 is formed with a gas introduction passage 14 that communicates between the space formed above the thrust surface 33 and the intermediate pressure space 32b. The gas introduction passage 14 communicates with the bleed hole 3 e according to the orbital motion of the orbiting scroll 3 . Intermediate-pressure refrigerant is introduced into the intermediate-pressure space 32b from the compression chamber 2b, which is in the middle of compression, by connecting the gas introduction passage 14 to the bleed hole 3e. On the other hand, the bleed hole 3e is blocked by facing the thrust surface 33 of the compliant frame 31 according to the orbital motion of the orbiting scroll 3, thereby stopping the introduction of the intermediate-pressure refrigerant into the intermediate-pressure space 32b. . By repeating the communication of the bleed hole 3e with the gas introduction passage 14 and the blockage of the bleed hole 3e by the thrust surface 33 in this way, the intermediate-pressure gas refrigerant flows from the compression chamber 2b to the intermediate-pressure space 32b. Introduction occurs intermittently. The intermediate pressure space 32b becomes intermediate pressure by intermittently introducing the intermediate pressure gas refrigerant.

The compliant frame 31 axially supports the orbiting scroll 3 by the intermediate pressure in the intermediate pressure space 32b. The intermediate pressure in the intermediate pressure space 32 b acts on the compliant frame 31 . A high pressure from the high-pressure gas atmosphere 6 acts on the compliant frame lower end surface 34 . The compliant frame 31 floats in the axial direction due to these pressures acting on the compliant frame 31 and has a function of pushing up the orbiting scroll 3 in the axial direction.

Between the outside of the boss portion 3c of the orbiting scroll 3 and the compliant frame 31, an intermediate-pressure boss portion outer space 38 is provided. Further, the compliant frame 31 is provided with an intermediate pressure regulating valve space 39d. The intermediate pressure regulating valve space 39d accommodates an intermediate pressure regulating valve 39a for adjusting the pressure of the boss portion outer space 38, an intermediate pressure regulating valve retainer 39b, and an intermediate pressure regulating spring 39c. The intermediate pressure adjusting spring 39c is contracted from its natural length and accommodated in the intermediate pressure adjusting valve space 39d.

Furthermore, the compliant frame 31 is provided with a through passage 39e that communicates between the boss portion outer space 38 and the intermediate pressure regulating valve space 39d. A compliant frame upper space 32a is provided between the outer peripheral surface of the compliant frame 31 on the fixed scroll side (upper side in FIG. 1) of the intermediate pressure regulating valve space 39d and the inner peripheral surface of the guide frame 30. ing. The compliant frame upper space 32a communicates with the intermediate pressure regulating valve space 39d. Also, the compliant frame upper space 32 a communicates with the space inside the Oldham ring 40 . Therefore, the boss portion outer space 38 and the inner space of the Oldham ring 40 communicate with each other via the through passage 39e, the intermediate pressure regulating valve space 39d, and the compliant frame upper space 32a.

The electric motor 16 rotates the drive shaft 19 . The electric motor 16 is configured such that its operating frequency can be controlled by, for example, an inverter device. The electric motor 16 has an electric motor rotor 16a and an electric motor stator 16b, and generates a rotational force with a variable rotational speed. The motor rotor 16a is fixed to the drive shaft 19 by shrink fitting or the like. The electric motor rotor 16a has a plurality of through passages 17a penetrating in the axial direction, and the plurality of through passages 17a are formed symmetrically or point-symmetrically with respect to the axis.

Also, the motor rotor 16a and the motor stator 16b are positioned so that a minute gap 17c exists between them. The electric motor stator 16b is connected to a glass terminal (not shown) fixed to the guide frame 30 via a lead wire (not shown) to obtain power from the outside. The electric motor stator 16b is fixed to the closed container 1 by shrink fitting or the like, and a through passage 17b is formed by notching in the outer peripheral portion of the electric motor stator 16b. The drive shaft 19 and the electric motor rotor 16a rotate with respect to the electric motor stator 16b when electric power is supplied to the electric motor stator 16b. A balance weight 18a is fixed to the motor rotor 16a and a balance weight 18b is fixed to the drive shaft 19 in order to balance the entire rotation system of the compressor 100. As shown in FIG.

