JP2008157172A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To improve holding performance of the oil content in a housing, by restraining splashing of the refrigerating machine oil stored in an oil storage part in a gas compressor. <P>SOLUTION: The inside of a case 11 has: a compressor body compressing refrigerant gas G; and a cyclone block 60 having a columnar space 64 surrounded by a cylindrical inner wall surface 61 centrifugally separating the refrigerating machine oil R from the refrigerant gas G by passing the refrigerant gas G delivered by being compressed by the compressor body, and by a bottom wall surface 62 continuing with this cylindrical inner wall surface 61. The cyclone block 60 is formed with a drain oil hole 65 draining the refrigerating machine oil R separated in the columnar space 64. The drain oil hole 65 is directly connected to an oil introducing passage 23 supplying the refrigerating machine oil R of the compressor body, and the refrigerating machine oil R drained from the drain oil hole 65 is prevented from blowing the refrigerating machine oil R stored in a bottom part of a delivery chamber 21. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a gas compressor, and in particular, to an improvement in an oil passage separated by an oil separator from compressed gas discharged from a compressor body.

  Conventionally, a gas compressor (compressor) for compressing a gas such as a refrigerant gas and circulating the gas through the air conditioning system is used in an air conditioning system (hereinafter referred to as an air conditioning system).

  Here, for example, a vane rotary type compressor is known as one of general compressors. This vane rotary type compressor has a configuration in which a compressor main body is accommodated in a housing.

  The main body of the compressor is a substantially cylindrical rotor that rotates integrally with the rotating shaft, a cylinder that surrounds the outside of the rotor, and a cylinder that is embedded in the rotor and has a substantially elliptical cross-sectional profile at the protruding end. A plate-like vane whose amount of protrusion from the outer peripheral surface of the rotor is variable so as to follow the inner peripheral surface of the rotor, and two side blocks that cover the rotor and the vane from both end surface sides of the rotor. .

  A plurality of compression chambers defined by two vanes that follow each other in the rotational direction of the rotor, the inner peripheral surface of the cylinder, the outer peripheral surface of the rotor, and the end surfaces of both side blocks are provided around the rotation axis. The volume of the chamber changes with the rotation of the rotor that rotates integrally with the rotating shaft, and the chamber is configured to compress and discharge the gas sucked into the chamber.

  In addition, a suction chamber having a low-pressure atmosphere through which the gas sucked into the compressor body passes is formed on one side of the compressor body between the inner surface of the housing and the outer surface of the compressor body. On the other side of the main body, a high-pressure atmosphere discharge chamber (a space through which the gas from which oil has been separated passes) through which the gas discharged from the compressor main body passes is formed.

  Here, the side block that defines the discharge chamber has a discharge path for guiding the high-pressure gas compressed in the compression chamber to the discharge chamber, and refrigeration oil mixed with the discharged gas, etc. An oil separator for centrifuging the oil component is attached.

  This oil separator has an inner wall surrounded by an inner wall surface that centrifuges the oil component with the momentum when compressed gas is discharged and a bottom wall surface continuous to the inner wall surface, and is separated in the inner space. The oil component is discharged to the oil storage part (bottom part of the discharge chamber) through the oil discharge hole.

  This oil component passes through the oil guide passage formed in the side block etc. from the oil storage part to apply back pressure for vane protrusion and to lubricate, clean, and cool the sliding part, and again into the compression chamber. Led.

  On the other hand, when the high-temperature and high-pressure gas after the oil component has been separated by the oil separator is refrigerant gas for the refrigeration cycle, it is discharged outside the gas compressor and cooled by the condenser to become medium-temperature and high-pressure liquefied refrigerant. The liquid-phase refrigerant separated from the gas-phase refrigerant in the liquid tank is rapidly expanded by the expansion valve to become a low-temperature and low-pressure mist-like liquefied refrigerant, and the evaporator exchanges heat with the air in contact with the outer surface of the evaporator. And is sucked into the compressor as a low-temperature and low-pressure gas-phase refrigerant (Patent Document 1).

