JP2013164008A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor that enhances the efficiency of an electric motor, improves volume efficiency, and achieves low-oil circulation.SOLUTION: A compressor includes: an oil separation mechanism 40 that separates oil from a coolant gas ejected from compressors 10; a cylindrical space 41 where the oil separation mechanism 40 swirls the coolant gas; an inflow port 42 that makes the coolant gas ejected from the compression mechanism 10 to flow into the cylindrical space 41; a dispensing outlet 43 that sends out the coolant gas separated from the oil from the cylindrical space 41 to a container space 31; and an outlet port 44 that discharges the separated oil and some of the coolant gas from the cylindrical space 41 to the other container space 32. The outlet port 44 is made eccentric from a center axis of the cylindrical space 41.

Description

  The present invention relates to a compressor provided with an oil separation mechanism that separates oil from refrigerant gas discharged from the compression mechanism.

  2. Description of the Related Art Conventionally, a compressor used for an air conditioner, a cooling device, and the like generally includes a compression mechanism section and an electric motor section that drives a rear portion of the compressor in a casing, and compresses the refrigerant gas returned from the refrigeration cycle. Compressed and fed into the refrigeration cycle. Generally, the refrigerant gas compressed by the compression mechanism unit once flows around the motor to cool the motor unit, and then is sent to a refrigeration cycle from a discharge pipe provided in the casing (for example, Patent Documents). 1). That is, the refrigerant gas compressed by the compression mechanism is discharged from the discharge port to the discharge space. Thereafter, the refrigerant gas passes through a passage provided on the outer periphery of the frame and is discharged to the upper part of the motor space between the compression mechanism unit and the motor unit. A part of the refrigerant gas is discharged from the discharge pipe after cooling the electric motor unit. Further, the other refrigerant gas communicates with the upper and lower motor spaces of the motor unit by a passage formed between the motor unit and the inner wall of the casing, cools the motor unit, and then rotates the rotor of the motor unit. And through the gap between the stator and the motor space at the top of the motor section, and discharged from the discharge pipe.

JP-A-5-44667

  However, in the conventional configuration, the high-temperature and high-pressure refrigerant gas compressed by the compression mechanism portion flows through the electric motor portion, so that the electric motor portion is heated by the refrigerant gas and causes a reduction in efficiency of the electric motor portion. It was.

  Also, through the passage provided on the outer periphery of the frame, the high-temperature discharge gas flows through the lower part of the compression mechanism unit, so the compression mechanism unit is heated, and in particular, the refrigerant gas in the low temperature state returned from the refrigeration cycle, Heat is received in the process of being sent to the compression chamber through the suction path. For this reason, the refrigerant gas has already expanded at the time of entering the compression chamber, and there has been a problem that the circulation rate is reduced due to the expansion of the refrigerant gas.

  Furthermore, when a lot of oil is contained in the refrigerant discharged from the discharge pipe, there is a problem that the cycle performance is deteriorated.

  The present invention has been made to solve the above-described conventional problems, and an object of the present invention is to provide a compressor that realizes high efficiency of the motor unit, improvement of volumetric efficiency, and low oil circulation. .

  In the compressor according to the present invention, the oil separation mechanism section has a cylindrical space for rotating the refrigerant gas, an inflow section for flowing the refrigerant gas discharged from the compression mechanism section into the cylindrical space, and one container from the cylindrical space. The inner space has a delivery port for sending the refrigerant gas from which the oil has been separated, and a discharge port for discharging the separated oil and a part of the refrigerant gas from the cylindrical space, and the cylindrical space is centered on the discharge port. Eccentric from the central axis.

  As a result, it is possible to provide a compressor that achieves high efficiency of the electric motor section, improvement of volumetric efficiency, and low oil circulation.

  According to the present invention, most of the high-temperature and high-pressure refrigerant gas that is compressed by the compression mechanism and delivered from the oil separation mechanism is led to the one container inner space and discharged from the discharge pipe. Therefore, since most of the high-temperature and high-pressure refrigerant gas does not pass through the electric motor part, the electric motor part is not heated by the refrigerant gas, and the efficiency of the electric motor part can be improved.

  In addition, according to the present invention, most of the high-temperature and high-pressure refrigerant gas can be guided to the one container inner space, so that the heating of the compression mechanism portion in contact with the other container inner space can be suppressed. Heating can be suppressed and high volumetric efficiency in the compression chamber can be obtained.

  Further, according to the present invention, the oil separated by the oil separation mechanism is discharged together with the refrigerant gas to the other container space, so that the oil hardly stays in the cylindrical space. Therefore, the separated oil is blown up in the cylindrical space by the swirling refrigerant gas, and is not sent out together with the refrigerant gas from the outlet, so that stable oil separation can be performed. Furthermore, since the oil is not retained in the cylindrical space, the cylindrical space can be made small.

  In addition, according to the present invention, in the discharge of part of the oil and the refrigerant gas separated by the oil separation mechanism, the oil separation mechanism is sufficiently enhanced by promoting the oil discharge and suppressing the refrigerant gas discharge. Can be demonstrated.

The longitudinal cross-sectional view of the compressor by Embodiment 1 of this invention FIG. 1 is an enlarged cross-sectional view of the main part of the compression mechanism in FIG. The principal part expanded sectional view of the compression mechanism part in the compressor by Embodiment 2 of this invention The principal part expanded sectional view of the compression mechanism part in the compressor by Embodiment 3 of this invention The principal part expanded sectional view of the compression mechanism part in the compressor by Embodiment 4 of this invention Vertical section of a compressor according to Embodiment 5 of the present invention A graph showing the relationship between the ratio of oil circulation to A / B and the COP ratio The principal part expanded sectional view of the oil separation mechanism part by Embodiment 6 of this invention The principal part expanded sectional view of the oil separation mechanism part by Embodiment 7 of this invention The principal part expanded sectional view of the oil separation mechanism part by Embodiment 8 of this invention The principal part expanded sectional view of the oil separation mechanism part by Embodiment 9 of this invention The principal part expansion perspective view of the oil separation mechanism part by Embodiment 10 of this invention

  According to a first aspect of the present invention, an airtight container includes a compression mechanism portion that compresses the refrigerant gas and an electric motor portion that drives the compression mechanism portion. A compressor that is divided into a container inner space, provided with a discharge pipe that discharges refrigerant gas from one container inner space to the outside of the sealed container, and an electric motor part is disposed in the other container inner space, and is discharged from the compression mechanism part. Provided with an oil separation mechanism that separates oil from the refrigerant gas, and the oil separation mechanism that swirls the refrigerant gas, and an inflow portion that flows the refrigerant gas discharged from the compression mechanism into the cylindrical space And, from the cylindrical space to the one container inner space, a delivery port for sending the refrigerant gas from which the oil has been separated, and a discharge port for discharging the separated oil and a part of the refrigerant gas from the cylindrical space, The center of the discharge port is the center of the cylindrical space Obtained by the arrangement in which a more eccentric, but not cylindrical space central axis disposed in the outlet range.

