WO2020148824A1

WO2020148824A1 - Compressor and refrigeration cycle device

Info

Publication number: WO2020148824A1
Application number: PCT/JP2019/001092
Authority: WO
Inventors: 克也前田
Original assignee: 三菱電機株式会社
Priority date: 2019-01-16
Filing date: 2019-01-16
Publication date: 2020-07-23

Abstract

This compressor is provided with a compressor body for compressing an oil-containing refrigerant and a cyclonic oil separator that separates the oil from refrigerant discharged from the compressor body. The oil separator is provided with: an outer cylinder section; a crown section fixed to the outer cylinder section and comprising a lid that covers an upper opening in the outer cylinder section, said lid having formed therein a discharge hole from which refrigerant is discharged after the oil is separated therefrom; and a valve body that is provided to the interior of the lid of the crown section and that is opened by the pressure of refrigerant rising in the interior of the lid toward the discharge hole.

Description

Compressor and refrigeration cycle device

The present invention relates to a compressor and a refrigeration cycle device equipped with an oil separator that separates oil from a refrigerant.

In the compressor, oil is supplied to the bearing and the compression chamber for the purpose of lubricating the bearing, cooling the compression heat, and sealing the gap. The oil supplied to each of these places is discharged from the compression chamber together with the compressed refrigerant gas. Therefore, an oil separator is provided downstream of the compression chamber, the oil and the refrigerant gas are separated by the oil separator, and the separated oil is supplied again to the bearing and the compression chamber.

Patent Document 1 discloses a compressor equipped with an oil separator. The oil separator of Patent Document 1 is composed of a double cylinder including an outer cylinder part and an inner cylinder part located inside the outer cylinder part, and is separated by centrifugal force by utilizing a difference in gas-liquid density. Oil and refrigerant gas are separated by a cyclone method. Specifically, the refrigerant gas containing oil flows into the oil separator and descends while swirling through the gap between the outer cylinder part and the inner cylinder part. At this time, the oil having a density higher than that of the refrigerant gas is blown to the inner peripheral surface of the outer cylinder portion by the centrifugal force and separated from the refrigerant gas. The separated oil flows down along the inner peripheral surface of the outer cylinder portion and collects in the lower portion of the oil separator. On the other hand, the refrigerant gas from which the oil has been separated rises inside the inner cylinder portion and is discharged to the outside from the discharge port provided in the lid that covers the upper openings of the outer cylinder portion and the inner cylinder portion. A check valve and a member that forms a moving space for the valve body of the check valve are provided in the middle of the flow path from the lower end opening of the inner cylindrical portion to the discharge port, and prevent the reverse flow of the refrigerant gas. ing.

JP, 2017-8810, A

In Patent Document 1, the member that forms the movement space of the valve body and the lid are formed as separate members, and the member that forms the movement space of the valve body is supported by the outer cylinder portion while being hooked by the lid. It is composed. Therefore, in Patent Document 1, the member forming the movement space of the valve body has a structure that is easily affected by vibration and the like, which may cause unstable operation of the valve body.

The present invention has been made in view of the above points, and an object of the present invention is to provide a compressor and a refrigeration cycle device that can stabilize the operation of the valve body.

The compressor according to the present invention includes a compressor main body that compresses a refrigerant containing oil, and a cyclone-type oil separator that separates oil from the refrigerant discharged from the compressor main body, and the oil separator is An outer cylinder part, and a lid part that covers the upper opening of the outer cylinder part and has a discharge port for discharging the refrigerant after oil separation, and a crown part fixed to the outer cylinder part; And a valve body which is provided inside the lid part of the portion and is opened by the pressure of the refrigerant that rises inside the lid part toward the discharge port.

According to the present invention, since the crown portion having the lid portion accommodating the valve body is fixed to the outer cylinder portion, the influence of vibration is reduced, and the influence of vibration acting on the valve body can be reduced. .. Therefore, according to the present invention, the operation of the valve body can be stabilized.