A similar oil separator is also provided in other types of gas compressors such as a scroll type.
Japanese Patent Laid-Open No. 2003-090286

  By the way, the oil discharged from the oil separator drain of the gas compressor described above vigorously collides with the surface (oil surface) of the oil stored in the oil storage part. The oil component on the surface is splashed, and a part of the sprayed oil component floats in the discharge chamber and may be discharged to the outside along with the gas by the air flow discharged from the discharge chamber to the outside. It is not possible to ensure the oil retention performance in the interior.

  The present invention has been made in view of the above circumstances, and provides a gas compressor capable of preventing the oil from being splashed at the bottom of the discharge chamber and improving the retention of the oil in the housing. For the purpose.

  The gas compressor according to the present invention prevents the oil component from being ejected from the oil separator to the discharge chamber by the structure in which the oil discharge hole of the oil separator and the oil guide passage for supplying the oil component of the compressor body are directly connected. Thus, oil droplets at the bottom of the discharge chamber are prevented from being splashed, and the oil retention performance in the housing is improved.

  That is, the gas compressor according to the present invention includes a compressor main body that compresses gas inside the housing, and a compressed gas that is compressed and discharged by the compressor main body and passes through to centrifuge oil from the compressed gas. An oil separator having an inner space surrounded by an inner wall surface and a bottom wall surface continuous with the inner wall surface, and the oil separator has an oil drain hole for discharging the oil component separated in the inner space In the gas compressor in which is formed, the oil discharge hole and an oil guide passage for supplying the oil content of the compressor main body are directly connected.

  According to the gas compressor according to the present invention configured as described above, the oil component separated in the oil separator flows directly into the oil guide passage of the compressor body from the oil drain hole and is blown out to the discharge chamber. There is nothing.

  Therefore, it is possible to prevent the sprayed oil component from flowing out of the discharge chamber due to the air flow as in the prior art, without spraying the oil component stored in the bottom of the discharge chamber to spray the oil component. Therefore, the oil retention performance in the housing can be improved.

  In the gas compressor according to the present invention, it is preferable that the oil drainage hole has an opening on the oil guide passage side formed above the opening on the internal space side of the oil separator.

  In order to discharge oil from the internal space of the oil separator, it is preferable to open to the lowest bottom portion of the internal space. On the other hand, the oil guide passage formed in, for example, the side block of the compressor body is formed up to the shaft support portion of the rotating shaft that is a sliding portion, and this shaft support portion is located on the internal space side of the oil separator. The position is higher in the vertical direction than the opening. Therefore, by forming the opening on the oil guide passage side of the oil drain hole at a position higher than the opening on the internal space side, the oil content in the internal space of the oil separator can be smoothly guided through the oil drain hole. It is possible to join the road, and resistance due to the flow of oil can be suppressed.

  Further, in the gas compressor according to the present invention, the inner wall surface is a cylindrical inner circumferential surface that swirls along with the compressed gas, and is surrounded by a centrifugal separation main body composed of the inner wall surface and the bottom wall surface, and the cylindrical inner circumferential surface. A cylindrical gas exhaust that is disposed in the cylindrical space (inner space) along the axis of the cylindrical space and guides the swirled gas to the outside of the centrifugal separation main body from the end surface opposite to the bottom wall surface. It is preferable to apply an oil separator of the type provided with a part.

  This type of oil separator has a strong momentum for discharging oil from the oil drain hole. Therefore, in a conventional gas compressor equipped with this type of oil separator, the oil content stored in the oil storage part at the bottom of the discharge chamber is reduced. This is because they are easily formed into droplets, and therefore, the above-described effects of the present invention can be more remarkably exhibited.

  According to the gas compressor according to the present invention, it is possible to prevent the oil component stored in the oil storage unit from being splashed and to improve the retention property of the oil component in the housing.

  DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, the best embodiment of the gas compressor of the invention will be described with reference to the drawings.