  According to this configuration, most of the high-temperature and high-pressure refrigerant gas that is compressed by the compression mechanism and delivered from the oil separation mechanism is led to the one container inner space and discharged from the discharge pipe. Therefore, since most of the high-temperature and high-pressure refrigerant gas does not pass through the electric motor part, the electric motor part is not heated by the refrigerant gas, and the efficiency of the electric motor part can be improved.

  Further, according to this configuration, most of the high-temperature and high-pressure refrigerant gas can be guided to the one container inner space, so that the heating of the compression mechanism portion in contact with the other container inner space can be suppressed. Heating can be suppressed and high volumetric efficiency in the compression chamber can be obtained.

  Further, according to this configuration, the oil separated by the oil separation mechanism is discharged together with the refrigerant gas from the discharge port located at the position facing the delivery port, so that the oil is mostly retained in the cylindrical space. No. Therefore, the separated oil is blown up in the cylindrical space by the swirling refrigerant gas, and is not sent out together with the refrigerant gas from the outlet, so that stable oil separation can be performed. Furthermore, since the oil is not retained in the cylindrical space, the cylindrical space can be made small.

  Further, according to this configuration, since the oil separated in the oil separation mechanism is guided to the lower part of the cylindrical space through the cylindrical space wall surface, the refrigerant gas exists on the center side and the oil exists on the wall surface side in the lower part of the cylindrical space. Since the oil discharge port is eccentric to the wall surface side from the central axis of the cylindrical space, the effect of the oil separation mechanism can be enhanced because the effect of increasing the oil discharge and suppressing the refrigerant gas discharge is obtained. Since oil discharge into the cycle can be suppressed, the heat exchange efficiency of the refrigeration cycle can be increased.

  According to a second invention, in the first invention, the compression mechanism section includes a fixed scroll, a turning scroll disposed to face the fixed scroll, and a main bearing member that supports a shaft that drives the turning scroll, and is a cylinder. A shaped space is formed in the fixed scroll and the main bearing member, and the discharge port communicates with the other in-container space.

  According to this configuration, by forming the oil separation mechanism portion in the compression mechanism portion, the path through which the refrigerant gas flows from the discharge port to the discharge pipe can be shortened, and the sealed container can be downsized.

  Further, according to this configuration, since the oil separated by the oil separation mechanism is discharged together with the refrigerant gas to the other container space, the oil hardly stays in the cylindrical space.

  The third invention is characterized in that, in the first invention, the discharge port is in contact with the wall surface of the cylindrical space.

  According to this configuration, since the oil transmitted through the wall surface can be directly discharged, the effect of the oil separation mechanism can be further enhanced, and the oil discharge into the cycle can be suppressed. Efficiency can be increased.

  The fourth invention is characterized in that, in the first invention, a discharge port is provided in the cylindrical space wall.

  According to this configuration, since the oil traveling on the wall surface can be discharged by the centrifugal force of the swirling refrigerant, the effect of the oil separation mechanism can be further enhanced and oil discharge into the cycle can be suppressed. Therefore, the heat exchange efficiency of the refrigeration cycle can be increased.

The fifth invention is characterized in that the eccentric direction of the discharge port is provided in a direction different from the eccentric direction of the delivery port.

  According to this configuration, since the separated oil can be prevented from rewinding, the effect of the oil separation mechanism can be enhanced, and the oil discharge into the cycle can be suppressed, so that the heat exchange efficiency of the refrigeration cycle Can be increased.

  The sixth invention is characterized in that a plurality of discharge ports are provided.

  According to this configuration, oil can be discharged more, so the effect of the oil separation mechanism can be enhanced, and oil discharge into the cycle can be suppressed, so that the heat exchange efficiency of the refrigeration cycle is increased. Can do.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings. Note that the present invention is not limited to the embodiments.

(Embodiment 1)
FIG. 1 is a longitudinal sectional view of a compressor according to Embodiment 1 of the present invention. As shown in FIG. 1, the compressor according to the present embodiment includes a compression mechanism unit 10 that compresses refrigerant gas and an electric motor unit 20 that drives the compression mechanism unit 10 in the sealed container 1.

  The inside of the sealed container 1 is divided into one container inner space 31 and the other container inner space 32 by the compression mechanism unit 10. The electric motor unit 20 is disposed in the other container space 32. The other container space 32 is divided into a compression mechanism side space 33 and an oil storage side space 34 by the electric motor unit 20. The oil storage section 2 is arranged in the oil storage space 34.

  A suction tube 3 and a discharge tube 4 are fixed to the sealed container 1 by welding. The suction pipe 3 and the discharge pipe 4 lead to the outside of the sealed container 1 and are connected to members constituting the refrigeration cycle. The suction pipe 3 introduces a refrigerant gas from the outside of the sealed container 1, and the discharge pipe 4 guides the refrigerant gas from one container inner space 31 to the outside of the sealed container 1.

  The main bearing member 11 is fixed in the sealed container 1 by welding or shrink fitting, and supports the shaft 5. A fixed scroll 12 is bolted to the main bearing member 11. The orbiting scroll 13 that meshes with the fixed scroll 12 is sandwiched between the main bearing member 11 and the fixed scroll 12. The main bearing member 11, the fixed scroll 12, and the orbiting scroll 13 constitute a scroll-type compression mechanism unit 10.

  Between the orbiting scroll 13 and the main bearing member 11, a rotation restraint mechanism 14 such as an Oldham ring is provided. The rotation restraint mechanism 14 prevents the orbiting scroll 13 from rotating, and guides the orbiting scroll 13 to make a circular orbital motion. The orbiting scroll 13 is eccentrically driven by an eccentric shaft portion 5 a provided at the upper end of the shaft 5. By this eccentric drive, the compression chamber 15 formed between the fixed scroll 12 and the orbiting scroll 13 moves from the outer periphery toward the center, and compresses with a reduced volume.