It is a cross-sectional schematic diagram of the compressor which concerns on Embodiment 1 of this invention. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. FIG. 3 is a structural explanatory view of oil separators having different check valve lift amounts in the compressor according to Embodiment 1 of the present invention. It is a figure which shows the modification 1 of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows the modification 2 of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows the modification 3 of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a figure which shows an example of the current plate of FIG. It is a schematic sectional drawing of the oil separator in the compressor which concerns on Embodiment 2 of this invention, and is the figure which partially expanded and was shown. It is a schematic sectional drawing of the oil separator in the compressor which concerns on Embodiment 3 of this invention. It is a schematic sectional drawing of the oil separator in the compressor which concerns on Embodiment 4 of this invention. It is a refrigerant circuit diagram of the refrigerating cycle device concerning Embodiment 5 of the present invention.

Hereinafter, embodiments of a compressor and a refrigeration cycle apparatus according to the present invention will be described with reference to the drawings. The present invention is not limited to these embodiments. Further, in each of the drawings, the same or corresponding parts are designated by the same reference numerals, and the description thereof will be omitted or simplified as appropriate. Further, regarding the configuration shown in each drawing, the shape, size, arrangement, etc. can be appropriately changed within the scope of the present invention.

Embodiment 1.
The compressor according to the first embodiment will be described with reference to FIGS.
1 is a schematic sectional view of a compressor according to Embodiment 1 of the present invention.
The compressor 1 according to the first embodiment includes a compressor body 10 and an oil separator 40. The oil separator 40 is fastened to the casing 11 of the compressor body 10 with bolts (not shown).

As shown in FIG. 1, the compressor body 10 includes a cylindrical casing 11, a motor 12 housed in the casing 11, a screw shaft 13 rotatably driven by the motor 12, and a screw shaft 13. And a screw rotor 14.

The side surface of the screw rotor 14 is provided with a pair of gate rotors 15 arranged so as to be symmetrical with respect to the screw shaft 13. A slide valve 16 is arranged between the side surface of the casing 11 and the screw rotor 14.

The motor 12 is composed of a stator 12a which is inscribed and fixed in the casing 11 and a motor rotor 12b which is arranged inside the stator 12a. The motor rotor 12b is fixed to the screw shaft 13 and is arranged on the same line as the screw rotor 14. An end of the screw shaft 13 on the side not fixed to the motor 12 is rotatably supported by a bearing 17. The rotation speed of the motor 12 can be changed by driving the inverter, and the compressor body 10 is driven by the inverter. The motor 12 may be a constant speed motor that rotates at a constant rotation speed.

The screw rotor 14 has a cylindrical shape, and a plurality of screw grooves 14a extending in a spiral shape from one end to the other end of the screw rotor 14 are formed on the outer peripheral surface. One end of the screw rotor 14 serves as a refrigerant gas suction side, and the screw groove 14a communicates with the suction pressure side. The other end side of the screw rotor 14 becomes the discharge side of the refrigerant gas, and the screw groove 14a communicates with the discharge pressure side. The inside of the casing 11 is divided by a partition wall 18 into a suction pressure side (right side in FIG. 1) filled with low-pressure refrigerant gas and a discharge pressure side (left side in FIG. 1) filled with high-pressure refrigerant gas.

The gate rotor 15 has a disk shape, and a plurality of tooth portions 15a are provided on the outer peripheral surface along the circumferential direction. The tooth portion 15a of the gate rotor 15 is arranged so as to mesh with the screw groove 14a of the screw rotor 14. The space surrounded by the screw groove 14a, the tooth portion 15a of the gate rotor 15, the inner peripheral surface of the casing 11 and the slide valve 16 is formed as a compression chamber 19 filled with a refrigerant gas to be compressed. Further, oil for lubricating the bearing 17 and sealing the compression chamber 19 is injected into the compression chamber 19.

The slide valve 16 is slidably provided on the suction pressure side and the discharge pressure side of the screw rotor 14 along the outer peripheral surface of the screw rotor 14, and has an opening 16a in the center. At this time, the slide valve 16 may be used for mechanical displacement control, or may be an internal volume variable valve (discharge port valve) for changing the discharge timing.

A discharge port (not shown) is connected to the discharge chamber 20 on the inner peripheral surface of the casing 11 on the discharge pressure side. The refrigerant gas containing the high-pressure oil filled in the compression chamber 19 is discharged into the discharge chamber 20 through the opening 16a opened in the slide valve 16 and the discharge port (not shown).

The discharge chamber 20 is a space in the compression chamber 19 where the refrigerant gas containing oil is discharged, and the refrigerant gas containing oil filling the discharge chamber 20 is led to the oil separator 40.