  FIG. 1 is a longitudinal sectional view showing a vane rotary compressor 100 (gas compressor) which is an embodiment of a gas compressor according to the present invention, and FIG. 2 is a view showing a cross section along the line AA in FIG. FIG. 3 is an enlarged cross-sectional view of the cyclone block 60 (oil separator) in FIG.

  The illustrated compressor 100 is configured, for example, as a part of an air conditioning system (hereinafter simply referred to as an air conditioning system) that performs cooling using the heat of vaporization of a cooling medium, and condensing that is another component of the air conditioning system. A condenser (condenser), an expansion valve, an evaporator (evaporator), etc. (all of which are not shown) are provided on the circulation path of the cooling medium.

  The compressor 100 compresses the refrigerant gas G as a gaseous cooling medium taken from the evaporator of the air conditioning system, and supplies the high-temperature and high-pressure refrigerant gas G obtained by the compression to the condenser of the air conditioning system. .

  The condenser cools the high-temperature and high-pressure refrigerant gas G to form a medium-temperature and high-pressure liquefied refrigerant, and this liquefied refrigerant is rapidly expanded by an expansion valve to form a low-temperature and low-pressure mist, and is evaporated by the evaporator. Heat corresponding to the heat of vaporization is taken from the surrounding air, thereby cooling the surrounding air, while the low-temperature and low-pressure refrigerant gas G vaporized by evaporation returns to the compressor 100 to form a refrigeration cycle.

  The compressor 100 includes a compressor main body housed in a housing including a case 11 and a front head 12, and a transmission mechanism that is attached to the front head 12 and transmits a driving force from a power source (not shown) to the compressor main body. 13. The compressor body is fixed to the front head 12 by a plurality of bolts, and the transmission mechanism 13 is rotatably supported by the front head 12 via a radial ball bearing 14.

  The case 11 has a cylindrical body that is open at one end, and the front head 12 is assembled so as to cover the opened part of the case 11. Further, the front head 12 is formed with a suction port 12a through which low-pressure refrigerant gas G is sucked from the evaporator, and the suction port 12a is provided with a check valve 12b for preventing a reverse flow of the refrigerant gas G. . On the other hand, the case 11 is formed with a discharge port 11a for discharging the high-pressure refrigerant gas G compressed by the compressor body to the condenser.

  The compressor main body accommodated in the housing includes a rotating shaft 51 that rotates about the axis by a driving force supplied via the transmission mechanism 13, a columnar rotor 50 that rotates integrally with the rotating shaft 51, and The outer peripheral surface of the rotor 50 has an inner peripheral surface 49a having a substantially oval cross-sectional outline surrounding the outer surface, and is embedded in the rotor 50 so as to protrude toward the outer side of the rotor 50, and a cylinder 40 having both ends open. The amount of protrusion is variable so that the tip of the protrusion side follows the inner peripheral surface 49 a of the cylinder 40, and five plate-like vanes 58 arranged at equal angular intervals around the rotation shaft 51, It consists of a front side block 30 and a rear side block 20 fixed so as to cover the open end surfaces from the outside of the open end surfaces on both sides.

  The compression chambers defined by the two vanes 58 and 58 that follow each other in the rotation direction of the two side blocks 20 and 30, the rotor 50, the cylinder 40, and the rotating shaft 51 (clockwise arrow direction in FIG. 2). The volume of 48 is repeatedly increased and decreased according to the rotation of the rotating shaft 51, whereby the refrigerant gas G sucked into each compression chamber 48 is compressed and discharged.

  One of the portions of the rotating shaft 51 protruding from both end faces 50a and 50b of the rotor 50 is pivotally supported by the bearing portion 32 of the front side block 30 and penetrates the front head 12 to the outside. The penetrating portion is pivotally supported by the front head 12, and the portion extending outward is connected to the transmission mechanism 13.