A suction path 16 is formed between the suction tube 3 and the compression chamber 15. The suction path 16 is provided in the fixed scroll 12. A discharge port 17 of the compression mechanism unit 10 is formed at the center of the fixed scroll 12. A reed valve 18 is provided at the discharge port 17. A muffler 19 that covers the discharge port 17 and the reed valve 18 is provided on one container inner space 31 side of the fixed scroll 12. The muffler 19 isolates the discharge port 17 from one container inner space 31. The refrigerant gas is sucked into the compression chamber 15 from the suction pipe 3 through the suction path 16. The refrigerant gas compressed in the compression chamber 15 is discharged into the muffler 19 from the discharge port 17. The reed valve 18 is pushed open when the refrigerant gas is discharged from the discharge port 17.

  A pump 6 is provided at the lower end of the shaft 5. The suction port of the pump 6 is disposed in the oil storage part 2 provided at the bottom of the sealed container 1. The pump 6 is driven by the shaft 5. Therefore, the oil in the oil storage section 2 can be reliably sucked up regardless of the pressure condition and the operating speed, and no oil runs out at the sliding section. The oil sucked up by the pump 6 is supplied to the compression mechanism 10 through an oil supply hole 7 formed in the shaft 5. If foreign matter is removed from the oil using an oil filter before or after the oil is sucked up by the pump 6, foreign matter can be prevented from being mixed into the compression mechanism unit 10, and further reliability can be improved.

  The pressure of the oil guided to the compression mechanism unit 10 is substantially the same as the discharge pressure of the refrigerant gas discharged from the discharge port 17 and also serves as a back pressure source for the orbiting scroll 13. As a result, the orbiting scroll 13 operates stably without leaving the fixed scroll 12 or hitting it. Further, part of the oil enters the fitting portion between the eccentric shaft portion 5a and the orbiting scroll 13 and the bearing portion 8 between the shaft 5 and the main bearing member 11 so as to obtain a clearance by the supply pressure and the own weight. Then, it is lubricated, then falls and returns to the oil storage section 2. A path 7 a is formed in the orbiting scroll 13, one end of the path 7 a opens to the high pressure region 35, and the other end of the path 7 a opens to the back pressure chamber 36. The rotation restraint mechanism 14 is disposed in the back pressure chamber 36.

  Accordingly, part of the oil supplied to the high pressure region 35 enters the back pressure chamber 36 through the path 7a. The oil that has entered the back pressure chamber 36 lubricates the thrust sliding portion and the sliding portion of the rotation restraint mechanism 14 and applies back pressure to the orbiting scroll 13 in the back pressure chamber 36.

  Next, the oil separation mechanism of the compressor according to the first embodiment will be described with reference to FIGS. 1 and 2. 2 is an enlarged cross-sectional view of the main part of the compression mechanism in FIG. The compressor according to the present embodiment is provided with an oil separation mechanism 40 that separates oil from refrigerant gas discharged from the compression mechanism 10.

  The oil separation mechanism section 40 communicates the cylindrical space 41 for turning the refrigerant gas, the inflow section 42 that communicates the inside of the muffler 19 and the cylindrical space 41, and the cylindrical space 41 and one container inner space 31. It has the delivery port 43 and the discharge port 44 which connects the cylindrical space 41 and the other container internal space 32. The cylindrical space 41 includes a first cylindrical space 41 a formed in the fixed scroll 12 and a second cylindrical space 41 b formed in the main bearing member 11.

  The inflow portion 42 communicates with the first cylindrical space 41a, and preferably the opening of the inflow portion 42 is formed on the inner peripheral surface of the upper end of the first cylindrical space 41a. The inflow portion 42 causes the refrigerant gas discharged from the compression mechanism portion 10 to flow into the cylindrical space 41 from the muffler 19. The inflow portion 42 opens in the tangential direction with respect to the cylindrical space 41.

  The delivery port 43 is formed on the upper end side of the cylindrical space 41 and is formed at least on the side of the in-container space 31 with respect to the inflow portion 42. The delivery port 43 is preferably formed on the upper end surface of the first cylindrical space 41a. And the delivery port 43 sends out the refrigerant gas which isolate | separated oil from the cylindrical space 41 to the one container inner space 31.

  The discharge port 44 is formed on the lower end side of the cylindrical space 41 and is formed at least on the other container inner space 32 side than the inflow portion 42. The discharge port 44 is preferably formed on the lower end surface of the second cylindrical space 41b. The discharge port 44 discharges the separated oil and a part of the refrigerant gas from the cylindrical space 41 to the compression mechanism side space 33.

  Here, the cross-sectional area A of the opening of the delivery port 43 is preferably smaller than the cross-sectional area C of the cylindrical space 41 and larger than the cross-sectional area B of the opening of the discharge port 44. When the cross-sectional area A of the opening of the delivery port 43 is the same as the cross-sectional area C of the cylindrical space 41, the swirling flow of the refrigerant gas is blown out from the delivery port 43 without being guided toward the discharge port 44. . Further, when the cross-sectional area B of the opening of the discharge port 44 is the same as the cross-sectional area C of the cylindrical space 41, the swirling flow of the refrigerant gas blows out from the discharge port 44. Further, by making the cross-sectional area A of the opening of the delivery port 43 larger than the cross-sectional area B of the opening of the discharge port 44, the flow path resistance at the delivery port 43 is reduced. As a result, the refrigerant gas is more likely to flow to the delivery port 43 than to the discharge port 44. As an example, A / B can be set to about 9.

  FIG. 7 is a graph showing the relationship between the ratio of oil circulation to A / B and the COP ratio. From FIG. 7, it can be seen that when A / B is reduced (= the cross-sectional area B of the discharge port 44 is made closer to the cross-sectional area A of the delivery port 43), the oil circulation rate ratio decreases. This is because the amount of refrigerant gas discharged from the discharge port 44 increases, so that the refrigerant gas flows into the space on the electric motor unit 20 side, and oil separation by collision and contact is promoted. However, when the refrigerant gas flows into the space on the electric motor unit 20 side, the electric motor unit 20 is heated by the high-temperature refrigerant gas, and the efficiency of the electric motor unit 20 is reduced. Further, the refrigerant gas that has flowed into the space on the electric motor unit 20 side passes through the compression mechanism unit 10 and is sent into the one container inner space 31, so that the compression mechanism unit 10 is heated, causing the intake refrigerant gas to be heated, The volume efficiency is reduced. As a result, when A / B becomes too small, the COP ratio decreases, and the performance improvement effect decreases.