Next, the oil separator 40 will be described in detail.
The oil separator 40 is a cyclone type oil separator that separates oil and refrigerant gas by centrifugal force using the difference in gas-liquid density. The oil separator 40 has an outer cylinder part 41 and a crown part 44. The crown portion 44 is formed integrally with the lid portion 43 having a substantially T-shaped cross section that prevents the upper opening of the outer tubular portion 41, and projects from the lower end portion of the lid portion 43, inside the outer tubular portion 41. It has a cylindrical inner cylinder portion 42 located at. A discharge port 43a for discharging the refrigerant after oil separation is formed in the center of the lid 43. As described above, the oil separator 40 has the outer cylinder portion 41 and the inner cylinder portion 42 and is formed of a double cylinder. Below the double cylinder, there is a bottom portion 46 configured to extend from the lower end portion of the outer cylinder portion 41, and above the bottom portion 46 is an oil storage portion 47 in which the oil separated by the oil separator 40 is stored. ..

A flow straightening plate 44a that reduces the swirling component of the refrigerant is provided at the bottom of the crown portion 44, specifically, at the bottom of the inner tubular portion 42. In the first embodiment, the crown portion 44 and the rectifying plate 44a are integrally formed by, for example, casting, and the integral portion is detachably attached to the lid portion 43 by a bolt (not shown) in the outer cylinder portion. It is fastened to 41.

2 to 5 are views showing an example of the current plate of FIG.
The straightening vane 44a is configured by a plate-shaped member that divides the bottom portion of the inner tubular portion 42 into a plurality of portions, and in the example of FIG. 2, the straightening vane 44a is linearly configured. In the example of FIG. 3, the rectifying plate 44a has a corrugated shape. With this configuration, the contact area of the swirling flow can be increased, and the effect of suppressing the swirling flow can be further obtained. In the example of FIG. 4, a plurality of rectifying plates 44a are provided. The configuration of FIG. 4 can improve the effect of suppressing the swirling flow as compared with the configuration of FIG. In the example of FIG. 5, the current plate 44a is formed in a cross shape. In the configuration of FIG. 5, since the flow passage areas of the regions partitioned by the flow regulating plate 44a are the same, not only the effect of suppressing the swirling flow but also the pressure loss reduction can be expected.

Return to the explanation of Figure 1. An inlet (not shown) for the refrigerant gas containing oil discharged from the compressor body 10 is formed on the upper side of the side surface of the outer cylinder portion 41. An oil outlet 41a is formed at the lower end of the side surface of the outer tubular portion 41. The lower opening of the outer cylinder part 41 is closed by a bottom plate 45.

Here, conventionally, the lid, the inner cylinder portion, and the member forming the movement space of the check valve were composed of different members. On the other hand, in the first embodiment, the lid portion 43 of the crown portion 44 also serves as the movement space of the check valve 50, and the check valve 50 is built in the lid portion 43. Hereinafter, the crown portion 44 will be specifically described.

The crown portion 44 has a lower first space 42a formed in the inner tubular portion 42 and an upper second space 42b formed in the lid portion 43, and the first space 42a and the second space 42a. 42b communicates with an opening 42c having a diameter smaller than that of both spaces. The second space 42b is a cylindrical space having the same diameter as the discharge port 43a, and a check valve 50 and a check valve guide 51 for supporting the vertical movement of the check valve 50 in the second space 42b. Are arranged. The check valve guide 51 is fixed to the inside of the lid portion 43 by a stop ring 52 above the check valve 50.

The check valve 50 has a valve body 50a that opens and closes the opening 42c, and a shaft portion 50b that extends upward from the upper surface of the valve body 50a. The check valve guide 51 has a guide hole 53a into which the shaft portion 50b of the check valve 50 is inserted, and the shaft portion 50b moves up and down in the guide hole 53a, so that the valve body 50a moves inside the second space 42b. Is designed to move up and down. In this way, the second space 42b serves as a movement space for the check valve 50, and the lid portion 43 has a structure in which the check valve 50 is built. The outer peripheral surface of the valve body 50a of the check valve 50 is formed to have a smaller diameter than the inner peripheral surface of the second space 42b, and the outer peripheral surface of the valve body 50a and the inner peripheral surface of the second space 42b slide. Does not form a face. Therefore, even if impurities such as iron powder adhere to the inner peripheral surface of the second space 42b, the check valve 50 can be prevented from sticking to the inner peripheral surface of the second space 42b.