  Similarly, the other side of the protruding portion of the rotating shaft 51 is pivotally supported by the bearing portion 22 of the rear side block 20, whereby the rotating shaft 51 is rotatable with respect to the rear side block 20 and the front side block 30. It is said that.

  Further, a lip seal 15 is disposed on a portion of the rotating shaft 51 outside the bearing portion 32 of the front side block 30 and inside the front head 12, and the refrigerating machine oil R is supplied to the rotating shaft 51. Leakage from the front head 12 through the gap between the front head 12 and the front head 12.

  The front shaft 12 is supported by the front head 12, the front side block 30 is fixed to the front head 12 by bolts, and the outer periphery of both side blocks 20, 30 is the inner periphery of the case 11, front head 12. The main body of the compressor is held at a predetermined position in the housing by holding on the surface.

  Further, in a state where the compressor main body is housed in the case 11, the rear side block 20 and the case 11 cause the high-pressure atmosphere discharge chamber 21 (refrigerator oil R () to discharge high-pressure refrigerant gas G from the compressor main body. A space through which the refrigerant gas G from which the oil component is separated passes is formed, and a suction chamber 34 in a low-pressure atmosphere that supplies the low-pressure refrigerant gas G to the compressor body is formed by the front side block 30 and the front head 12. Thus, the discharge chamber 21 communicates with the discharge port 11a, and the suction chamber 34 communicates with the suction port 12a. The suction chamber 34 and the discharge chamber 21 are hermetically isolated by the above-described O-ring or the like.

  In addition, a cyclone block 60 (oil separator) for separating the refrigeration oil R from the refrigerant gas G is attached to the rear side block 20, and the outer surface of the cyclone block 60 is exposed in the discharge chamber 21. Are arranged. A short columnar axial back pressure space 68 having an axis parallel to the axis of the rotating shaft 51 is formed between the rear side block 20 and the cyclone block 60.

  At the lower part of the discharge chamber 21, the sliding portion of the compressor 100 is lubricated, cooled, and cleaned, and the vane 58 protrudes toward the inner peripheral surface 49a of the cylinder 40, and the tip thereof extends to the inner peripheral surface 49a. A refrigerating machine oil R for applying a back pressure to the vane 58 is stored so as to urge the contacted state.

  Here, in order to ensure adequate lubrication on the suction port 12a side and the like of the compressor 100, a certain amount of the refrigeration oil R is circulated in the refrigeration cycle. When the engine is stopped, the refrigeration oil R in the refrigeration cycle flows backward from the condenser side due to the influence of changes in temperature and pressure in the refrigeration cycle, or the refrigeration oil R supplied into the compressor body flows backward. The refrigerating machine oil R is stored at the bottom of the discharge chamber 21.

  Further, even if the refrigerant gas G has been separated from the refrigerating machine oil R by the cyclone block 60, since some refrigerating machine oil R is mixed, the inside of the discharge chamber 21 is discharged before being discharged from the discharge port 11a. When the refrigerant gas G comes into contact with the wall surface, the outer surface of the cyclone block 60, the outer surface of the rear side block 20, or the like, a part of the mixed refrigerating machine oil R adheres to these surfaces, and the oil of the adhering refrigerating machine oil R The droplets flow down to the bottom of the discharge chamber 21, and the refrigerating machine oil R is collected at the bottom.

  As shown in FIG. 2, the rotor 50 is formed with five slit-like vane grooves 56 at equal angular intervals around the rotation center of the rotor 50, and the vane 58 described above is formed in these vane grooves 56. , And each vane 58 is applied to the centrifugal force generated by the rotation of the rotor 50 and the refrigerating machine oil R applied to the back pressure chamber 59 (part of the back pressure space) defined by the vane groove 56 and the bottom surface of the vane 58. The oil pressure (back pressure) of the rotary shaft 51 protrudes toward the inner peripheral surface 49a of the cylinder 40 and is biased so that the protruding tip of the vane 58 is in contact with the inner peripheral surface 49a of the cylinder 40. With rotation, the tip follows the inner peripheral surface 49a.