  From the above results, it is preferable to set A / B to 3 or more and 10 or less in order to achieve the performance improvement effect of both the oil circulation rate ratio and the COP ratio more remarkably.

  In the present embodiment, the first cylindrical space 41 a is formed by drilling the outer peripheral portion of the fixed scroll 12, and the second cylindrical space is formed by drilling the outer peripheral portion of the main bearing member 11. 41b is formed. In addition, a groove that opens in a tangential direction is formed on the end surface on the non-wrap side of the fixed scroll 12 with respect to the first cylindrical space 41 a, and a part of the groove on the first cylindrical space 41 a side is formed by the muffler 19. The inflow part 42 is comprised by covering. Moreover, the delivery port 43 is comprised with the hole formed in the muffler 19, and this hole is arrange | positioned in opening of the 1st cylindrical space 41a. Further, the discharge port 44 is constituted by a hole formed in the bearing cover 45, and this hole is arranged in the opening of the second cylindrical space 41b.

  Hereinafter, the operation of the oil separation mechanism 40 according to the present embodiment will be described. The refrigerant gas discharged into the muffler 19 is guided to the cylindrical space 41 through the inflow portion 42 formed in the fixed scroll 12. Since the inflow portion 42 opens in a tangential direction with respect to the cylindrical space 41, the refrigerant gas delivered from the inflow portion 42 flows along the inner wall surface of the cylindrical space 41, and the inner periphery of the cylindrical space 41. A swirling flow is generated on the surface. This swirling flow is a flow toward the discharge port 44. The refrigerant gas contains oil supplied to the compression mechanism unit 10, and while the refrigerant gas is swirling, the oil having a high specific gravity adheres to the inner wall of the cylindrical space 41 by centrifugal force, and the refrigerant gas and To separate.

  The swirl flow generated on the inner peripheral surface of the cylindrical space 41 turns back after reaching the discharge port 44 or in the vicinity of the discharge port 44 and changes to an upward flow passing through the center of the cylindrical space 41. The refrigerant gas from which the oil has been separated by the centrifugal force reaches the delivery port 43 by the upward flow and is sent to the one container inner space 31. The refrigerant gas sent out to one container inner space 31 is sent out from the discharge pipe 4 provided in the one container inner space 31 to the outside of the sealed container 1 and supplied to the refrigeration cycle.

The oil separated in the cylindrical space 41 is sent out from the discharge port 44 to the compression mechanism side space 33 together with a small amount of refrigerant gas. The oil sent out to the compression mechanism side space 33 reaches the oil storage part 2 through the wall surface of the sealed container 1 and the communication path of the electric motor part 20 due to its own weight.

  The refrigerant gas sent out to the compression mechanism side space 33 passes through the gap of the compression mechanism portion 10, reaches one container inner space 31, and is sent out from the discharge pipe 4 to the outside of the sealed container 1.

  In the oil separation mechanism 40 according to the present embodiment, the delivery port 43 is formed on the one container inner space 31 side with respect to the inflow part 42, and the discharge port 44 is formed on the other container inner space 32 side with respect to the inflow part 42. To do. Therefore, a swirl flow is generated on the inner peripheral surface of the cylindrical space 41 between the inflow portion 42 and the discharge port 44, and swirl at the center of the cylindrical space 41 between the discharge port 44 and the delivery port 43. A flow in the opposite direction to the flow is generated. Therefore, as the discharge port 44 moves away from the inflow portion 42, the number of revolutions of the refrigerant gas increases and the oil separation effect increases. Further, since the swirling refrigerant gas passes through the central portion of the swirling flow, the delivery port 43 only needs to be on the side opposite to the discharge port from the inflow portion 42. That is, the effect of oil swirl separation can be enhanced by increasing the distance between the inflow portion 42 and the discharge port 44 as much as possible.

  In addition, the oil separation mechanism 40 according to the present embodiment discharges the oil together with the refrigerant gas from the discharge port 44 without storing the separated oil in the container inner space 32. An action of guiding the generated swirling flow toward the discharge port 44 is provided.

  If the discharge port 44 is not formed in the cylindrical space 41 and the oil is stored in the cylindrical space 41, the flow that pulls to the outside from the discharge port 44 does not occur, so the swirl flow disappears before reaching the oil surface. If it reaches the oil level, it will roll up the oil. Moreover, in order to exhibit the oil separation function without forming the discharge port 44 in the cylindrical space 41, it is necessary to form a space sufficient to store oil.

  However, by discharging the oil from the discharge port 44 together with the refrigerant gas as in the oil separation mechanism unit 40 according to the present embodiment, the swirling flow can be guided to the discharge port 44 and the oil is not wound up.

  According to the present embodiment, most of the high-temperature and high-pressure refrigerant gas compressed by the compression mechanism unit 10 and delivered from the oil separation mechanism unit 40 is guided to the one container inner space 31 and discharged from the discharge pipe 4. Is done. Therefore, most of the high-temperature and high-pressure refrigerant gas does not pass through the electric motor unit 20, so that the electric motor unit 20 is not heated by the refrigerant gas, and the electric motor unit 20 can be highly efficient.

  In addition, according to the present embodiment, most of the high-temperature and high-pressure refrigerant gas is guided to the one container inner space 31, so that the heating of the compression mechanism unit 10 in contact with the other container inner space 32 can be suppressed. In addition, heating of the suction refrigerant gas can be suppressed, and high volumetric efficiency in the compression chamber can be obtained.

  In addition, according to the present embodiment, the oil separated by the oil separation mechanism 40 is discharged together with the refrigerant gas to the other container space 32, so that the oil is mostly retained in the cylindrical space 41. No. Therefore, the separated oil is blown up in the cylindrical space 41 by the swirling refrigerant gas and is not sent together with the refrigerant gas from the delivery port 43, so that stable oil separation can be performed. Further, since the oil is not retained in the cylindrical space 41, the cylindrical space 41 can be made small.