In the check valve 50 configured as described above, the differential pressure between the pressure of the refrigerant gas passing through the flow straightening plate 44a and rising in the inner cylinder portion 42 and the pressure on the downstream side of the valve body 50a is greater than zero. Then, when the weight of the valve body 50a is overcome, the valve body 50a is lifted to open the valve. When the check valve 50 is opened, the check valve guide 51 plays a role of a stopper, and the valve body 50a is lifted to a position where the check valve guide 51 abuts. Further, during the operation stop, the check valve 50 closes the opening 42c with the valve body 50a to close the valve, and separates the first space 42a and the second space 42b and serves as a partition between high pressure and low pressure. ..

Next, the flows of the refrigerant gas and the oil in the compressor according to the first embodiment will be described.
When the motor 12 fixed on the same axis as the screw rotor 14 rotates, low-pressure refrigerant gas is sucked into the compression chamber 19 from the suction pressure side of the screw rotor 14 (left side in FIG. 1). The refrigerant sucked into the compression chamber 19 is sent to the discharge pressure side of the screw rotor 14 (right side in FIG. 1) while being compressed in the compression chamber 19. The refrigerant gas compressed to a high pressure in the compression chamber 19 is discharged from the discharge port 43a to the discharge chamber 20 together with the oil injected into the compression chamber 19. The refrigerant gas containing oil discharged to the discharge chamber 20 flows toward the oil separator 40.

The refrigerant gas containing oil that has reached the oil separator 40 flows into the outer cylinder part 41 from an inlet (not shown) formed on the upper side of the side surface of the outer cylinder part 41. The refrigerant gas containing oil that has flowed into the outer tubular portion 41 descends while swirling through the gap between the outer tubular portion 41 and the inner tubular portion 42. Of the refrigerant gas including the oil that swirls and descends, the oil having a higher density than the refrigerant gas is blown to the inner peripheral surface of the outer cylinder portion 41 by the centrifugal force and separated from the refrigerant gas. Then, the separated oil flows downward along the inner peripheral surface of the outer tubular portion 41 due to gravity, and falls into the oil storage portion 47 through the oil outlet 41a. The oil stored in the oil storage portion 47 is supplied to the compression chamber 19 or the bearing 17 through a path (not shown) provided in the casing 11.

On the other hand, the refrigerant gas separated from the oil descends while swirling in the gap between the outer cylinder part 41 and the inner cylinder part 42, turns back at the bottom plate 45, and becomes an upflow while continuing to swirl into the inner cylinder part 42. Inflow. When flowing into the inner tubular portion 42, the refrigerant gas is rectified by passing through the rectifying plate 44a and rises inside the inner tubular portion 42. Then, when the check valve 50 opens due to the pressure of the refrigerant rising inside the inner tubular portion 42, the refrigerant flows from the first space 42a into the second space 42b through the opening 42c, and the second space 42b. Flows upwards and is discharged from the discharge port 43a to the cycle side.

Here, the point that the lift amount of the check valve 50 greatly affects the pressure loss will be described with reference to FIG. 2 below.

FIG. 6 is a structural explanatory view of oil separators having different check valve lift amounts in the compressor according to the first embodiment of the present invention.
In FIG. 6, (a) and (b) are obtained by changing the internal dimension of the crown portion 44 and changing the lift amount of the check valve 50. The height position of the opening 42c is lower in (b) than in (a), and the lift amount of the check valve 50 is enlarged by h _L. The outer dimensions of the crown portion 44 are the same in (a) and (b).

Most of the refrigerant gas flowing into the inner cylinder portion 42 and passing through the opening 42c collides with the valve body 50a of the check valve 50, and then flows into the second space 42b. At this time, as the lift amount of the valve body 50a increases, not only the flow passage area increases, but also the collision of the refrigerant gas with the valve body 50a is alleviated and the pressure loss can be reduced. Therefore, it is preferable to increase the lift amount as shown in (b) in order to reduce the pressure loss.