The drive shaft 19 has a swing shaft 21 forming the upper portion of the drive shaft 19 , a main shaft 20 forming the intermediate portion of the drive shaft 19 , and a sub shaft 22 forming the lower portion of the drive shaft 19 . The main shaft 20 has a cylindrical structure, is fitted in a main bearing 25 provided on the inner peripheral surface of the compliant frame 31, and is rotatably supported. The sub-shaft 22 is rotatably supported by a sub-bearing 27 provided on the inner peripheral surface of the sub-frame 37 . The lower end surface of the secondary shaft 22 is supported by its own weight by a thrust bearing 28 . Thrust bearing 28 is fixed to holder 29 , and holder 29 is fixed to sub-frame 37 . The main bearing 25 and the sub-bearing 27 have a cylindrical structure and are made of, for example, sliding bearings such as a copper-lead alloy, and rotatably support the drive shaft 19 .

The drive shaft 19 transmits the rotational force generated by the electric motor 16 to the compression mechanism section 2 . Inside the drive shaft 19, an oil supply passage 23 extending axially from the end of the drive shaft 19 and

supply passages

24a and 24b extending radially from the oil supply passage 23 are formed. The oil supply passage 23 opens at the axial upper end of the drive shaft 19 . A supply passage 24 a is formed in the sub shaft 22 and a supply passage 24 b is formed in the main shaft 20 . The supply path 24b opens at a position covered by the main bearing 25 and supplies the main bearing 25 with oil. A supply passage 24a of the subshaft 22 opens at a position covered with the subshaft 22 and supplies the subshaft 22 with oil. The oil sucked up from the oil sump space 5 passes through the oil supply passage 23 and the

supply passages

24a and 24b, and is supplied to sliding portions such as the main bearing 25, the swing bearing 26 and the sub-bearing 27. In FIG. 1, thin arrows indicate the flow of oil.

FIG. 4 is a perspective view of a subframe and an annular member of the compressor according to Embodiment 1. FIG. 5 is a partial schematic cross-sectional view of a subframe and an annular member of the compressor according to Embodiment 1. FIG. As shown in FIG. 4, the sub-frame 37 has a cylindrical portion 37a through which the drive shaft 19 is passed, and fixed leg portions 37b provided on the outer peripheral surface of the cylindrical portion 37a. The fixed leg portion 37b extends axially and radially from the cylindrical portion 37a. The fixed leg portion 37b is further formed such that the radially outer end extends upward. A radially outer end surface of the fixed leg portion 37b is fixed to the inner peripheral surface of the sealed container 1 by welding or the like. Three fixed leg portions 37b are formed at equal intervals in the circumferential direction on the outer peripheral surface of the cylindrical portion 37a. The number of fixing legs 37b is not limited to three, and may be two or four or more. A plurality of fixing legs 37b may be provided.

The fixed leg portion 37b has two wall surfaces 37c facing each other in the circumferential direction. to a passage hole 52 of the annular member 50, which will be described later. As will be described later, in the annular member upper space 60, the rotation of the electric motor rotor 16a provided above the sub-frame 37 causes a swirling flow of refrigerant gas containing oil that has been compressed to a high pressure. . This swirl flow is a flow directed in the same direction as the rotation direction R of the electric motor rotor 16a. In FIG. 4, the dotted arrow indicates the direction of the swirling flow. A wall surface 37c1 of the fixed leg portion 37b is an inclined surface 37c2 that is inclined upward toward the side opposite to the rotation direction R so as to easily receive this swirling flow. The function and the like of this inclined surface 37c2 will be described later.

The annular member 50 is composed of a single plate member. The annular member 50 is made of a metal plate. A through hole 51 is formed in the center of the annular member 50 , and the drive shaft 19 is passed through the through hole 51 to be arranged between the electric motor 16 and the oil stored in the oil storage space 5 . The annular member 50 has an outer diameter slightly smaller than the inner diameter of the sealed container 1 and forms a slight gap with the inner peripheral surface of the sealed container 1 . This gap is provided to return the oil adhering to the inner peripheral surface of the sealed container 1 to the oil reservoir space 5 .

The annular member 50 is formed with a passage hole 52 through which the coolant in the annular member upper space 60 passes toward the oil reservoir space 5 . In other words, the circular ring member 50 is formed with a passage hole 52 through which the refrigerant above the circular ring member 50 is passed downwardly of the circular ring member 50 . The passage hole 52 is configured as a through hole. The passage holes 52 are provided in the same number as the fixing leg portions 37b, and are arranged on the side opposite to the rotation direction R with respect to the fixing leg portions 37b. The passage hole 52 is provided in contact with the lower edge 37c3 of the wall surface 37c1 of the fixed leg portion 37b. 4 shows an example of a rectangular shape, the shape of the passage hole 52 is not limited to a rectangular shape. The function and the like of the passage hole 52 of the annular member 50 will be described later.

