WO2022224420A1

WO2022224420A1 - Compressor and refrigeration cycle device

Info

Publication number: WO2022224420A1
Application number: PCT/JP2021/016384
Authority: WO
Inventors: 貴彦村上; 貴也木本
Original assignee: 三菱電機株式会社
Priority date: 2021-04-23
Filing date: 2021-04-23
Publication date: 2022-10-27
Also published as: JPWO2022224420A1; JP7080423B1

Abstract

A compressor according to the present disclose comprises: a sealed container; a compression mechanism unit that is provided in the sealed container and that compresses a fluid; an electric motor unit that has a stator and a rotor and that is disposed above the compression mechanism unit in the sealed container; a drive shaft that is connected to the rotor and to a compression mechanism and that has a protrusion which protrudes from the upper part of the rotor; and a first oil separation member that is disposed at the upper end part of the protrusion of the drive shaft and that rotates together with the drive shaft. The first oil separation member has a collar part which protrudes in the radial directions of the drive shaft and at which a plurality of blades are provided in the vertical direction. In a plan view in which the first oil separation member is viewed from above, each of the blades is positioned such that: an outer circumference-side edge point is positioned on the outer circumference of the collar part; an inner circumference-side edge point is on a circle that is concentric with and inward of the outer circumference and is positioned at a right angle to a straight line which connects the outer circumference-side edge point of the blade and the center of the concentric circle; and a shadow made by projecting the blade in the horizontal direction does not overlap with an adjacent blade.

Description

Compressor and refrigeration cycle equipment

This technology relates to compressors and refrigeration cycle equipment. In particular, the present invention relates to a hermetic compressor having an oil separation member inside.

Among compressors that compress fluid, hermetic compressors often have a structure in which refrigerating machine oil is stored at the bottom of a hermetic container. Refrigerating machine oil lubricates the drive of the equipment and serves as a lubricating oil that prevents wear. Refrigerant oil is supplied to the bearings and the compression mechanism. The refrigerating machine oil supplied to the bearings lubricates the bearings, and then is discharged out of the compressor together with the fluid from the bearing sliding portions. In addition, the refrigerating machine oil supplied to the compression mechanism functions as a seal between gaps to suppress the frictional force of the piston and prevent fluid from leaking, and is discharged out of the compressor together with the fluid. Therefore, the discharged fluid contains the refrigerating machine oil supplied to the bearings and the compression mechanism.

Here, a case where a compressor is used in a refrigeration cycle device having a refrigerant circuit will be described. In a refrigerant circuit that circulates a fluid refrigerant, if the amount of refrigerating machine oil that flows out of the compressor increases, the amount of refrigerating machine oil that adheres to the inside of the heat exchanger increases. A decrease in efficiency of the refrigeration cycle due to a decrease in performance and an increase in pressure loss occurs. Further, when the amount of refrigerating machine oil flowing out of the compressor increases, the amount of refrigerating machine oil stored in the compressor decreases, which causes poor lubrication of sliding parts. Therefore, it is necessary to efficiently separate the refrigerant and the refrigerating machine oil within the compressor in order to suppress an increase in the refrigerating machine oil flowing out of the compressor.

Therefore, in some conventional compressors, an oil separating member is installed on the drive shaft that connects the compression mechanism and the electric motor to prevent the refrigerating machine oil from flowing out of the compressor. For example, a donut-shaped (hollow disk-shaped) plate member is bent at a plurality of locations on the outer peripheral portion to form wing portions, and an oil separating member that has a polygonal shape in plan view is provided on the drive shaft. A machine has been proposed (see, for example, Patent Document 1).

Japanese Patent No. 4964288

The oil separation member in the compressor of Patent Document 1 separates the refrigerant and the refrigerating machine oil by the centrifugal separation effect and the effect of the flow velocity gradient in the vicinity of the blades of the oil separation member. Therefore, when the capacity and flow rate of the compressor are increased, the blades are positioned on the outer periphery, and the oil separation effect at the blades is reduced.