Here, in order to increase the lift amount, if the structure is changed such that the height of the discharge port 43a is changed, the length of the lid portion 43 of the oil separator 40 in the vertical direction is increased, and the weight is increased. As a result, there is a problem that the cost becomes high. In the first embodiment, since the check valve 50 is built in the lid 43, the lift amount of the check valve 50 can be increased without increasing the weight of the whole. Specifically, the lift amount of the check valve 50 can be increased by lowering the height position of the opening 42c. That is, the lift amount can be increased by replacing the crown portion 44 with the lower height position of the opening 42c.

By using the crown portion 44 in which the lift amount of the check valve 50 is increased in this way, it is possible to reduce the pressure loss near the check valve 50 and improve the performance of the compressor. Here, the lift amount is recommended to be 10 mm or more in consideration of pressure loss, and the upper limit value is recommended to be 50 mm. This is because if the lift amount exceeds 50 mm, an impact force is generated when the check valve 50 falls into the opening 42c when the operation is stopped, and the check valve 50 may be damaged.

As described above, in the first embodiment, the crown portion 44 having the lid portion 43 accommodating the check valve 50 is fixed to the outer cylinder portion 41. That is, the member that forms the movement space of the valve body 50a and the lid member that closes the upper opening of the outer tubular portion 41 are integrally formed, and the integrally formed product is fixed to the outer tubular portion 41. Therefore, as compared with the conventional structure in which these members are provided separately, the effect of vibration is reduced, and the effect of vibration acting on the valve body 50a can be reduced. Therefore, according to the first embodiment, the operation of the valve body 50a can be stabilized.

In addition, in the first embodiment, the member that forms the movement space of the valve body 50a and the member that closes the upper opening of the outer tubular portion 41 are integrally formed as the crown portion 44, so the number of parts can be reduced. ..

Further, in the first embodiment, since the lid portion 43 has the check valve 50 built therein, the lift amount of the check valve 50 can be changed only by changing the internal design of the crown portion 44 without increasing the overall weight. It can be expanded. Therefore, it is possible to provide a compressor having a simple structure and improving the compressor performance by reducing the pressure loss.

Further, in the first embodiment, the lid portion 43 has the built-in check valve 50, so that the height of the discharge port 43a does not change even if the lift amount is changed as described above. Therefore, it is possible to improve the compressor performance by reducing the pressure loss without increasing the weight of the lid portion 43 of the oil separator 40.

In addition, in the first embodiment, since the crown portion 44 and the flow straightening plate 44a have an integrated structure, the number of parts can be reduced, the number of assembly steps can be reduced, and the manufacturing cost and the management cost can be effectively suppressed. is there. However, the present invention is not limited to the structure in which the crown portion 44 and the flow straightening plate 44a are integrated, and includes a structure in which they are formed separately.

In addition, although the rectifying plate 44a is provided on the bottom portion 46 of the inner tubular portion 42 in FIG. 1, it may be provided on the outer tubular portion 41. Hereinafter, three modified examples in which the current plate 44a is provided in the outer cylinder portion 41 will be described.

(Modification 1)
FIG. 7: is a figure which shows the modification 1 of the current plate of FIG. 8 to 11 are diagrams showing an example of the current plate of FIG. 7.
In the first modification, the current plate 44a is provided inside the outer tubular portion 41, upstream of the inlet of the first space 42a and upstream of the oil outlet 41a. As a result, the refrigerant gas containing oil that descends while swirling in the gap between the outer tubular portion 41 and the inner tubular portion 42 passes through the flow straightening plate 44a and the swirling component is suppressed. The oil contained in the refrigerant gas is separated from the refrigerant gas, and the swirling component is suppressed. The oil in which the swirling component is suppressed flows out from the oil outlet 41 a and falls into the oil reservoir 47. As described above, since the oil drops into the oil storage portion 47 after the swirling component is suppressed, the roughness of the wave front of the oil stored in the oil storage portion 47 is reduced.

On the other hand, the refrigerant gas containing oil is separated from the oil and the swirling component is suppressed, and the refrigerant gas is folded back at the bottom plate 45. The refrigerant returned by the bottom plate 45 passes through the current plate 44a and flows into the first space 42a. In this way, the refrigerant flowing into the first space 42a passes through the flow straightening plate 44a twice, so that the swirling component is greatly reduced.

Further, in comparison with the configuration in which the inner tubular portion 42 to which the flow straightening plate 44a is attached is attached to the outer tubular portion 41, in the modified example 1, when the inner tubular portion 42 is assembled to the outer tubular portion 41, etc. It is possible to reduce the risk of damage to the current plate 44a.