Next, startup and operation of the compressor 100 will be described with reference to FIGS. 1 to 3. FIG. Outlined arrows in FIGS. 1 and 2 indicate the flow of the refrigerant. When a low-pressure (suction pressure) gas refrigerant is supplied from the suction pipe 7 toward the suction check valve 9, the gas refrigerant overcomes the spring force of the spring 10 and causes the suction check valve 9 to stop (not shown). ). As a result, the suction check valve 9 is opened, and the gas refrigerant flows into the suction side space 8 inside the sealed container 1 .

On the other hand, the drive shaft 19 starts rotating when electric power is supplied to the electric motor 16 from the outside. The rotation of the drive shaft 19 causes the swing shaft 21 to rotate, and the swing scroll 3 performs a swing motion (orbital motion). At this time, the gas refrigerant is sucked into the compression chamber 2 b formed between the orbiting scroll 3 and the fixed scroll 4 .

The gas refrigerant is eventually boosted from low pressure to high pressure due to the geometric volume change of the compression chamber 2b. Thereafter, the gas refrigerant pressurized to a high pressure is discharged from the discharge port 12, passes through the flow path 30c, and is guided below the guide frame 30. As shown in FIG. The inside of the sealed container 1 becomes a high-pressure gas atmosphere 6 due to the gas refrigerant guided below the guide frame 30 . A high-pressure gas refrigerant inside the sealed container 1 is discharged to the outside through a discharge pipe 11 .

The bleed outlet 3eo of the bleed hole 3e of the oscillating bed plate 3b temporarily communicates with the gas introduction passage 14 due to the orbital motion of the oscillating scroll 3. The bleed outlet 3eo of the bleed hole 3e is temporarily communicated with the gas introduction passage 14, whereby the intermediate-pressure gas refrigerant that is being compressed in the compression chamber 2b communicating with the bleed hole 3e is bled out of the compression chamber 2b. , through the gas introduction channel 14 into the intermediate pressure space 32b. The temporary communication between the bleed hole 3e and the gas introduction passage 14 is intermittently performed while the orbiting scroll 3 revolves.

The intermediate pressure space 32b is a space sealed by an upper annular seal member 36a and a lower annular seal member 36b. Therefore, the intermediate-pressure gas refrigerant introduced into the intermediate-pressure space 32b floats the compliant frame 31 in the axial direction.

The intermediate pressure Pm1 in the boss outer space 38 is a combination of a predetermined pressure α determined by the elastic force of the intermediate pressure regulating spring 39c and the area exposed to the intermediate pressure of the intermediate pressure regulating valve 39a, and the pressure in the suction side space 8. It is the sum with Ps, which is Ps+α. Further, the intermediate pressure Pm2 of the intermediate pressure space 32b is the product of a predetermined magnification β determined at the position of the compression chamber 2b communicating with the intermediate pressure space 32b and the pressure Ps of the suction side space 8, and is expressed as Ps×β. Become.

Due to the intermediate pressure Pm1, the intermediate pressure Pm2, and the high pressure from the high-pressure gas atmosphere 6 acting on the lower end surface 34 of the compliant frame 34, the compliant frame 31 floats along the inner peripheral surface of the guide frame 30 in the axial direction. The force due to this levitation is called pressing force.

Due to the pressing force of the compliant frame 31, the orbiting scroll 3 is pushed up via the thrust surface 33 and floats. The levitation of the orbiting scroll 3 reduces the gap between the tip of each of the spiral bodies of the fixed scroll 4 and the orbiting scroll 3 forming the compression chamber 2b and the base plate. As a result, the high-pressure gas refrigerant is less likely to leak from the compression chamber 2b, and a highly efficient scroll compressor can be obtained.