Therefore, the object is to obtain a compressor and a refrigeration cycle device having a structure with a higher oil separation effect regardless of the capacity of the compressor.

A compressor according to this disclosure includes a closed container, a compression mechanism provided in the closed container for compressing a fluid, a stator and a rotor, and disposed above the compression mechanism in the closed container. A drive shaft connected to an electric motor section, a rotor and a compression mechanism and having a projection projecting from the top of the rotor, and a first oil disposed on the upper end portion of the projection of the drive shaft and rotating together with the drive shaft. The first oil separation member protrudes in the radial direction of the drive shaft and has a flange on which a plurality of blades are installed in the vertical direction. In a plan view when the oil separation member 1 is viewed from above, the outer peripheral side end point is located on the outer periphery of the flange portion, the inner peripheral side end point is inside the outer periphery and concentric with the outer periphery, and is on the outer peripheral side of the blade. It is positioned at a right angle to the straight line connecting the end point and the center of the concentric circle, and at a position where the shadow of the blade projected in the horizontal direction does not overlap the adjacent blade.

A refrigeration cycle apparatus according to this disclosure has a refrigerant circuit in which the compressor, condenser, decompression device, and evaporator described above are connected by piping, and refrigerant is circulated.

In the present disclosure, the compressor has a first oil separation member arranged at the upper end portion of the protrusion of the drive shaft and rotating together with the drive shaft. The first oil separating member has a plurality of blades in the vertical direction on the flange. The blade has an outer peripheral side end point and an inner peripheral side end point located from the outer peripheral side to the inner peripheral side of the flange portion. Therefore, even if the capacity and flow rate of the compressor are increased, the refrigerating machine oil can be efficiently separated from the refrigerant by generating a swirling flow with the blades extending from the outer peripheral side to the inner peripheral side of the flange.

1 is a diagram illustrating a configuration of a compressor 100 according to Embodiment 1; FIG. Fig. 2 is an enlarged view of a main portion near the upper portion of compressor 100 according to Embodiment 1; FIG. 3 is a side view of the first oil separating member 5 according to Embodiment 1 when viewed from the side of the compressor 100; 2 is a plan view of the first oil separating member 5 according to Embodiment 1 when viewed from the direction of the upper surface of the compressor 100. FIG. FIG. 4 is a diagram for explaining the flow of refrigerant inside the compressor 100 according to Embodiment 1; FIG. 3 is a diagram for explaining the flow of refrigerant inside a conventional compressor 101; FIG. 11 is a plan view of the first oil separating member 5 according to Embodiment 2 when viewed from the direction of the upper surface of the compressor 100; FIG. 11 is an enlarged view of a main portion near the upper portion of compressor 100 according to Embodiment 3; FIG. 11 is a diagram showing a configuration example of a refrigeration cycle apparatus according to Embodiment 4;

A compressor and a refrigeration cycle device according to an embodiment will be described below with reference to the drawings. In the following drawings, the same reference numerals denote the same or corresponding parts, and are common throughout the embodiments described below. The forms of the constituent elements shown in the entire specification are merely examples, and are not limited to the forms described in the specification. In particular, the combination of components is not limited only to the combinations in each embodiment, and the components described in other embodiments can be applied to other embodiments. Also, in the following description, the upper side of the drawing is referred to as the "upper side" and the lower side is referred to as the "lower side". Furthermore, for ease of understanding, directional terms (e.g., "right", "left", "front", "back", etc.) are used as appropriate; The terminology is not intended to limit the claimed invention. In addition, in the drawings, the size relationship of each component may differ from the actual size.

Embodiment 1.
FIG. 1 is a diagram illustrating the configuration of a compressor 100 according to Embodiment 1. FIG. FIG. 1 shows a schematic longitudinal section to show the internal configuration of the compressor 100 . Moreover, FIG. 2 is an enlarged view of a main portion near the upper portion of the compressor 100 according to Embodiment 1. As shown in FIG. Here, in each drawing described below, such as the compressor 100 shown in FIG. 1, there are portions where hatching is omitted to make the portions to be described easier to see.