The shape of the current plate 44a may be linear as shown in FIG. 8 or may be corrugated as shown in FIG. Further, a plurality of straightening vanes 44a may be provided as shown in FIG. 10, or the straightening vanes 44a may be formed in a cross shape as shown in FIG.

(Modification 2)
FIG. 12 is a diagram showing a modified example 2 of the current plate of FIG. 1. 13 to 16 are views showing an example of the current plate of FIG.
In the second modification, the current plate 44 a is provided on the bottom plate 45 of the outer tubular portion 41. Modification 2 is configured such that the bottom plate 45 is provided with the flow straightening plate 44a, so that the strengths of the bottom plate 45 and the flow straightening plate 44a are improved as compared with the modification 1. Furthermore, the second modification is easier to manufacture than the first modification. Furthermore, in the second modification, the vertical length of the inner peripheral surface of the outer tubular portion 41 used for oil separation is longer than that in the first modification, so that the oil separation efficiency is improved.

The shape of the current plate 44a may be linear as shown in FIG. 13 or may be corrugated as shown in FIG. Further, a plurality of straightening vanes 44a may be provided as shown in FIG. 15, or the straightening vanes 44a may be formed in a cross shape as shown in FIG.

(Modification 3)
17: is a figure which shows the modification 3 of the current plate of FIG. 18 to 21 are views showing an example of the current plate of FIG.
In the third modification, the current plate 44 a is provided on the bottom plate 45 of the outer tubular portion 41. In Modification 3, a gap 48 is further provided along the entire circumference between the outer peripheral surface of the current plate 44a and the inner peripheral surface of the outer tubular portion 41. Since the gap 48 is provided in the modified example 3 as compared with the modified example 1, the vertical length of the inner peripheral surface of the outer tubular portion 41 used for oil separation is increased and the oil separation efficiency is improved. Go up.

The shape of the current plate 44a may be linear as shown in FIG. 18 or may be corrugated as shown in FIG. Further, a plurality of straightening vanes 44a may be provided as shown in FIG. 20, or the straightening vanes 44a may be formed in a cross shape as shown in FIG.

By the way, conventionally, the check valve has a configuration in which the outer peripheral surface of the valve body serves as a sliding surface and moves in the guide. Therefore, if the swirl component remains in the guide, foreign matter such as metal powder enters and bites into the minute gap between the outer peripheral surface of the valve body and the guide, and sticks at the position where the check valve does not close. There was a possibility to do. If the check valve sticks in this way, the check valve may not function properly. On the other hand, in the first embodiment, the shaft portion 50b having an outer diameter smaller than that of the valve body 50a is movably supported by the check valve guide 51. Therefore, in the configuration of the first embodiment, the surface area of the sliding surface between the check valve guide 51 and the shaft portion 50b is smaller than that of the conventional structure, and the sliding portion between the check valve guide 51 and the shaft portion 50b is smaller. Is near the swirl center of the refrigerant gas. In other words, there are few regions where impurities enter, and the regions themselves are located outside the main stream of the refrigerant gas. Therefore, it is unlikely that foreign matter is caught in the gap between the check valve guide 51 and the shaft portion 50b. Therefore, the risk of the shaft portion 50b sticking to the check valve guide 51 can be reduced.

Embodiment 2.
The second embodiment differs from the first embodiment in the shape of the opening 42c of the inner tubular portion 42 of the oil separator 40. Other configurations are the same as or equivalent to those in the first embodiment. Hereinafter, the second embodiment will be described focusing on the configuration different from that of the first embodiment, and the configuration not described in the second embodiment is the same as that of the first embodiment.

FIG. 22 is a schematic cross-sectional view of an oil separator in a compressor according to Embodiment 2 of the present invention, which is a partially enlarged view. Note that the check valve 50 and the check valve guide 51 are not shown in FIG. 22 in order to make the structure of the main part of the second embodiment easier to understand.
In the second embodiment, the peripheral edge portion 42ca of the opening 42c on the refrigerant inflow side has a smooth R shape. The R shape preferably has a radius of curvature of 3 mm to 30 mm. With the configuration having an R shape with a radius of curvature of 3 mm to 30 mm, the influence of pressure loss can be reduced. The R shape having a radius of curvature of 3 mm to 30 mm is a shape that facilitates manufacturing when the lid portion 43 and the inner cylinder portion 42 are integrally formed by casting. By integrally forming the lid part 43 and the inner cylinder part 42 by casting, the inner peripheral surface of the inner cylinder part 42 can be made to have a large surface roughness using the casting surface. Increasing the surface roughness of the inner peripheral surface of the inner cylindrical portion 42 provides resistance to the flow in the swirling direction, so that the swirling flow is suppressed. Further, the entrainment of oil due to the upward swirling flow can be suppressed, and the pressure loss at the outlet of the lid 43 and the check valve 50 can be reduced.