On the other hand, if the pressure inside the compression chamber 2b becomes abnormally high during start-up and liquid compression, the axial gas load acting on the orbiting scroll 3 becomes excessive. Then, the orbiting scroll 3 pushes down the compliant frame 31 via the thrust surface 33 . That is, a relatively large gap is generated between the tip of the spiral body of each of the fixed scroll 4 and the orbiting scroll 3 and the base plate, so that an abnormal pressure rise in the compression chamber 2b can be suppressed, and there is no damage to the sliding portion. can obtain a compressor 100 with a high

Next, the flow of oil in the compressor 100 will be described with reference to FIG. Thin arrows in FIG. 1 indicate the flow of oil. When the drive shaft 19 rotates with the rotation of the motor rotor 16 a , the inside of the sealed container 1 is filled with the gas compressed by the compression mechanism 2 and becomes a high-pressure gas atmosphere 6 . Since the oil reservoir space 5 exposed to the high-pressure gas atmosphere 6 and the suction side space 8 of the compression mechanism 2 communicate with each other through the oil supply passage 23 of the drive shaft 19, the oil in the oil reservoir space 5 is be sucked up. This oil is supplied to the main bearing 25, the sub-bearing 27 and the rocking bearing 26 from the oil supply passage 23, the supply passage 24a and the supply passage 24b, respectively. The oil supplied to the main bearing 25, the sub-bearing 27 and the swing bearing 26 lubricates the bearings and then returns to the oil reservoir space 5 below the sealed container 1 by its own weight.

Here, the oil supplied to the main bearing 25 lubricates the main bearing 25 and then is led to the boss portion outer space 38 or the high-pressure gas atmosphere 6 . After passing through the main bearing 25 , the oil supplied to the boss portion 3 c of the orbiting scroll 3 lubricates the orbiting bearing 26 . led to. The oil guided to the boss outer space 38 overcomes the spring force of the intermediate pressure regulating spring 39c when passing through the through passage 39e, pushes up the intermediate pressure regulating valve 39a, and temporarily enters the compliant frame upper space 32a. Ejected. After that, this oil is discharged inside the Oldham ring 40 and supplied to the suction side space 8 .

A part of the refrigerant discharged to the compliant frame upper space 32 a is supplied to the reciprocating sliding surface 41 after being supplied to the thrust surface 3 d and flows into the suction side space 8 . The oil that has flowed into the suction side space 8 is sucked into the compression mechanism portion 2 together with the low-pressure gas refrigerant. The sucked oil seals and lubricates the gaps between the fixed scroll 4 and the orbiting scroll 3 that constitute the compression mechanism 2, thereby enabling normal operation.

Excess oil in the compression mechanism portion 2 is discharged from the discharge port 12 of the compression mechanism portion 2 in a state of being contained in the refrigerant, passes through the flow path 30c along the flow of the refrigerant, and enters the compression mechanism portion. 2 below. Refrigerant containing oil that has been guided downward from the compression mechanism portion 2 is guided to the annular member upper space 60 through the through passage 17b. The annular member upper space 60 is a space below the electric motor 16 and above the sub-frame 37 . In the annular member upper space 60, a swirling flow is generated due to the rotation of the electric motor rotor 16a.

Here, if the compressor 100 does not have the annular member 50 , the swirling flow in the annular member upper space 60 collides with the oil in the oil sump space 5 . As a result, the oil in the oil reservoir space 5 scatters and becomes misty, and the misty oil is mixed with the refrigerant and is discharged out of the sealed container as a result, increasing the amount of oil discharged out of the sealed container. .

On the other hand, since the compressor 100 is provided with the annular member 50, the annular member 50 can suppress the collision of the swirling flow with the oil in the oil reservoir space 5, thereby suppressing oil scattering. The fixed leg portion 37b of the sub-frame 37 has a wall surface 37c1 functioning as a wind guide wall. For this reason, the oil existing in the annular member upper space 60 is rectified by the wall surface 37c1 into a flow toward the passage hole 52 while being contained in the refrigerant, and is actively transferred to the oil sump space 5 through the passage hole 52. be guided. The oil-containing refrigerant guided into the oil sump space 5 separates the oil while swirling in the oil sump space 5 , and the separated oil is stored in the oil sump space 5 .

The oil existing in the annular member upper space 60 flows along with the swirling flow in the annular member upper space 60 while being contained in the refrigerant, and collides with the wall surface 37c1 of the fixed leg portion 37b. to adhere to. The oil adhering to the wall surface 37c1 drops from the passage hole 52 into the oil reservoir space 5 along the wall surface 37c1 due to its own weight.