The compressor 100 sucks fluid, compresses it, and discharges it. Although not particularly limited, the fluid compressed by the compressor 100 is the refrigerant circulating in the refrigerant circuit in the refrigeration cycle device. Compressor 100 of Embodiment 1 is a hermetic compressor. The compressor 100 has a compression mechanism section 1 and an electric motor section 10 inside a substantially cylindrical sealed container 11 . Also, the sealed container 11 of the compressor 100 has a discharge pipe 7 for discharging the refrigerant on its upper surface.

The electric motor section 10 has a motor that receives power supply from an external power source (not shown), drives it to rotate, and rotates the compression mechanism section 1 . The electric motor section 10 has a stator 2 and a rotor 3 . The stator 2 has a hollow cylindrical shape. The outer peripheral portion of the electric motor portion 10 is press-fitted into the inner wall of the closed container 11 . The stator 2 is configured, for example, by laminating a plurality of steel plates such as electromagnetic steel plates. In addition, the stator 2 has, for example, distributed winding coils 2a in the grooves of the inner circumference. The coil 2a is connected to a terminal 12 and receives power through the terminal 12. As shown in FIG.

The rotor 3 has a hollow cylindrical shape. The rotor 3 is arranged inside the stator 2 . When the rotor 3 is arranged inside the stator 2 , a slight gap is formed between the outer peripheral surface of the rotor 3 and the inner peripheral surface of the stator 2 . The rotor 3 is configured by laminating a plurality of steel plates such as electromagnetic steel plates. The rotor 3 has vertical through-holes 3a through which a coolant flows. A drive shaft 4 is inserted in the center of the rotor 3 . The drive shaft 4 is connected at its lower end to the compression mechanism 1, which will be described later. Further, the drive shaft 4 has an upper end projecting from the upper portion of the rotor 3 . Hereinafter, the protruding portion at the upper end of the drive shaft 4 will be referred to as a protruding portion 4a.

The compression mechanism section 1 compresses the fluid sucked into the sealed container 11 . Compression mechanism section 1 of Embodiment 1 is, for example, a rotary compression mechanism. In Embodiment 1, a two-cylinder rotary compression mechanism is used. However, the compression mechanism section 1 is not limited to the configuration described above. For example, a single-cylinder rotary compression mechanism, a scroll compression mechanism, or the like may be used.

The compression mechanism 1 of Embodiment 1 is composed of devices such as a cylinder 13a, a rotary piston (rolling piston) 13b provided in the cylinder 13a, a cylinder 14a, and a rotary piston 14b provided in the cylinder 14a. The rotary piston 13b and the rotary piston 14b are connected to eccentric shaft portions of the drive shaft 4, respectively. A suction pipe 15 is connected to a compression chamber formed between the cylinder 13a and the rotary piston 13b. A suction pipe 16 is connected to a compression chamber formed between the cylinder 14a and the rotary piston 14b. The intake pipe 15 and the intake pipe 16 are connected to the muffler 17 . The suction pipe 15 and the suction pipe 16 are pipes that allow the low-pressure gas refrigerant to flow into the sealed container 11 . The muffler 17 is a muffler that reduces or eliminates noise generated by refrigerant flowing from the

suction pipes

15 and 16 .

In addition, when the drive shaft 4 rotates, the compression mechanism 1 is supplied with the refrigerating machine oil stored in the lower portion of the sealed container 11 through an oil supply path (not shown) formed in the drive shaft 4. A first oil separating member 5 and a second oil separating member 6 are provided on the projecting portion 4 a of the drive shaft 4 .