  As a result, each compression chamber 48 defined by the cylinder 40, the rotor 50, the two vanes 58 and 58 that are arranged in the rotational direction of the rotating shaft 51, the front side block 30, and the rear side block 20 is The volume change is repeated according to the rotation of the rotor 50.

  Further, the front side block 30 is provided with a front suction port 31 that allows the suction chamber 34 and the compression chamber 48 to communicate with each other. The refrigerant gas G introduced into the suction chamber 34 from the suction port 12a is transferred to the front side block 30. The air is sucked into the compression chamber 48 through the suction port 31.

  On the other hand, a recess is formed in a part of the outer periphery of the cylinder 40, and this recess forms a discharge chamber 45 surrounded by the inner end surfaces of the side blocks 20 and 30 and the inner peripheral surface of the case 11. .

  Then, the refrigerant gas G in the compression chamber 48 is transferred to the outside of the compression chamber 48 in a portion facing the compression chamber 48 corresponding to the compression stroke of the refrigerant gas G in the thinned cylinder 40 in which the discharge chamber 45 is formed. That is, a discharge port 42 that discharges to the discharge chamber 45 is provided, and a reed valve 43 that opens and closes the discharge port 42 according to the internal pressure of the compression chamber 48 is disposed.

  The reed valve 43 has a leaf spring shape, and the pressure acting from the refrigerant gas G in the compression chamber 48 through the discharge port 42 (specifically, this pressure and the pressure inside the discharge chamber 45 (further, the reed valve 43 is connected to the discharge port). 42 is elastically deformed so as to bend toward the discharge chamber 45 in accordance with the difference between the initial load pressure corresponding to the urging force and the pressure obtained by adding the initial load pressure). The discharged discharge port 42 is opened.

  In addition, in order to prevent the reed valve 43 from being damaged due to excessive bending or from being permanently deformed due to sustained large bending, a valve support 44 that regulates the deformation amount of the reed valve 43 is superimposed on the reed valve 43. And fastened to the cylinder 40 together.

  The high-pressure refrigerant gas G discharged from the compression chamber 48 to the discharge chamber 45 through the discharge port 42 and the reed valve 43 is introduced into the cyclone block 60 through the rear side block 20.

  The cyclone block 60 is a circle surrounded by a cylindrical inner wall surface 61 (inner wall surface, cylindrical inner peripheral surface) for rotating the high-temperature and high-pressure refrigerant gas G discharged from the discharge chamber 45 and a bottom wall surface 62 continuous to the cylindrical inner wall surface 61. A centrifugal separation body 63 for centrifuging the refrigerating machine oil R contained in the refrigerant gas G, which has a columnar space 64 (internal space), is coaxial with the central axis of the cylindrical space 64 in the cylindrical space 64. An inner cylindrical gas exhaust portion 66 that guides the refrigerant gas G swirled from the end surface (upper surface in FIG. 1) side opposite to the bottom wall surface 62 to the outside of the centrifugal separation main body 63 is provided. .

  In the upper part of the centrifugal separation body 63 of the cyclone block 60, the introduction hole 61a for introducing the refrigerant gas G discharged from the discharge chamber 45 and passing through the rear side block 20 into the cylindrical space 64 along the cylindrical inner wall surface 61. In the lower part of the centrifugal separation body 63, an oil drain hole 65 for discharging the refrigerating machine oil R separated in the cylindrical space 64 from the cylindrical space 64 is formed.

  As shown in detail in FIG. 3, the oil drain hole 65 is directly connected to an oil guide path 23 formed in the rear side block 20 described later.

  In addition, the oil discharge hole 65 is such that the opening 65b on the oil guide passage 23 side is located above the opening 65a on the cylindrical space 64 side of the centrifugal separation body 63, and is inclined at a constant angle as a whole. Yes.