Here, if the wall surface 37c1 of the fixed leg portion 37b is a vertical surface, the oil adhering to the wall surface 37c1 will flow in the following two ways. One is a flow that drops from the passage hole 52 into the oil reservoir space 5 by its own weight along the wall surface 37c1. The other is a flow that flows upward along the wall surface 37c1 and scatters into the annular member upper space 60. FIG.

In Embodiment 1, the wall surface 37c1 of the fixed leg portion 37b forms an inclined surface 37c2 that inclines upward toward the direction opposite to the rotation direction R. For this reason, the oil adhering to the inclined surface 37 c 2 is concentrated in a flow that falls toward the oil reservoir space 5 without scattering into the annular member upper space 60 .

Also, the passage hole 52 is provided on the side opposite to the rotation direction R with respect to the fixed leg portion 37b of the sub-frame 37 . If the passage hole 52 is provided on the side of the rotation direction with respect to the fixed leg portion 37b, the swirl flow of the refrigerant containing the oil is dammed by the fixed leg portion 37b, and the swirl flow can be guided to the pass hole 52. Can not. On the other hand, since the passage hole 52 is provided on the side opposite to the rotation direction R with respect to the fixed leg portion 37b, the wall surface 37c1 of the fixed leg portion 37b can guide the swirling flow to the passage hole 52. .

Also, the passage hole 52 is provided in contact with the lower edge 37c3 of the wall surface 37c1. For this reason, the oil adhering to the wall surface 37c1 easily flows into the passage hole 52, and the amount of oil falling into the oil reservoir space 5 is increased compared to the configuration in which the passage hole 52 is provided away from the lower edge 37c3 of the wall surface 37c1. can.

In this manner, the compressor 100 uses the annular member 50 to suppress oil splashing in the oil sump space 5, while the oil existing in the annular member upper space 60 is actively removed by the inclined surface 37c2 and the passage hole 52. It can be led to the oil reservoir space 5 . Therefore, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container.

Here, in Embodiment 1, the configuration necessary for exhibiting the function of reducing the amount of oil discharged to the outside of the sealed container is the passage hole 52 of the annular member 50 and the fixed leg portion 37b of the sub-frame 37. I can say. The annular member 50 is formed from a single plate member, and the sub-frame 37 has a conventionally existing structure. Therefore, the number of parts can be reduced compared to the conventional structure in which a plurality of baffle plates are fixed to the annular member. In this manner, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.

In addition, in the compressor 100, the inclined surface 37c2 straightens the swirling flow of the refrigerant containing oil toward the passage hole 52 and actively guides the oil to the oil reservoir space 5. A higher effect of reducing the amount of oil discharged to the outside of the sealed container can be expected.

Next, the definition of the angle of the wall surface 37c1 with respect to the annular member 50 for enhancing the rectifying effect of the wall surface 37c1 of the fixed leg portion 37b will be described.

FIG. 6 is a partial schematic perspective view of the subframe and annular member of the compressor according to Embodiment 1. FIG. As shown in FIG. 6, the flow path surrounded by the end AB on the side opposite to the rotation direction R of the wall surface 37c1 and the end CD on the side opposite to the rotation direction R of the passage hole 52, that is, surrounded by ABCD. Let the channel through which the particles are captured be the capture channel 55, and let its area be S1. Also, let S2 be the area of the channel formed by the passage hole 52, that is, the area of the channel surrounded by the EFCD.

The refrigerant swirling in the annular member upper space 60 is guided from the capture channel 55 to the passage hole 52 as indicated by arrows w1 and w2. At this time, the compressor 100 preferably satisfies S1>S2 in order to "capture the swirling refrigerant" and "actively return the oil to the oil reservoir space 5 by contraction".

With the above configuration, the compressor 100 can efficiently capture the swirling refrigerant in the capture channel 55 , and the refrigerant is contracted from the capture channel 55 toward the passage hole 52 to flow into the oil sump space 5 . Active return of oil can be achieved.

Here, the angle formed by the annular member 50 and the wall surface 37c1 is θ, the length of the lower side of the wall surface 37c1, that is, the length between EF, is T, and the length between the lower side and the upper side of the wall surface 37c1, that is, AE Let L be the length between
S1=T×L×2 sin(θ/2) (Formula 1)
S2=T×L (Formula 2)
It can be expressed as. Note that AE=BF=DE=CF and DC=EF=AB.