FIG. 3 is a side view of the first oil separating member 5 according to Embodiment 1 when viewed from the side of the compressor 100. FIG. Moreover, FIG. 4 is a plan view of the first oil separation member 5 according to Embodiment 1 when viewed from the direction of the upper surface of the compressor 100 . As shown in FIGS. 3 and 4, the first oil separation member 5 has a cup portion 5a, a brim portion 5b, blade portions 5c and a flange 5d. The cup portion 5a has a substantially cup shape whose diameter increases from the lower portion, which is the connection portion with the drive shaft 4, toward the upper portion. The flange portion 5b is a substantially donut-shaped (hollow disk-shaped) plate member. The brim portion 5b is provided at the upper end portion of the cup portion 5a. Therefore, the flange portion 5b projects in the radial direction of the drive shaft 4. As shown in FIG. The flange 5d is a member having a substantially hollow cylindrical shape and is provided at the lower end of the cup portion 5a. The first oil separation member 5 is connected to the protrusion 4a by inserting the flange 5d into the protrusion 4a of the drive shaft 4 by press fitting or the like. Here, although the first oil separation member 5 in Embodiment 1 is described as having the cup portion 5a, the cup portion 5a is not essential. For example, the first oil separating member 5 without the cup portion 5a has a configuration in which the flange portion 5b and the flange 5d are directly connected.

Further, the blade portion 5c has a plurality of blades. As shown in FIG. 4, when the first oil separation member 5 is viewed from the top of the compressor 100 in a plan view, each blade of the blade portion 5c has a flange portion 5b. are located on the outer periphery of the flange portion 5b and on concentric circles inside the outer periphery of the flange portion 5b. Here, the endpoint on the outer circumference side of the blade is defined as the endpoint on the outer circumference side, and the endpoint located on the inner concentric circle is defined as the endpoint on the inner circumference side. Further, in the blades of the first oil separating member 5 in Embodiment 1, the inner peripheral side endpoint is located at a right angle to the straight line connecting the outer peripheral circle side endpoint of the blade portion 5c and the center of the concentric circle (on the straight line ), and when the blade is horizontally projected from the side surface, the shadow projected by the adjacent blade portion 5c does not overlap.

The outer diameter R of the flange portion 5b of the first oil separation member 5 in the state where the blade portion 5c is not provided is substantially the same as the outer diameter of the rotor 3. Therefore, the outer diameter R of the flange portion 5b is large enough to cover the through hole 3a of the rotor 3 in plan view. Therefore, even if the compressor 100 is not provided with the second oil separation member 6, the refrigerant flowing out from the through hole 3a of the rotor 3 can more reliably contact the cup portion 5a and the flange portion 5b. can be done. Therefore, the first oil separating member 5 can more reliably separate the refrigerating machine oil from the refrigerant flowing out from the through holes 3 a of the rotor 3 .

Also, the second oil separation member 6 shown in FIGS. 1 and 2 is a substantially doughnut-shaped plate member installed between the first oil separation member 5 and the rotor 3 . The second oil separating member 6 also separates the refrigerating machine oil from the refrigerant. The second oil separation member 6 has a disk portion 6a and a flange 6b. The disc portion 6a is a substantially doughnut-shaped plate member. The outer diameter of the disk portion 6a is substantially the same as the outer diameter of the rotor 3. As shown in FIG. Therefore, the outer diameter of the disk portion 6a is large enough to cover the through hole 3a of the rotor 3 in plan view. This is to ensure that the coolant flowing out of the through-holes 3a of the rotor 3 comes into contact with the disk portion 6a. By covering the through hole 3 a of the rotor 3 with the disk portion 6 a of the second oil separation member 6 , the refrigerating machine oil can be separated more reliably from the refrigerant flowing out from the through hole 3 a of the rotor 3 . The flange 6b has a substantially hollow cylindrical shape and is provided below the disk portion 6a. The second oil separating member 6 is connected to the projecting portion 4a by inserting (for example, press-fitting) the flange 6b into the projecting portion 4a. Here, the second oil separating member 6 in Embodiment 1 is a substantially doughnut-shaped plate member, but the shape is not limited to this. For example, the second oil separating member 6 may be substantially cup-shaped. Also, here, the compressor 100 is described as having the second oil separation member 6, but the second oil separation member 6 is not essential. The compressor 100 may have only the first oil separating member 5 .