Moreover, according to this Embodiment, since the oil storage part 2 is arrange | positioned in the oil storage side space 34 and oil is not stored in the compression mechanism side space 33, the airtight container 1 can be reduced in size. Further, according to the present embodiment, the muffler 19 that isolates the discharge port 17 of the compression mechanism 10 from the one container inner space 31 is disposed, and the inside of the muffler 19 and the cylindrical space 41 are separated by the inflow portion 42. By communicating, the refrigerant gas compressed by the compression mechanism unit 10 can be reliably guided to the oil separation mechanism unit 40. That is, since all the refrigerant gas passes through the oil separation mechanism 40, the oil can be efficiently separated from the refrigerant gas. Further, since most of the high-temperature refrigerant gas discharged from the discharge port 17 is discharged from the discharge pipe 4 to the outside of the sealed container 1 without passing through the other container inner space 32, the electric motor unit 20 and the compression mechanism The heating of the part 10 can be suppressed.

  Further, according to the present embodiment, since the cylindrical space 41 is formed in the fixed scroll 12 and the main bearing member 11, the path through which the refrigerant gas flows from the discharge port 17 to the discharge pipe 4 can be configured to be short and sealed. The container 1 can be reduced in size.

(Embodiment 2)
FIG. 3 is an enlarged cross-sectional view of the main part of the compression mechanism in the compressor according to Embodiment 2 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, the first cylindrical space 41 c and the delivery port 43 a are formed by performing stepped hole processing on the outer peripheral portion of the fixed scroll 12. The first cylindrical space 41 c is formed by processing a hole that does not penetrate from the fastening surface side end surface (lap side end surface) with the main bearing member 11. The delivery port 43a extends from the fastening surface side end surface (wrap side end surface) with the main bearing member 11 or from the anti-fastening surface side end surface (anti-wrap side end surface) with the main bearing member 11 to the first cylindrical space 41c. It is formed by penetrating a hole smaller than the cross section.

  Moreover, the 2nd cylindrical space 41d and the discharge port 44a are formed by giving a stepped hole process to the outer peripheral part of the main bearing member 11. FIG. The second cylindrical space 41d is formed by processing a hole that does not penetrate from the fastening surface (thrust receiving surface) with the fixed scroll 12. The discharge port 44a penetrates a hole smaller than the cross section of the second cylindrical space 41d from the fastening surface (thrust surface) with the fixed scroll 12 or from the anti-fastening surface (anti-thrust surface) with the fixed scroll 12. Form.

  Moreover, the inflow part 42a forms the through-hole opened in a tangential direction with respect to the 1st cylindrical space 41c from the anti-fastening surface side end surface (anti-wrap side end surface) with the main bearing member 11 of the fixed scroll 12. It consists of that.

  Also in the present embodiment, the operation of the oil separation mechanism unit 40 is the same as that in the first embodiment, and the operation and effect in the first embodiment are also the same, and thus the description thereof is omitted.

(Embodiment 3)
FIG. 4 is an enlarged cross-sectional view of the main part of the compression mechanism in the compressor according to Embodiment 3 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, a cylindrical delivery pipe 46 is provided in the cylindrical space 41. One end 46 a of the delivery pipe 46 forms a delivery outlet 43, and the other end 46 b of the delivery pipe 46 is disposed in the cylindrical space 41. In the present embodiment, the other end 46b of the delivery pipe 46 extends into the second cylindrical space 41b. A ring-shaped space 46c is formed on the outer periphery of the delivery pipe 46, and the inflow portion 42 opens into the ring-shaped space 46c. At one end 46a of the delivery pipe 46, a flange 46d extending outward is formed.

  The refrigerant gas flowing in from the inflow portion 42 becomes a swirling flow, passes through the ring-shaped space 46 c, reaches the discharge port 44 along the inner peripheral surface of the cylindrical space 41, and then flows back in the center of the cylindrical space 41. . Then, it flows into the delivery pipe 46 from the other end 46 b of the delivery pipe 46 and flows out from one end 46 a of the delivery pipe 46.

  In the present embodiment, the first cylindrical space 41 e is formed by performing stepped hole processing on the outer peripheral portion of the fixed scroll 12. That is, a hole larger than the inner peripheral cross section of the first cylindrical space 41e is formed in the end surface on the side opposite to the wrap of the fixed scroll 12, and the flange 46d of the delivery pipe 46 is accommodated in this hole. Here, the second cylindrical space 41b is formed in the main bearing member 11 as in the first embodiment, but a stepped hole is formed in the outer peripheral portion of the main bearing member 11 as in the second embodiment. It may be formed by applying.

  As shown in the present embodiment, by providing the delivery pipe 46 in the cylindrical space 41, for example, even when the compressor is operated at a high frequency, the oil separation effect can be reliably obtained. When the delivery pipe 46 is provided, it is important that the axis of the cylindrical space 41 and the axis of the delivery pipe 46 are aligned.

  Further, when the delivery pipe 46 is provided, the delivery pipe 46 is provided with a flange 46 d, the flange 46 d is disposed in a hole formed in the cylindrical space 41, and the delivery pipe 46 is fixed to the cylindrical space 41 by the muffler 19. It is important to. In addition, the inner diameter cross-sectional area D of the delivery pipe 46 is made larger than the cross-sectional area B of the discharge port 44. As a result, the refrigerant gas is more likely to flow to the delivery port 43 than to the discharge port 44. As an example, D / B can be set to about 9.

  According to the present embodiment, the oil separation effect in the cylindrical space 41 can be enhanced by providing the cylindrical delivery pipe 46 in the cylindrical space 41. Also in the present embodiment in which the delivery pipe 46 is provided, the basic operation of the oil separation mechanism unit 40 is the same as that of the first embodiment, and the operations and effects in the first embodiment are also the same, so the description is omitted. .

(Embodiment 4)
FIG. 5 is an enlarged cross-sectional view of the main part of the compression mechanism in the compressor according to Embodiment 4 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, a cylindrical delivery pipe 47 is provided in the cylindrical space 41. The delivery pipe 47 in the present embodiment is formed integrally with the muffler 19. One end 47 a of the delivery pipe 47 forms a delivery outlet 43, and the other end 47 b of the delivery pipe 47 is disposed in the cylindrical space 41. In the present embodiment, the other end 47b of the delivery pipe 47 extends into the second cylindrical space 41b.