In order to find the angle θ that satisfies the inequality S1>S2, θ can be derived as θ>60° by substituting

Equations

1 and 2 into this inequality. However, if .theta. is 90.degree. When θ is 90°, the wall surface 37c1 blocks the swirling flow. If θ exceeds 90°, the swirling flow will flow along the upper surface of the wall surface 37c1, and the flow in the annular member upper space 60 will become aggressive. Therefore, the range of θ can be defined as 60°<θ<90°.

As described above, the compressor 100 according to the first embodiment has a plate-shaped plate-like structure in which the through hole 51 for passing the drive shaft 19 is formed, and the drive shaft 19 is passed through the through hole 51 and attached to the lower part of the sub-frame 37 . An annular member 50 is provided. The sub-frame 37 has a plurality of fixed legs 37 b extending in the axial direction of the drive shaft 19 and in the radial direction of the drive shaft 19 and fixed to the sealed container 1 . The annular member 50 is formed with the same number of passage holes 52 as the plurality of fixed leg portions 37b, through which the refrigerant above the annular member 50 is allowed to pass below the annular member 50. As shown in FIG. The plurality of passage holes 52 are formed on the side opposite to the rotation direction of the electric motor 16 with respect to the plurality of fixed leg portions 37b. A wall surface 37c1 on the side opposite to the rotation direction R in each of the plurality of fixed leg portions 37b serves as an air guide wall that guides the refrigerant above the annular member 50 to each of the plurality of passage holes 52. As shown in FIG.

With the above-described configuration, the compressor 100 uses the annular member 50 to suppress oil scattering in the oil sump space 5 , while the oil existing above the annular member 50 is actively removed by the wall surface 37 c 1 and the passage hole 52 . It can lead to the reservoir space 5 . Therefore, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container. The annular member 50 is formed from a plate member, and the sub-frame 37 has a conventionally existing structure. Therefore, the number of parts can be reduced compared to the conventional structure in which a plurality of baffle plates are fixed to the annular member. In this manner, the compressor 100 can reduce the amount of oil discharged to the outside of the sealed container while reducing the number of parts.

A wall surface 37c1 of the plurality of fixed leg portions 37b is an inclined surface 37c2 that is inclined upward toward the side opposite to the rotation direction R.

With the above configuration, the compressor 100 can more reliably reduce the amount of oil discharged to the outside of the sealed container.

The plurality of passage holes 52 are provided in contact with the lower edge 37c3 of the wall surface 37c1 of the plurality of fixed legs 37b.

With the above configuration, the compressor 100 can increase the amount of oil that drops into the oil reservoir space 5 through the passage hole 52 .

The angle θ of the wall surface 37c1 with respect to the annular member 50 satisfies 60°<θ<90°.

With the above configuration, the wall surface 37c1 can obtain rectification of the refrigerant to the oil reservoir space 5.

In the compressor 100, the area of the flow passage surrounded by the end of the wall surface 37c1 opposite to the rotation direction and the end of the passage hole 52 opposite to the rotation direction is S1, and the area of the passage hole 52 is S1. When the area is S2, S1>S2 is satisfied.

With the above configuration, the compressor 100 can capture the whirling refrigerant and positively return the oil to the oil reservoir space 5 by contraction.

The sub-frame 37 has a cylindrical portion 37a through which the drive shaft 19 is passed, and has three fixed leg portions 37b. ing.

With the above configuration, the compressor 100 causes the swirl flow of the refrigerant containing oil to collide with the wall surfaces 37c1 of the three fixed leg portions 37b, and the three passage holes 52 provided in the same number as the fixed leg portions 37b flow into the oil sump space 5. can lead to Therefore, the compressor 100 can more positively return the oil to the oil sump space 5 than the configuration with the two fixing legs 37b.

In the compressor 100 to which the above technology is applied, the flow in the annular member upper space 60 is a swirling flow, and if the intention is to return the oil to the oil reservoir space 5, such as shown in FIG. It is not limited to a vertical scroll compressor having a compliant frame. The compressor 100 to which the above technology is applied may be a vertical scroll compressor that does not have a compliant frame.

Embodiment 2.
Embodiment 2 relates to a refrigeration cycle apparatus such as an air conditioner in which compressor 100 of Embodiment 1 is mounted.