Here, the positional relationship between the first oil separation member 5 and the second oil separation member 6 will be explained. Compressor 100 in Embodiment 1 sets the lengths of

flanges

5d and 6b of first oil separation member 5 and second oil separation member 6, for example. In a state where the first oil separation member 5 and the second oil separation member 6 are provided on the projecting portion 4a, the lower end portion of the flange 6b of the second oil separation member 6 and the upper portion of the rotor 3 are in contact with each other. to Also, the lower end portion of the flange 5d of the first oil separation member 5 and the upper portion of the disk portion 6a of the second oil separation member 6 are brought into contact with each other. The lengths of the

flanges

5d and 6b are set, and the first oil separation member 5 and the second oil separation member 6 are attached to the drive shaft 4 corresponding to the

flanges

5d and 6b. Therefore, it becomes easy to dispose the first oil separation member 5 and the second oil separation member 6 at desired positions.

First, the height of the upper end portion of the blade portion 5c, which is the upper end portion of the first oil separation member 5, is approximately the same as the height of the upper end portion of the coil 2a wound around the stator 2. For example, the height difference between the two is ±5 mm. Further, the first oil separation member 5 and the discharge pipe 7 are such that the distance between the upper end of the vane portion 5c of the first oil separation member 5 and the inlet port 7a of the discharge pipe 7 is equal to or less than the radius of the flange portion 5b. , the discharge pipe 7 and the first oil separating member 5 are arranged in a positional relationship such that they do not come into contact with each other.

FIG. 5 is a diagram explaining the flow of refrigerant inside the compressor 100 according to the first embodiment. FIG. 6 is a diagram for explaining the flow of refrigerant inside the conventional compressor 101. As shown in FIG. A conventional compressor 101 shown in FIG. 6 does not include the first oil separation member 5, and has a hollow disc-shaped plate member having the same shape as the second oil separation member 6 in the compressor 101. The oil separating member 106 is provided on the projecting portion 4a of the drive shaft 4. As shown in FIG.

A current flows from an external power supply (not shown) to the coil 2a of the stator 2 via the terminal 12. A magnetic field is generated by a current flowing through the coil 2a. The generated magnetic field causes the rotor 3 and the drive shaft 4 to rotate. As the drive shaft 4 rotates, the rotary piston 13b and the rotary piston 14b also rotate. As a result, the volume of the compression chamber in the compression mechanism portion 1 is reduced, and the refrigerant sucked from the

suction pipes

15 and 16 is compressed. The compressed refrigerant is discharged into the space between the compression mechanism portion 1 and the electric motor portion 10 . The refrigerant discharged into the space between the compression mechanism portion 1 and the electric motor portion 10 mainly passes through the through holes 3 a of the rotor 3 and flows out to the upper portion of the electric motor portion 10 .

For example, in the case of conventional compressor 101, as shown in FIG. direction is changed. At this time, the refrigerating machine oil mixed in the refrigerant is separated by the centrifugal separation effect of the oil separation member 106 . The separated refrigerator oil adheres to or collides with the coil ends of the stator 2, the inner wall of the closed container 11, and the like. The refrigerating machine oil that has collided with the equipment flows to the bottom of the sealed container 11 through gaps in the equipment and is returned.
Here, if the distance between the oil separation member 106 and the rotor 3 is too long and the position where the flow direction of the refrigerant is changed is too high, the refrigerant that has flowed out of the through holes 3a spread to Therefore, the refrigerant existing near the inlet 7a of the discharge pipe 7 has a high concentration of refrigerating machine oil. Further, if the distance between the oil separation member 106 and the rotor 3 is too short, the oil separation member 106 cannot sufficiently centrifuge the refrigerant present near the inlet 7a of the discharge pipe 7 . Therefore, the refrigerant present near the inlet 7a of the discharge pipe 7 has a high concentration of refrigerating machine oil.

In the case of the compressor 100 according to Embodiment 1, as shown in FIG. 11 in the outer peripheral direction toward the inner wall. At this time, the refrigerating machine oil mixed in the refrigerant is separated by the centrifugal separation effect of the second oil separation member 6 .