  On the other hand, after the refrigerant gas G introduced into the centrifugal separation main body 63 from the introduction hole 61a spirals downward along the cylindrical inner wall surface 61 to centrifuge the refrigerating machine oil R, A hollow cylinder portion 66b having an upper opening 66a for exhausting the refrigerant gas G from the upper portion of the centrifugal separation main body portion 63 to the outside of the centrifugal separation main body portion 63 is provided.

  The high-temperature and high-pressure refrigerant gas G exhausted to the outside of the centrifugal separation body part 63 through the hollow cylinder part 66b passes through the discharge chamber 21 and the discharge port 11a and becomes a condenser of the air conditioning system constituting the refrigeration cycle. Discharged.

  The compressor 100 is provided with a vane 58 for the purpose of lubrication between the rotary shaft 51 and the bearings 22 and 32, lubrication between the end surfaces of the rotor 50 and the inner end surfaces of the side blocks 20 and 30, and the like. For the purpose of supplying hydraulic pressure (back pressure) to the back pressure space (back pressure chamber 59, salai groove 25 and shaft back pressure space 68 described later) to urge the inner peripheral surface 49a of the cylinder 40, the discharge chamber 21 is provided. The structure which guides the refrigerating machine oil R stored in the lower part of each to each part is provided.

  That is, the oil guide passage 23 reaching the bearing portion 22 is formed in the rear side block 20, and the oil guide passage in the bearing portion 22 is formed on the inner end surface 26 of the rear side block 20 (surface facing the end surface 50 a of the rotor 50). A salai groove 25, which is a recess communicating with the back pressure chamber 59 of the rotor 50, is formed from the opening 23 through a minute gap (throttle) between the bearing portion 22 and the rotating shaft 51.

  Specifically, the oil guide passage 23 is connected to the oil guide passage 23a extending from the bottom of the discharge chamber 21 to the bearing portion 22, the opening 65b of the oil discharge hole 65, and the oil guide passage 23b joining the oil guide passage 23a. It is constituted by an oil guide passage 23c branched from the oil guide passage 23a and connected to a through hole 46 of a cylinder 40 described later.

  The oil guide passage 23 a supplies the refrigeration oil R stored in the bottom of the discharge chamber 21 to the bearing 22 from the opening on the bottom side by the pressure in the discharge chamber 21, and the oil guide passage 23 b is connected to the cyclone block 60. All the refrigerating machine oil R separated in the cylindrical space 64 and discharged from the oil drain hole 65 by the pressure and the swirling flow in the cylindrical space 64 is joined to the refrigerating machine oil R fed to the oil guide path 23a. , A part is supplied to the bearing 22 or the like, and the oil guide passage 23c branches from the oil guide passage 23a and supplies the refrigeration oil R supplied to the oil guide passage 23a to the front side block 30 side.

  The oil guide passage 23 a is also provided in the shaft back pressure space 68, which is a space formed between the rear side block 20 and the cyclone block 60, through a minute gap (throttle) between the bearing portion 22 and the rotating shaft 51. The shaft back pressure space 68 communicates with the Sarai groove 25 through the back pressure communication passage 28 without pressure loss.

  Thereby, the back pressure chamber 59, the Sarai groove 25, the back pressure communication path 28, and the shaft back pressure space 68 have substantially the same pressure Pv, and constitute the back pressure space of the vane 58.

  Specifically, the pressure Pv acting on the back pressure space is higher than the pressure Ps of the suction chamber 34 in the low-pressure atmosphere, and is a minute gap between the bearing 22 and the peripheral surface portion of the rotating shaft 51. The intermediate pressure (Ps <Pv <Pd) is lower than the pressure Pd of the discharge chamber 21 in the high-pressure atmosphere by the amount that has passed through the (throttle).

  The Sarai groove 25 is a concave portion having a substantially fan-shaped outline (shown by a broken line in FIG. 2) over a predetermined angular range around the center of the bearing portion 22, and passes through the above-described minute gap to the intermediate pressure Pv. The lowered refrigerator oil R is stored.