As described above, according to the second embodiment, the same effect as that of the first embodiment can be obtained, and the peripheral edge of the opening 42c on the refrigerant inflow side is formed into a smooth R shape to further reduce the pressure loss. It is possible to obtain a compressor capable of

Embodiment 3.
The third embodiment differs from the first embodiment in the shape of the first space 42a of the inner tubular portion 42 of the oil separator 40. Other configurations are the same as or equivalent to those in the first embodiment. Hereinafter, the third embodiment will be described focusing on the configuration different from the first embodiment, and the configuration not described in the third embodiment is the same as that of the first embodiment.

FIG. 23 is a schematic sectional view of an oil separator in the compressor according to the third embodiment of the present invention.
In the third embodiment, the first space 42a of the oil separator 40 has a dome shape that is convex upward.

According to the third embodiment, the same effects as those of the first embodiment can be obtained, and the first space 42a of the crown portion 44 has a dome shape that is convex upward, thereby further reducing the pressure loss. Can be obtained.

Fourth Embodiment
The fourth embodiment has a configuration in which the volume of the second space 42b of the crown portion 44 of the oil separator 40 is larger than that of the first embodiment. Other configurations are the same as or equivalent to those in the first embodiment. Hereinafter, the fourth embodiment will be described focusing on the configuration different from the first embodiment, and the configuration not described in the fourth embodiment is similar to the first embodiment.

FIG. 24 is a schematic sectional view of an oil separator in a compressor according to Embodiment 4 of the present invention.
In the fourth embodiment, the second space 42b of the oil separator 40 is configured to have an inner diameter larger than the inner diameter of the discharge port 43a in the vertical direction except for the communication port with the discharge port 43a. In the example of FIG. 5, the upper part of the cylinder has a shape in which the diameter is reduced toward the upper side, and the diameter-reduced tip portion is formed to have the same diameter as the discharge port 43a.

By configuring the second space 42b as described above, the volume can be expanded compared to the case where the second space 42b is a cylindrical space having the same diameter as the discharge port 43a as in the first embodiment. The diameter of the discharge port 43a cannot be changed because it is determined by the size of the pipe on the discharge side. However, since the inner diameter of the second space 42b does not have such a restriction, the second space 42b can be enlarged. By setting the inner diameter to be equal to or larger than the discharge port 43a, the flow passage area of the second space 42b can be increased as compared with the first embodiment. it can. Therefore, the pressure loss of the refrigerant gas can be further reduced.

As described above, according to the fourth embodiment, the same effect as that of the first embodiment can be obtained, and since the volume of the second space 42b is increased as compared with the first embodiment, the pressure loss is further reduced. A compressor can be obtained.

Here, in Embodiments 1 to 4, the oil separator 40 is provided with the flow straightening plate 44a, but the flow straightening plate 44a may not be provided. The first to fourth embodiments can be combined as appropriate. For example, the second embodiment and the third embodiment may be combined, and the first space 42a of the oil separator in FIG. 22 may have a dome shape that is convex upward.

The refrigerant applied to the compressor 1 is not limited to a specific refrigerant, but it is preferable to select a refrigerant having a low GWP in consideration of the influence on the environment, for example. The refrigerant having a low GWP is, for example, R32, R513A, HFO-1123, HFO-1234yf, HFO-1234ze, or a mixed refrigerant containing at least one of these. Further, the refrigerant applied to the compressor 1 may be a natural refrigerant such as carbon dioxide or ammonia.