The refrigerant flows into the first oil separation member 5 provided near the inlet 7a of the discharge pipe 7. The first oil separation member 5 rotates together with the drive shaft 4, and a swirling flow is generated in the vicinity of the blade portion 5c. In the first oil separating member 5, the blades of the blade portion 5c have a larger area for pushing away the refrigerant, thereby increasing the swirl flow velocity. and the refrigerating machine oil mixed in the refrigerant can be separated. The first oil separation member 5 exerts a centrifugal separation effect due to a greater centrifugal force due to the swirling flow, and separates the refrigerating machine oil that has not been separated from the refrigerant in the second oil separation member 6 . Therefore, the compressor 100 according to Embodiment 1 further improves the oil separation effect as compared with the conventional compressor 101 .

As described above, the compressor 100 according to the first embodiment has the hollow disk-shaped collar portion 5b extending in the radial direction of the drive shaft 4 and the blade portions 5c standing upright from the collar portion 5b. It comprises a rotating first oil separation member 5 . As the first oil separation member 5 rotates together with the drive shaft 4 , the refrigerating machine oil can be separated from the refrigerant that has flowed into the first oil separation member 5 by a swirling flow generated in the vicinity of the vanes 5 c. Then, the separated refrigerating machine oil receives a swirling flow, is sprayed against the inner wall of the sealed container 11 by centrifugal force, stops there, drips from there, and is efficiently recovered and collected in the lower part of the sealed container 11. - 特許庁

In addition, the first oil separation member 5 can be simplified in configuration by integrally forming the flange portion 5b and the blades of the blade portion 5c.

Furthermore, the outer diameter of the hollow disc-shaped flange portion 5b (more specifically, the outer diameter of the portion of the blade portion 5c that is connected to the blades in the blade portion 5b) is ± It has a diameter within 5% and is approximately the same diameter. Therefore, the outer diameter of the flange portion 5b is large enough to cover the through hole 3a of the rotor 3 in a plan view of the compressor 100 viewed from above. As a result, the refrigerating machine oil can be more reliably separated from the refrigerant flowing out from the through holes 3 a of the rotor 3 . Moreover, the difference in the vertical direction between the upper end of the blade of the blade 5c of the first oil separating member 5 and the upper end of the coil 2a of the stator 2 is within ±5 mm. Therefore, the refrigerating machine oil can be separated more reliably.

In the compressor 100 according to Embodiment 1, the first oil separation member 5 is such that the vertical distance between the blades of the blade portion 5c and the inlet port 7a of the discharge pipe 7 of the closed container 11 is equal to the flange portion 5b. , and positioned within a range that does not come into contact with the discharge pipe 7. Therefore, a larger amount of refrigerant from which the first oil separating member 5 has separated the refrigerating machine oil can be discharged from the discharge pipe 7 .

Compressor 100 in Embodiment 1 can exert a centrifugal separation effect with only first oil separation member 5 , but between first oil separation member 5 and rotor 3 together with drive shaft 4 It has a rotating hollow disc-shaped second oil separation member 6 . The first oil separating member 5 swirls the refrigerant from which the second oil separating member 6 has separated the refrigerating machine oil, and further separates the refrigerating machine oil.

In addition, since the compressor 100 has the second oil separation member 6, the first oil separation member 5 can be installed near the inflow port 7a of the discharge pipe 7. Therefore, the effect of separating the refrigerating machine oil can be further enhanced.

Further, the outer diameter of the disk portion 6a of the hollow disk-shaped second oil separating member 6 is within ±5% of the outer diameter of the rotor 3 in a plan view of the compressor 100 viewed from above. diameter. Therefore, the outer diameter of the disc portion 6a is large enough to cover the through hole 3a of the rotor 3 in a plan view of the compressor 100 viewed from above. As a result, the refrigerating machine oil can be separated from the refrigerant flowing out from the through holes 3 a of the rotor 3 .

The first oil separation member 5 and the second oil separation member 6 have

flanges

5d and 6b, respectively. Then, the lower end of the flange 6b and the upper portion of the rotor 3 are brought into contact with each other, and the lower end of the flange 5d and the upper surface of the second oil separation member 6 are brought into contact with each other. Set to specified length. Therefore, it becomes easy to dispose the first oil separation member 5 and the second oil separation member 6 at desired positions.