  A ring-shaped space 47c is formed on the outer periphery of the delivery pipe 47, and the inflow portion 42 opens into the ring-shaped space 47c. The refrigerant gas flowing in from the inflow portion 42 becomes a swirling flow, passes through the ring-shaped space 47 c, reaches the discharge port 44 along the inner peripheral surface of the cylindrical space 41, and then flows back in the center of the cylindrical space 41. . Then, it flows into the delivery pipe 47 from the other end 47 b of the delivery pipe 47 and flows out from one end 47 a of the delivery pipe 47.

As shown in the present embodiment, by providing the delivery pipe 47 in the cylindrical space 41, for example, even when the compressor is operated at a high frequency, the oil separation effect can be reliably obtained. When the delivery pipe 47 is provided, it is important that the axis of the cylindrical space 41 and the axis of the delivery pipe 47 are aligned. When the delivery pipe 47 is provided, the delivery pipe 47 can be fixed to the cylindrical space 41 by forming the delivery pipe 47 integrally with the muffler 19. In addition, the inner diameter cross-sectional area D of the delivery pipe 47 is made larger than the cross-sectional area B of the discharge port 44.

  According to the present embodiment, by providing the cylindrical delivery pipe 47 in the cylindrical space 41, the oil separation effect in the cylindrical space 41 can be enhanced.

  Also in the present embodiment in which the delivery pipe 47 is provided, the basic operation of the oil separation mechanism unit 40 is the same as that of the first embodiment, and the operations and effects in the first embodiment are also the same, so the description thereof is omitted. .

  The cylindrical space 41 is configured by a first cylindrical space 41a formed in the fixed scroll 12 and a second cylindrical space 41b formed in the main bearing member 11 as in the first embodiment. The second cylindrical space 41b may be formed by performing stepped hole processing on the outer peripheral portion of the main bearing member 11 as in the second embodiment.

(Embodiment 5)
FIG. 6 is a longitudinal sectional view of a compressor according to Embodiment 5 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG.

  In the present embodiment, the refrigerant gas swirling member 48 that constitutes the cylindrical space 41 is disposed in the one in-container space 31. The refrigerant gas swirling member 48 is installed on the outer peripheral surface of the muffler 19. The refrigerant gas swirling member 48 is formed with an inflow portion 42b, a delivery port 43b, and a discharge port 44b.

  The inflow portion 42b communicates with the inside of the muffler 19 and the cylindrical space 41, the delivery port 43b communicates with the cylindrical space 41 and one of the container internal spaces 31, and the discharge port 44b communicates with the cylindrical space 41 with one side. The container interior space 31 is communicated with. The opening of the inflow portion 42 b is formed on the inner peripheral surface on one end side of the cylindrical space 41. The inflow portion 42 b causes the refrigerant gas discharged from the compression mechanism portion 10 to flow into the cylindrical space 41 from the muffler 19. The inflow portion 42 b opens in the tangential direction with respect to the cylindrical space 41.

  The delivery port 43b is formed on one end side of the cylindrical space 41 and is formed on at least one end side of the inflow portion 42b. The delivery port 43b is preferably formed on the end face on one end side of the cylindrical space 41. And the delivery port 43b sends out the refrigerant gas which isolate | separated oil from the cylindrical space 41 to the one container inner space 31. FIG.

  The discharge port 44b is formed on the other end side of the cylindrical space 41, and is formed at least on the other end side than the inflow portion 42b. Moreover, the discharge port 44b is arrange | positioned facing the delivery port 43b. The discharge port 44b is preferably formed below the end surface on the other end side of the cylindrical space 41. The discharge port 44 b may be formed on the side surface on the other end side of the cylindrical space 41. Here, the term “opposing” includes not only the case where the discharge port 44 b is provided on the bottom surface of the cylindrical space 41, but also the case where it is provided on the side surface of the cylindrical space 41. The discharge port 44b discharges the separated oil and a part of the refrigerant gas from the cylindrical space 41 to the one in-container space 31. Here, the cross-sectional area A of the opening of the delivery port 43b is smaller than the cross-sectional area C of the cylindrical space 41 and larger than the cross-sectional area B of the opening of the discharge port 44b.

Hereinafter, the operation of the oil separation mechanism 40 according to the present embodiment will be described. The refrigerant gas discharged into the muffler 19 is guided to the cylindrical space 41 through an inflow portion 42 b formed on the upper surface of the muffler 19. Since the inflow portion 42 b opens in a tangential direction with respect to the cylindrical space 41, the refrigerant gas delivered from the inflow portion 42 b flows along the inner wall surface of the cylindrical space 41, and the inner periphery of the cylindrical space 41. A swirling flow is generated on the surface. This swirling flow is a flow toward the discharge port 44b. The refrigerant gas contains oil supplied to the compression mechanism unit 10, and while the refrigerant gas is swirling, the oil having a high specific gravity adheres to the inner wall of the cylindrical space 41 by centrifugal force, and the refrigerant gas and To separate.

  The swirling flow generated on the inner peripheral surface of the cylindrical space 41 turns back after reaching the discharge port 44b or in the vicinity of the discharge port 44b, and changes to a reverse flow passing through the center of the cylindrical space 41. The refrigerant gas from which the oil has been separated by the centrifugal force reaches the delivery port 43b by a flow passing through the center of the cylindrical space 41, and is delivered to the one in-container space 31. The refrigerant gas sent out to one container inner space 31 is sent out from the discharge pipe 4 provided in the one container inner space 31 to the outside of the sealed container 1 and supplied to the refrigeration cycle.

  Also, the oil separated in the cylindrical space 41 accumulates in one direction due to its own weight, and the discharge port 44b is formed in the lower part of the end face on the other end side or the lower part of the cylindrical space 41, so that the oil is easily discharged. it can. The separated oil is sent to the upper surface of the muffler 19 from the discharge port 44b together with a small amount of refrigerant gas. The oil sent to the upper surface of the muffler 19 passes through the gap of the compression mechanism portion 10 due to its own weight, reaches the compression mechanism side space 33 from one container inner space 31, and further passes through the wall surface of the sealed container 1 and the communication path of the electric motor portion 20. Then, the oil storage unit 2 is reached. The refrigerant gas sent out from the discharge port 44b is sent out from the discharge pipe 4 provided in one container inner space 31 to the outside of the sealed container 1 and supplied to the refrigeration cycle.