  Then, as the rotor 50 rotates, the back pressure of the vane groove 56 is only while the back pressure chamber 59 of the vane groove 56 exposed to the end surface 50 a of the rotor 50 passes through the Sarai groove 25 of the rear side block 20. The space 59 and the Sarai groove 25 communicate with each other, the refrigerating machine oil R having the intermediate pressure Pv in the Saray groove 25 is supplied to the back pressure space 59 in the vane groove 56, and the vane 58 has the intermediate pressure Pv of the supplied refrigerating machine oil R. In response, it protrudes toward the inner peripheral surface 49 a of the cylinder 40.

  Further, a through hole 46 connected to the oil passage 23 of the rear side block 20 is provided on the bottom side of the cylinder 40, and an opening on the front side block 30 side of the through hole 46 and the bearing portion 32 are provided in the front side block 30. The refrigerating machine oil R is lowered to the intermediate pressure Pv through a minute gap between the bearing portion 32 and the rotary shaft 51 and is formed on the inner end face of the front side block 30. It is guided to the Sarai groove 35, which is a concave portion.

  The salai groove 35 of the front side block 30 also communicates with the back pressure chamber 59 of the rotor 50, similar to the saray groove 25 of the rear side block 20.

  When the back pressure chamber 59 of the vane groove 58 of the rotor 50 communicates with the refrigerating machine oil R supplied to the Sarai grooves 25 and 35, the thrust output of the vane 58 acts on the back pressure chamber 59. Including the angle range where 59 does not communicate with each other, it penetrates between the end faces 50a, 50b of the rotor 50 and the end faces of the side blocks 20, 30, etc., and between the end faces facing each other or between the side blocks 20, 30 A sliding frictional force is reduced at a portion that slides by relative movement, such as between the end surface and the side surface of the vane 58, or between the tip of the vane 58 and the inner peripheral surface 49a of the cylinder 40.

  The refrigerating machine oil R that has permeated into the sliding portions is mixed into the refrigerant gas G in the compression chamber 48, is discharged from the compression chamber 48 together with the refrigerant gas G, and is supplied to the oil guide path 23 through the cyclone block 60. Or stored in the bottom of the discharge chamber 21.

  According to the compressor 100 according to this embodiment configured as described above, the high-pressure refrigerant gas G discharged from the discharge chamber 45 passes through the rear side block 20 and is introduced into the columnar shape of the centrifugal separation main body 63 from the introduction hole 61a. It is introduced inside the space 64.

  The refrigerant gas G introduced into the cylindrical space 64 spirals in the downward direction D along the circumferential direction of the cylindrical inner wall surface 61 by the momentum of the air flow of the refrigerant gas G when discharged from the discharge chamber 45. Descent. As a result, the refrigerating machine oil R contained in the refrigerant gas G is centrifuged at the cylindrical inner wall surface 61, and the separated refrigerating machine oil R flows into the bottom wall surface 62 and flows into the drain hole 65 through the opening 65a. It flows into the oil guide passage 23 from the opening 65b.

  Thereby, the refrigerating machine oil R separated from the refrigerant gas G in the cyclone block 60 does not blow the oil surface of the refrigerating machine oil R accumulated in the bottom part (oil storage part) of the discharge chamber 21.

  Accordingly, it is possible to prevent the refrigerating machine oil R from being splashed by spraying the refrigerating machine oil R discharged from the cyclone block 60 onto the oil surface of the refrigerating machine oil R accumulated in the oil storage part, and the refrigeration that has been sprayed in that way. The machine oil R can be prevented from flowing out of the discharge chamber 21 due to the airflow in the discharge chamber 21. Therefore, the oil retention performance in the housing (case 11 and front head 12) of the cyclone block 60 can be improved.