FIG. 7 is a schematic configuration diagram of a refrigeration cycle apparatus according to Embodiment 2. FIG. The refrigeration cycle device 200 includes a compressor 100 , a four-way switching valve 103 connected to the discharge side of the compressor 100 , and an outdoor heat exchanger 104 . The refrigeration cycle device 200 further includes a decompressor 105 a and a decompressor 105 b such as electric expansion, an indoor heat exchanger 106 , and a gas-liquid separator 107 . The refrigerating cycle device 200 forms a refrigerating circuit in which these devices are sequentially connected via pipes. Outdoor heat exchanger 104 and indoor heat exchanger 106 function as condensers or evaporators by switching four-way switching valve 103 . The four-way switching valve 103 can be omitted in the refrigeration cycle device 200 . Therefore, the refrigeration cycle device 200 may be configured to include the compressor 100 , the condenser, the pressure reducer, the evaporator, and the gas-liquid separator 107 .

The gas-liquid separator 107 separates the inflowing two-phase refrigerant into saturated gas refrigerant and saturated liquid refrigerant. The gas-liquid separator 107 has an injection pipe 110, which is a gas outflow pipe for discharging the separated saturated gas refrigerant to the outside. A downstream end of the injection pipe 110 is connected to the compressor 100 . An on-off valve 111 for opening and closing the injection pipe 110 is connected to the injection pipe 110 .

In heating operation when the refrigeration cycle device 200 is applied to, for example, an air conditioner, the four-way switching valve 103 is connected to the solid line side in FIG. The high-temperature, high-pressure refrigerant compressed by the compressor 100 flows into the indoor heat exchanger 106, where it is condensed and liquefied. After that, the two-phase refrigerant flows into the gas-liquid separator 107 . The saturated liquid refrigerant separated by the gas-liquid separator 107 passes through the pressure reducer 105a, flows to the outdoor heat exchanger 104, evaporates, and is gasified. The gasified refrigerant passes through the four-way switching valve 103 and returns to the compressor 100 again. That is, in heating operation, the refrigerant circulates as indicated by the solid line arrows in FIG. Due to this circulation, the refrigerant exchanges heat with the outside air in the outdoor heat exchanger 104, which is an evaporator, and absorbs heat. The refrigerant that has absorbed heat is sent to the indoor heat exchanger 106, which is a condenser, and exchanges heat with the indoor air to warm the indoor air.

In cooling operation when the refrigeration cycle device 200 is applied to, for example, an air conditioner, the four-way switching valve 103 is connected to the dashed line side in FIG. The high-temperature and high-pressure refrigerant compressed by the compressor 100 flows to the outdoor heat exchanger 104, is condensed and liquefied, and is then decompressed by the pressure reducer 105a into a low-temperature and low-pressure two-phase state. influx. The saturated liquid refrigerant separated by the gas-liquid separator 107 flows through the pressure reducer 105b to the indoor heat exchanger 106, where it evaporates and gasifies. The gasified refrigerant passes through the four-way switching valve 103 and returns to the compressor 100 again. That is, in the cooling operation, the refrigerant circulates as indicated by the dashed arrows in FIG. Due to this circulation, the refrigerant exchanges heat with indoor air in the indoor heat exchanger 106, which is an evaporator, and absorbs heat from the indoor air. This cools the indoor air. The refrigerant that has absorbed heat is sent to the outdoor heat exchanger 104, which is a condenser, exchanges heat with the outside air, and radiates heat to the outside air.

By including the compressor 100 of Embodiment 1, the refrigeration cycle apparatus 200 configured in this manner can reduce the amount of oil rising from the compressor 100 and improve reliability. Moreover, the refrigerant circuit of FIG. 7 is a refrigerant circuit having pressure reducers on both upstream and downstream sides of the gas-liquid separator 107 and using the gas-liquid separator 107 at an intermediate pressure. In such a refrigerant circuit, an excessive amount of oil exists in the gas-liquid separator 107, and it is considered that an oil return device is required to prevent the excessive oil from being returned to the sealed container 1. Since the refrigerating cycle device 200 includes the compressor 100 described above, the oil can be positively returned to the oil reservoir space 5 inside the compressor, so an oil return device is unnecessary.

It should be noted that the refrigeration cycle device 200 can be applied to a refrigerator, a freezer, a refrigerating device, a water heater, etc., in addition to the air conditioner.