Embodiment 2.
FIG. 7 is a plan view of the first oil separation member 5 according to Embodiment 2 when viewed from the direction of the upper surface of the compressor 100. FIG. As shown in FIG. 7, the first oil separating member 5 in Embodiment 2 has one or more bending points 5e in the blade portion 5c, and has blades bent at the bending points 5e.

The surface area is increased by bending the blades at one or more bending points 5e. Further, the blades having a concave shape in the direction of rotation can receive the refrigerant discharged by the rotation. Therefore, the first oil separation member 5 can increase the swirling flow velocity due to rotation. Therefore, the centrifugal separation effect of the refrigerating machine oil can be further enhanced.

Embodiment 3.
FIG. 8 is an enlarged view of a main portion near the upper portion of compressor 100 according to Embodiment 3. As shown in FIG. In the compressor 100 of Embodiment 3, the inlet port 7a of the discharge pipe 7 installed on the upper surface of the closed container 11 is positioned between the upper end portion and the lower end portion of the blades of the blade portion 5c in the vertical direction. The first oil separating member 5 and the discharge pipe 7 are arranged as shown. As a result, a greater amount of the refrigerant from which the first oil separating member 5 has separated the refrigerating machine oil can be discharged from the discharge pipe 7 .

Embodiment 4.
FIG. 9 is a diagram illustrating a configuration example of a refrigeration cycle apparatus according to Embodiment 4. FIG. Here, FIG. 9 shows an air conditioner as the refrigeration cycle device. In the air conditioner of FIG. 9, an outdoor unit 300 and an indoor unit 200 are connected by a refrigerant pipe 400 to form a refrigerant circuit for circulating the refrigerant. Outdoor unit 300 has compressor 100 described in the first embodiment. The outdoor unit 300 also has a four-way valve 302 , an outdoor heat exchanger 303 , an expansion valve 304 and an outdoor fan 305 . Also, the indoor unit 200 has an indoor heat exchanger 201 .

The compressor 100 compresses and discharges the sucked refrigerant, as described above. Here, although not particularly limited, the compressor 100 may arbitrarily change the operating frequency by, for example, control by an inverter circuit. The four-way valve 302 is a valve that switches the flow of refrigerant between cooling operation and heating operation.

The outdoor heat exchanger 303 exchanges heat between refrigerant and air (outdoor air). Outdoor heat exchanger 303 functions, for example, as an evaporator during heating operation to evaporate and vaporize the refrigerant. Also, the outdoor heat exchanger 303 functions as a condenser during cooling operation, and condenses and liquefies the refrigerant. In addition, the outdoor fan 305 sends outdoor air to the outdoor heat exchanger 303 to promote heat exchange between the outdoor air and the refrigerant.

An expansion valve 304 such as a throttle device, which serves as a decompression device, decompresses and expands the refrigerant. For example, if the expansion valve 304 is composed of an electronic expansion valve or the like, the opening is adjusted based on an instruction from a control device (not shown) or the like. Indoor heat exchanger 201 performs heat exchange between, for example, air to be air-conditioned and refrigerant. Indoor heat exchanger 201 functions as a condenser during heating operation, and condenses and liquefies the refrigerant. In addition, the indoor heat exchanger 201 functions as an evaporator during cooling operation to evaporate and vaporize the refrigerant. The indoor blower 202 sends air to be air-conditioned to the indoor heat exchanger 201 to promote heat exchange between the air and the refrigerant.

As described above, according to the refrigeration cycle apparatus of Embodiment 4, by having the compressor 100 described in Embodiment 1 as a device, it is possible to improve the oil separation effect of separating the refrigerating machine oil from the refrigerant. . Therefore, the amount of refrigerating machine oil discharged from the compressor 100 is reduced, and it is possible to prevent the refrigerating machine from interfering with the heat transfer of the refrigerant in the heat exchanger. Therefore, the heat exchange efficiency can be increased, and the efficiency in the refrigerant circuit can be improved.