  In the oil separation mechanism 40 according to the present embodiment, the outlet 43b is formed on one end side of the cylindrical space 41 with respect to the inflow portion 42b, and the discharge port 44b is on the other end side of the cylindrical space 41 with respect to the inflow portion 42b. Form. Therefore, a swirl flow is generated on the inner peripheral surface of the cylindrical space 41 between the inflow portion 42b and the discharge port 44b, and swirl at the center of the cylindrical space 41 between the discharge port 44b and the delivery port 43b. A flow in the opposite direction to the flow is generated. Therefore, as the discharge port 44b moves away from the inflow portion 42b, the number of times the refrigerant gas turns increases and the oil separation effect increases. Moreover, since the refrigerant gas after turning passes through the center of the swirling flow, the delivery port 43b only needs to be on the side opposite to the outlet than the inflow portion 42b. That is, the effect of oil swirl separation can be enhanced by increasing the distance between the inflow portion 42b and the discharge port 44b as much as possible.

  In addition, the oil separation mechanism 40 according to the present embodiment discharges the oil together with the refrigerant gas from the discharge port 44b without storing the oil separated in the cylindrical space 41. An action of guiding the generated swirling flow toward the discharge port 44b is provided.

  If the discharge port 44b is not formed in the cylindrical space 41 and the oil is stored in the cylindrical space 41, a flow that pulls to the outside from the discharge port 44b does not occur, and the swirling flow winds up the oil. Further, in order to exhibit the oil separation function without forming the discharge port 44b in the cylindrical space 41, it is necessary to form a space sufficient to store oil. However, by discharging the oil from the discharge port 44b together with the refrigerant gas as in the oil separation mechanism unit 40 according to the present embodiment, the swirling flow can be guided to the discharge port 44b and the oil is not wound up.

  According to the present embodiment, it is possible to perform swivel separation without changing the axial dimension of the compressor. Further, in order to increase the number of revolutions of the refrigerant gas, it is possible to increase the distance between the cylindrical space 41, more specifically, the distance between the inflow portion 42b and the discharge port 44b. As a result, the oil separation mechanism 40 can be provided inside the sealed container 1 while maintaining the dimensions of the compressor itself, and the effect of oil swirl separation can be enhanced.

Further, according to the present embodiment, the refrigerant gas swirling member 48 constituting the cylindrical space 41 is arranged in the one container inner space 31, so that a path through which the refrigerant gas flows from the discharge port 17 to the discharge pipe 4 can be obtained. It can be configured to be short and the sealed container 1 can be miniaturized.

  According to the present embodiment, the high-temperature and high-pressure refrigerant gas compressed by the compression mechanism unit 10 and delivered from the oil separation mechanism unit 40 is guided to the one container inner space 31 and discharged from the discharge pipe 4. Therefore, since the high-temperature and high-pressure refrigerant gas does not pass through the electric motor unit 20, the electric motor unit 20 is not heated by the refrigerant gas, and the electric motor unit 20 can be highly efficient.

  Further, according to the present embodiment, since the high-temperature and high-pressure refrigerant gas is guided to the one container inner space 31, it is possible to suppress the heating of the compression mechanism unit 10 in contact with the other container inner space 32. Heating of the refrigerant gas can be suppressed, and high volumetric efficiency in the compression chamber can be obtained.

  Further, according to the present embodiment, the oil separated by the oil separation mechanism 40 is discharged together with the refrigerant gas into the one container inner space 31, so that the oil is mostly retained in the cylindrical space 41. No. Therefore, the separated oil is blown up in the cylindrical space 41 by the swirling refrigerant gas, and is not sent together with the refrigerant gas from the delivery port 43b, so that stable oil separation can be performed. Further, since the oil is not retained in the cylindrical space 41, the cylindrical space 41 can be made small. Moreover, according to this Embodiment, since the oil storage part 2 is arrange | positioned in the oil storage side space 34 and oil is not stored in the compression mechanism side space 33, the airtight container 1 can be reduced in size.

  Further, according to the present embodiment, the muffler 19 that isolates the discharge port 17 of the compression mechanism unit 10 from the one container inner space 31 is disposed, and the inside of the muffler 19 and the cylindrical space 41 are separated by the inflow portion 42b. By communicating, the refrigerant gas compressed by the compression mechanism unit 10 can be reliably guided to the oil separation mechanism unit 40. That is, since all the refrigerant gas passes through the oil separation mechanism 40, the oil can be efficiently separated from the refrigerant gas. Further, since the high-temperature refrigerant gas discharged from the discharge port 17 is discharged from the discharge pipe 4 to the outside of the sealed container 1 without passing through the other container inner space 32, the electric motor unit 20 and the compression mechanism unit 10. Can be suppressed.

  In the compressor in each of the above embodiments, two or more cylindrical spaces 41 may be provided.

  In the compressor in each of the above embodiments, carbon dioxide can be used as the refrigerant. Carbon dioxide is a high-temperature refrigerant, and the present invention is more effective when such a high-temperature refrigerant is used. When carbon dioxide is used as the refrigerant, it is preferable to use oil (PAG) mainly composed of polyalkylene glycol as the oil. PAG is a poorly compatible oil, does not dissolve in carbon dioxide refrigerant, and is mixed in a state separated from each other. Therefore, when the refrigerant gas and the PAG are introduced into the cylindrical space 41, a large centrifugal force acts on the PAG having a high specific gravity with respect to the refrigerant gas. As a result, the PAG is blown away in the outer peripheral direction and adheres to the inner wall of the cylindrical space 41, so that it can be separated from the refrigerant gas. That is, the effect according to the present invention is remarkably exhibited with respect to incompatible oil (or incompatible oil).

(Embodiment 6)
FIG. 8 is an enlarged cross-sectional view of the main part of the oil separation mechanism in the compressor according to Embodiment 6 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

In the present embodiment, the discharge port 44 is eccentric from the central axis of the cylindrical space 41.
At this time, it is preferable to decenter 10% or more of the cylindrical space diameter from the central axis. By decentering the discharge port 44 from the central axis of the cylindrical space 41, the ratio of the oil to be discharged and the refrigerant in a part of the refrigerant can be reduced and the ratio of the oil can be increased. Can get more. The reason why the ratio of the discharged refrigerant increases is that there is a large amount of oil separated by the swirl on the wall surface, and a large amount of separated refrigerant is present at the swivel center.