1 closed vessel, 2 compression mechanism, 2b compression chamber, 3 oscillating scroll, 3a oscillating spiral body, 3b oscillating bed plate, 3c boss, 3d thrust surface, 3e bleeding hole, 3ei bleed inlet, 3eo bleed outlet, 4 Fixed scroll, 4a Fixed scroll, 4b Fixed base plate, 5 Oil reservoir space, 6 High pressure gas atmosphere, 7 Suction pipe, 8 Suction side space, 9 Suction check valve, 10 Spring, 11 Discharge pipe, 12 Discharge port, 14 Gas introduction passage 15a Fixed side Oldham ring groove 15b Swing side Oldham ring groove 16 Electric motor 16a Electric motor rotor 16b Electric motor stator 17a Penetration passage 17b Penetration passage 17c Minute gap 18a Balance weight, 18b balance weight, 19 drive shaft, 20 main shaft, 21 swing shaft, 22 sub shaft, 23 oil supply passage, 24 a supply passage, 24 b supply passage, 25 main bearing, 26 swing bearing, 27 sub bearing, 28 thrust bearing , 29 holder, 30 guide frame, 30a upper fitting cylindrical surface, 30b lower fitting cylindrical surface, 30c flow path, 31 compliant frame, 32a compliant frame upper space, 32b intermediate pressure space, 33 thrust surface, 34 compliant Frame lower end surface 35a Upper fitting cylindrical surface 35b Lower fitting cylindrical surface 36a Upper annular seal member 36b Lower annular seal member 37 Subframe 37a Cylindrical part 37b Fixed leg 37c Wall surface 37c1 Wall surface , 37c2 Inclined surface, 37c3 Lower edge, 38 Boss outer space, 39a Intermediate pressure regulating valve, 39c Intermediate pressure regulating spring, 39d Intermediate pressure regulating valve space, 39e Penetrating flow path, 40 Oldham ring, 41 Reciprocating sliding surface, 42a Fixed side key 42b Swing side key 50 Annular member 51 Through hole 52 Passing hole 55 Capturing channel 60 Annular member upper space 100 Compressor 103 Four-way switching valve 104 Outdoor heat exchanger , 105a decompressor, 105b decompressor, 106 indoor heat exchanger, 107 gas-liquid separator, 110 injection pipe, 111 on-off valve, 200 refrigeration cycle device.

Claims

A closed container having an oil reservoir space at the bottom, a compression mechanism disposed in the closed container for compressing a refrigerant, an electric motor disposed below the compression mechanism, and a rotational force of the electric motor applied to the compression mechanism. A compressor comprising: a drive shaft that transmits power to a part; and a frame that is arranged below the electric motor and supports the drive shaft,
a plate-shaped annular member having a through hole through which the drive shaft passes, the drive shaft being passed through the through hole, and attached to the lower part of the frame;
the frame has a plurality of fixed legs extending in the axial direction of the drive shaft and in the radial direction of the drive shaft and fixed to the closed container;
The annular member is formed with the same number of passage holes as the plurality of fixed leg portions, through which the refrigerant above the annular member passes below the annular member,
the plurality of passage holes are formed on a side opposite to the rotation direction of the electric motor with respect to the plurality of fixed legs,
A compressor in which a wall surface of each of the plurality of fixed legs on the side opposite to the rotational direction serves as an air guide wall that guides the refrigerant above the annular member to each of the plurality of passage holes.
The compressor according to claim 1, wherein the wall surfaces of the plurality of fixed legs are sloped surfaces that slope upward toward the side opposite to the direction of rotation.
The compressor according to claim 1 or claim 2, wherein the plurality of passage holes are provided in contact with lower edges of the wall surfaces of the plurality of fixed leg portions.
The compressor according to any one of claims 1 to 3, wherein the angle θ of the wall surface with respect to the annular member satisfies 60°<θ<90°.
The area of the flow path surrounded by the end of the wall surface opposite to the rotation direction and the end of the passage hole opposite to the rotation direction is S1, and the area of the passage hole is S2. The compressor according to any one of claims 1 to 4, wherein S1>S2 is satisfied when .
The frame has a cylindrical portion through which the drive shaft passes,
The compression according to any one of claims 1 to 5, wherein the plurality of fixed leg portions are three, and are provided on the outer peripheral surface of the cylindrical portion at equal intervals in the circumferential direction of the drive shaft. machine.
A refrigeration cycle apparatus comprising the compressor according to any one of claims 1 to 6, a condenser, a pressure reducer, and an evaporator.