1 compression mechanism, 2 stator, 2a coil, 3 rotor, 3a through hole, 4 drive shaft, 4a protrusion, 5 first oil separation member, 5a cup, 5b flange, 5c blade, 5d flange , 5e bending point, 6 second oil separation member, 6a disk portion, 6b flange, 7 discharge pipe, 7a inlet, 10 electric motor portion, 11 sealed container, 12 terminal, 13a cylinder, 13b rotary piston, 14a cylinder, 14b rotary piston, 15 suction pipe, 16 suction pipe, 17 muffler, 100 compressor, 101 compressor, 200 indoor unit, 201 indoor heat exchanger, 202 indoor blower, 300 outdoor unit, 302 four-way valve, 303 outdoor heat exchanger , 304 Expansion valve, 305 Outdoor fan, 400 Refrigerant piping.

Claims

a closed container;
a compression mechanism provided in the sealed container for compressing the fluid;
an electric motor section having a stator and a rotor and arranged above the compression mechanism section in the closed container;
a drive shaft connected to the rotor and the compression mechanism and having a protrusion projecting from an upper portion of the rotor;
a first oil separation member arranged at the upper end portion of the protrusion of the drive shaft and rotating together with the drive shaft,
The first oil separation member is
Having a flange projecting in the radial direction of the drive shaft and having a plurality of blades installed in the vertical direction,
In a plan view of the first oil separation member viewed from above, each blade has an outer peripheral end point located on the outer periphery of the flange portion, and an inner peripheral end point located inside the outer periphery. is on a concentric circle and is at a position perpendicular to a straight line connecting the outer peripheral side end point of the blade and the center of the concentric circle, and the shadow of the blade projected in the horizontal direction overlaps the adjacent blade Compressor to the position where it should not be.
The compressor according to claim 1, wherein the flange portion and the plurality of blades are composed of a single plate.
A discharge pipe is provided on the upper surface of the closed container and discharges the fluid compressed by the compression mechanism to the outside,
The first oil separation member is
3. The compressor according to claim 1, wherein the vertical distance between the upper ends of the blades and the inlet of the discharge pipe is equal to or less than the radius of the flange portion and is positioned within a range that does not come into contact with the discharge pipe. .
A discharge pipe is provided on the upper surface of the closed container and discharges the fluid compressed by the compression mechanism to the outside,
3. The compressor according to claim 1, wherein the inlet of the discharge pipe is positioned between the upper end and the lower end of the blade of the first oil separation member in the vertical direction.
the plurality of vanes,
In a plan view when the first oil separation member is viewed from above, one or more inflection points that are not located on a line connecting the outer peripheral side end point and the inner peripheral side end point are separated from the outer peripheral side end point and the inner peripheral side end point. 5. The compressor according to any one of claims 1 to 4, having between the side end points.
6. The compressor according to any one of claims 1 to 5, wherein the upper ends of the plurality of blades are located within ±5 mm of difference in the vertical direction from the upper ends of the coils wound around the stator. .
The outer diameter of the flange portion is within ±5% of the outer diameter of the rotor in plan view when the first oil separation member is viewed from above. 7. The compressor according to any one of 6.
8. The method according to any one of claims 1 to 7, wherein a second oil separation member is provided in a portion of the protruding portion of the drive shaft located between the rotor and the first oil separation member. Compressor as described.
The outer diameter of the second oil separation member is a hollow disk-shaped member having a diameter within ±5% of the outer diameter of the rotor in plan view when viewed from above. 9. Compressor according to 8.
The first oil separation member and the second oil separation member each have a flange at the bottom,
The lower end portion of the flange of the second oil separation member and the upper portion of the rotor are in contact with each other, and the lower end portion of the flange of the first oil separation member and the upper surface of the second oil separation member contact each other. 10. A compressor according to claim 8 or 9, wherein the contacts are in contact with each other.
A refrigeration cycle apparatus having a refrigerant circuit in which the compressor, condenser, decompression device, and evaporator according to any one of claims 1 to 10 are pipe-connected and the refrigerant is circulated.