Embodiment 5.
FIG. 25 is a refrigerant circuit diagram of the refrigeration cycle device according to Embodiment 5 of the present invention. In FIG. 25, the thick line shows the oil flow and the thin line shows the refrigerant flow.
As shown in FIG. 25, the refrigeration cycle device 100 includes a compressor 1, a condenser 2, an expansion valve 3, and an evaporator 4. Further, the compressor 1 is the compressor according to any one of the above-described first to fourth embodiments, and has the compressor body 10 and the oil separator 40. In the compressor 1, oil is mixed in the refrigerant discharged from the compressor body 10, and the oil is separated into the refrigerant and the oil by the oil separator 40. The separated oil is returned to the compressor body 10 by utilizing the differential pressure. On the other hand, the refrigerant from which the oil has been separated by the oil separator 40 flows into the condenser 2 and is cooled. The refrigerant cooled by the condenser 2 is decompressed by the expansion valve 3 and then heated by the evaporator 4 to become a refrigerant gas. The refrigerant gas flowing out from the evaporator 4 is sucked into the compressor 1.

According to the fifth embodiment, since the compressor 1 according to any of the first to fourth embodiments is mounted, the same effect as above can be obtained.

1 compressor, 2 condenser, 3 expansion valve, 4 evaporator, 10 compressor body, 11 casing, 12 motor, 12a stator, 12b motor rotor, 13 screw shaft, 14 screw rotor, 14a screw groove, 15 gate rotor , 15a teeth, 16 slide valve, 16a opening, 17 bearing, 18 partition, 19 compression chamber, 20 discharge chamber, 40 oil separator, 41 outer cylinder part, 41a oil outlet, 42 inner cylinder part, 42a first space , 42b second space, 42c opening portion, 42ca peripheral portion, 43 lid portion, 43a discharge port, 44 crown portion, 44a straightening plate, 45 bottom plate, 46 bottom portion, 47 oil storage part, 50 check valve, 50a valve body, 50b shaft part, 51 check valve guide, 52 retaining ring, 53 guide hole, 100 refrigeration cycle device.

Claims

A compressor body for compressing a refrigerant containing oil,
A cyclone-type oil separator for separating the oil from the refrigerant discharged from the compressor body,
The oil separator is
The outer cylinder part,
A lid that covers the upper opening of the outer tubular portion and has a lid portion in which a discharge port for discharging the refrigerant after oil separation is formed, and a crown portion fixed to the outer tubular portion,
A compressor provided with a valve body which is provided inside the lid portion of the crown portion, and which is opened by the pressure of the refrigerant rising inside the lid portion toward the discharge port.
The compressor according to claim 1, wherein the crown portion has an inner cylinder portion that is integrally formed with the lid portion, protrudes from the lid portion, and is located inside the outer cylinder portion.
A lower first space and an upper second space are formed in the crown portion, and the first space and the second space communicate with each other through the opening, and the opening and closing the opening. The compressor according to claim 1 or 2, wherein a valve body is arranged in the second space.
The lift amount of the valve body can be increased by replacing the crown portion with the outer cylinder portion detachably, and by replacing the crown portion with another crown portion having a different height position of the opening. The described compressor.
The compressor according to claim 3 or 4, wherein a peripheral portion of the opening on the refrigerant inflow side is formed in an R shape.
The compressor according to claim 5, wherein the R shape is formed with a radius of curvature of 3 mm to 30 mm.
The compressor according to any one of claims 3 to 6, wherein a space upstream of the opening in the crown portion is formed in a dome shape that is convex upward.
8. The space in the crown portion on the downstream side of the opening has an inner diameter larger than the inner diameter of the discharge port in the vertical direction except for the communication port with the discharge port. The compressor according to claim 1.
The compressor according to any one of claims 1 to 8, wherein a lift amount of the valve body is set to 10 mm to 50 mm.
10. The flow straightening plate, which is provided at the bottom of the crown portion and partitions the bottom portion to reduce the swirling component of the refrigerant flowing into the inside of the crown portion. Compressor.
The compressor according to claim 10, wherein the crown portion and the straightening vane are integrally configured.
The compressor according to any one of claims 1 to 11, wherein the compressor body is driven by an inverter.
The compressor according to any one of claims 1 to 12, wherein movement of the valve body is supported by a check valve guide fixed to an inner circumference of the lid portion.
The compressor according to any one of claims 1 to 13, wherein the valve body has a shaft portion, which is smaller than an outer diameter of the valve body, as a sliding portion, and a center of the shaft portion is near a turning center portion.
A refrigeration cycle apparatus including the compressor according to any one of claims 1 to 14.