  Further, in order to discharge the refrigerating machine oil R from the cylindrical space 64 of the cyclone block 60, the opening 65 a on the cylindrical space 64 side of the oil drain hole 65 opens to the lowest bottom wall surface 62 portion of the cylindrical space 64. It is preferable. On the other hand, the oil guide passage 23 a formed in the side block 20 of the compressor main body is formed up to the bearing 22 of the rotating shaft 51 which is a sliding portion. The bearing 22 is a cylindrical space 64 of the cyclone block 60. It becomes a position higher in the illustrated vertical direction than the opening 65a on the side.

  And since the compressor 65 of this embodiment is formed in the position where the opening 65b by the side of the oil guide path 23 of the oil drain hole 65 is higher than the opening 65a in the cylindrical space 64 side of the centrifugal separation main-body part 63, The refrigerating machine oil R in the cylindrical space 64 of the centrifugal separation body 63 can be smoothly joined to the oil guide passage 23 (particularly the oil guide passage 23a) via the oil drain hole 65, and the oil guide passage 23b. It is possible to suppress the refrigerating machine oil R that has flowed into the flow resistance of the refrigerating machine oil R being pumped through the oil guide path 23a.

  Further, the compressor 100 according to the present embodiment has a centrifugal separation body 63 composed of a cylindrical inner wall surface 61 and a bottom wall surface 62, and a columnar space 64 surrounded by the cylindrical inner wall surface 61. The cyclone block 60 is provided with a cylindrical gas exhaust part 66 that is disposed along the swirling refrigerant gas G and guides the swirling refrigerant gas G from the end surface side opposite to the bottom wall surface 62 to the outside of the centrifugal separation body 63. However, since the cyclone block 60 of this type has a strong momentum for discharging the refrigerating machine oil R from the oil discharge hole 65, the conventional gas compressor provided with this type of cyclone block 60 uses the refrigerating machine oil R of the oil storage section. It is easy to make it splash, and therefore, a more remarkable effect can be exhibited as compared with the case where the above-described configuration is applied to another type of cyclone block.

  In addition, although the compressor 100 of each embodiment mentioned above is a vane rotary type gas compressor, the gas compressor which concerns on this invention is not limited to the thing of the vane rotary type which is this embodiment, The present invention can also be applied to other types of gas compressors, for example, swash plate type or scroll type gas compressors.

It is a longitudinal section showing a vane rotary type compressor which is one embodiment of a gas compressor concerning the present invention. It is sectional drawing by the surface along the AA line in FIG. It is a figure which shows the expansion of the cyclone block in FIG.

Explanation of symbols

21 Discharge chamber 23, 23a, 23b, 23c Oil guide path 60 Cyclone block (oil separator)
61 Cylinder inner wall surface (inner wall surface, cylinder inner peripheral surface)
62 Bottom wall surface 63 Centrifuge body 64 Cylindrical space (internal space)
65 Oil drainage hole 65a Cylindrical space side opening 65b Oil guide passage side opening 100 Compressor (gas compressor)
G Refrigerant gas (gas)
R Refrigerating machine oil (oil content)
Rs Oil level

Claims (3)

Inside the housing are a compressor main body for compressing gas, an inner wall surface through which the compressed gas compressed and discharged by the compressor main body passes and centrifugally separates oil from the compressed gas, and a bottom continuous to the inner wall surface An oil separator having an internal space surrounded by wall surfaces, the oil separator having a drainage hole for discharging the oil separated in the internal space;
The gas compressor, wherein the oil discharge hole and an oil guide passage for supplying the oil content of the compressor body are directly connected.   2. The gas compressor according to claim 1, wherein the oil discharge hole has an opening on the oil guide passage side formed above an opening on the inner space side. The inner wall surface is a cylindrical inner circumferential surface on which the compressed gas swirls,
The oil separator is disposed along the axis of the columnar space in a columnar space surrounded by the centrifugal separation body portion composed of the inner wall surface and the bottom wall surface and the inner circumferential surface of the cylinder, 3. The gas compressor according to claim 1, further comprising a cylindrical gas exhaust unit that guides the gas that has been discharged from an end surface side opposite to the bottom wall surface to the outside of the centrifugal separation main body unit.

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