  In this embodiment, attention is paid to the fact that the separated oil adheres to the wall surface of the cylindrical space 41 by turning and accumulates in the lower part along the wall surface, and it is known that there is not much oil in the turning center part. . Further, the refrigerant swirled along the wall surface of the cylindrical space 41 flows to the post-delivery port 43 that has gathered at the center of the cylindrical space 41. For this reason, if the discharge port 44 exists in the turning center part, it is obstructed by the flow of the refrigerant and the oil is not smoothly discharged.

  By decentering the discharge port 44 from the central axis of the cylindrical space 41, the separated oil can be discharged smoothly, so that only the refrigerant gas from which the oil has been separated can be sent out, and the oil is discharged to the refrigeration cycle. It can suppress and can obtain a high heat exchange rate.

(Embodiment 7)
FIG. 9 is an enlarged cross-sectional view of the main part of the oil separation mechanism in the compressor according to Embodiment 7 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, the discharge port 44 is provided so as to be in contact with the wall surface of the cylindrical space 41. The discharge port 44 eccentric from the central axis of the cylindrical space 41 is in contact with the wall surface of the cylindrical space 41, and the basic action is the same as in the sixth embodiment. By providing the discharge port 44 so as to be in contact with the wall surface of the cylindrical space 41, the oil that has fallen along the wall surface of the cylindrical space 41 is discharged without accumulating on the bottom surface of the cylindrical space 41. Therefore, only the refrigerant gas from which the oil is further separated can be sent out, and the discharge of oil to the refrigeration cycle can be suppressed and a high heat exchange rate can be obtained.

(Embodiment 8)
FIG. 10 is an enlarged cross-sectional view of the main part of the oil separation mechanism in the compressor according to Embodiment 8 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, the discharge port 44 that is eccentric from the central axis of the cylindrical space 41 is provided on the wall surface of the cylindrical space 41. By providing the discharge port 44 in the wall surface of the cylindrical space 41, the oil that has fallen along the wall surface of the cylindrical space 41 is discharged without accumulating on the bottom surface of the cylindrical space 41, thereby smoothly discharging the separated oil. Therefore, only the refrigerant gas from which the oil is further separated can be sent out, the oil discharge to the refrigeration cycle can be suppressed, and a high heat exchange rate can be obtained.

(Embodiment 9)
FIG. 11 is an enlarged cross-sectional view of a main part of an oil separation mechanism in a compressor according to Embodiment 9 of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

In the present embodiment, out of the outlets 44 eccentric from the central axis of the cylindrical space 41, the outlets 43 are eccentric from the central axis of the cylindrical space 41. The direction is different. By shifting the eccentric direction of the discharge port 44 and the eccentric direction of the delivery port 43, the discharge port 44 is arranged in a direction in which the turning speed is fast and the oil is separated, so that the separated oil can be discharged without being mixed with the refrigerant again. Therefore, oil discharge to the refrigeration cycle can be suppressed and a high heat exchange rate can be obtained.

(Embodiment 10)
FIG. 12 is an enlarged perspective view of a main part of the oil separation mechanism in the compressor according to the tenth embodiment of the present invention. The basic configuration of the present embodiment is the same as that shown in FIG. Further, the same components as those described in FIGS. 1 and 2 are denoted by the same reference numerals, and the description thereof is partially omitted.

  In the present embodiment, a plurality of discharge ports 44 that are eccentric from the turning center axis are provided. Since the oil discharge effect in the first embodiment can be enhanced by providing a plurality of discharge ports 44 and all of the discharge ports being eccentric from the turning center axis, only the refrigerant gas from which the oil is further separated is sent out. It is possible to suppress oil discharge to the refrigeration cycle and obtain a high heat exchange rate.

  The present invention can be applied to a compressor having a compression mechanism section and an electric motor section in a sealed container such as a scroll compressor and a rotary compressor, and is particularly suitable for a compressor using a high-temperature refrigerant.

DESCRIPTION OF SYMBOLS 1 Airtight container 2 Oil storage part 4 Discharge pipe 10 Compression mechanism part 11 Main bearing member 12 Fixed scroll 17 Discharge port 19 Muffler 20 Electric motor part 31 Container inner space 32 Container inner space 33 Compression mechanism side space 34 Oil storage side space 40 Oil separation Mechanism part 41 Cylindrical space 42 Inflow part 43 Outlet 44 Outlet 46 Outlet pipe 47 Outlet pipe 48 Refrigerant gas swivel member

Claims (6)

A compression mechanism that compresses the refrigerant gas, and an electric motor that drives the compression mechanism are provided in a sealed container.
By the compression mechanism, the inside of the sealed container is divided into one container inner space and the other container inner space,
A compressor in which a discharge pipe for discharging the refrigerant gas from the one container inner space to the outside of the sealed container is provided, and the electric motor unit is disposed in the other container inner space;
An oil separation mechanism for separating oil from the refrigerant gas discharged from the compression mechanism;
The oil separation mechanism is
A cylindrical space for swirling the refrigerant gas;
An inflow portion for allowing the refrigerant gas discharged from the compression mechanism portion to flow into the cylindrical space;
A delivery port for sending out the refrigerant gas from which the oil is separated from the cylindrical space to the one container inner space;
A discharge port that is disposed opposite to the delivery port and discharges the separated oil and a part of the refrigerant gas from the cylindrical space;
The compressor in which the discharge port is eccentric from the central axis of the cylindrical space. The compression mechanism includes a fixed scroll, a turning scroll disposed opposite to the fixed scroll, and a main bearing member that supports a shaft that drives the turning scroll, and a cylindrical space is formed between the fixed scroll and the main scroll. The compressor according to claim 1, wherein the compressor is formed in a bearing member, and the discharge port communicates with the other container inner space. The compressor according to claim 1, wherein the discharge port is in contact with the cylindrical space wall surface. The compressor according to claim 1, wherein the discharge port is provided in the cylindrical space wall surface. The compressor according to any one of claims 1 to 4, wherein an eccentric direction of the discharge port is opposite to an eccentric direction of the delivery port. The compressor according to any one of claims 1 to 5, wherein a plurality of eccentric outlets are provided.