JP2010001835A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas compressor capable of suppressing oil content from being discharged to the outside thereof by preventing the oil content from being excessively stagnated in the inner space of an oil separator. <P>SOLUTION: An oil discharge hole 61d for discharging the refrigerating machine oil R flowing down on a bottom wall surface 61c to an oil discharge section (bottom section of a discharge chamber 21) is formed in a cyclone block 60. The oil discharge hole 61d is formed in such a manner that the bottom edge 61e thereof is lower than the bottom wall surface 61c. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

  The present invention relates to a gas compressor, and more particularly to an improvement in an oil separator that centrifuges oil 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. .

  The volume changes with the rotation of the rotor by the 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, and compresses the sucked gas Thus, a plurality of compression chambers for discharging are defined.

  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 space surrounded by an inner peripheral wall surface for centrifuging the oil component at a moment when compressed gas is discharged, and a bottom wall surface from which the separated oil component flows down. The separated oil is discharged from a drain hole formed in a portion of the peripheral wall formed in the vicinity of the bottom wall surface by the swirling flow of gas, and is stored in the lower part (oil storage part) of the discharge chamber.

  On the other hand, the gas after swirling in the internal space and separating the oil component is exhausted from the oil separator and discharged to the outside of the gas compressor through the discharge chamber (Patent Document 1).

Note that a similar oil separator is also provided in other types of gas compressors such as a scroll type.
JP 11-82352 A

  However, although the oil drainage hole is formed in the portion of the peripheral wall near the bottom wall surface, the bottom edge of the oil drainage hole is formed at a position higher than the bottom wall surface of the internal space. The oil component is accumulated between the bottom wall surface and the bottom edge of the oil drainage hole that is higher than the bottom wall surface, and the oil is hardly discharged from the internal space.

  And the oil which stayed on the bottom wall surface of the internal space in this way is rolled up by the rising air flow when the gas descending while turning to the bottom of the internal space rises up the internal space and is exhausted from the oil separator The oil thus wound up is discharged to the outside of the gas compressor together with the gas, and there is a risk that the amount of oil inside the gas compressor is excessively reduced.

  The present invention has been made in view of the above circumstances, and is a gas compressor that can prevent oil from staying excessively in the internal space of the oil separator and suppress the discharge of oil to the outside of the gas compressor. The purpose is to provide.

  The gas compressor according to the present invention is formed so that the bottom edge of the oil drain hole of the oil separator is positioned lower than the bottom wall surface defining the internal space, so that the oil content on the bottom wall surface is discharged. There is nothing to prevent the oil from flowing into the oil hole, and it is possible to prevent the oil from being excessively retained in the internal space of the oil separator, thereby suppressing the oil from being discharged out of the gas compressor.

  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 peripheral wall surface and a bottom wall surface from which the separated oil component flows down, and the oil separator discharges the oil component that has flowed down to the bottom wall surface to an oil storage section. In the gas compressor in which the oil drain hole is formed, the oil drain hole is formed so that a bottom edge thereof is positioned lower than the bottom wall surface.

  According to the gas compressor according to the present invention configured as described above, since the bottom edge of the oil drain hole is formed at a position lower than the bottom wall surface, the oil component that has flowed down on the bottom wall surface is drained. When the oil flows into the hole, it does not prevent the oil from getting over the bottom edge of the oil discharge hole, the oil on the bottom wall flows smoothly into the oil discharge hole, and the oil stays excessively on the bottom wall. It suppresses, the winding-up of the staying oil part by gas is suppressed, and discharge | emission of the oil part out of a gas compressor can be suppressed.

  According to the gas compressor which concerns on this invention, it can prevent that an oil component retains excessively in the internal space of an oil separator, and can suppress discharge | emission of the oil component outside a gas compressor.

  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 taken along line AA in the compressor 100 shown in FIG. FIG. 3 is a diagram showing details of the cyclone block 60 in the compressor 100 shown 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. Along with a condenser, an expansion valve, an evaporator, and the like (all not shown), they are provided on a cooling medium circulation path.

  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 compressed refrigerant gas G to the condenser of the air conditioning system. The condenser liquefies the compressed refrigerant gas G and sends it to the expansion valve as a high-pressure liquid refrigerant.

  The high-pressure liquid refrigerant is reduced in pressure by the expansion valve and sent to the evaporator. The low-pressure liquid refrigerant absorbs heat from ambient air and vaporizes in the evaporator, and cools the air around the evaporator by heat exchange with the heat of vaporization.

  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.

  The front head 12 is formed with a suction port 12a through which a low-pressure refrigerant gas G is sucked from the evaporator, and a check valve 12b for preventing the refrigerant gas G from flowing backward is provided at the suction port 12a. 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 together with the rotating shaft 51, and the rotor 50. A cylinder 40 having a substantially elliptical inner peripheral surface 49a surrounding the outer periphery of the outer peripheral surface and open at both ends, and the rotor 50 so as to protrude outward of the rotor 50 as shown in FIG. And 5 plate-like vanes 58 arranged at equal angular intervals around the rotating shaft 51, with the protruding amount being variable so that the tip of the protruding side follows the inner peripheral surface 49a of the cylinder 40. The cylinder 40 includes 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.

  Then, each compression defined by two vanes 58 and 58 that follow each other in the rotational 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 chamber 48 is configured so that the refrigerant gas G sucked into the compression chambers 48 is compressed and discharged by repeatedly increasing and decreasing according to the rotation of the rotary shaft 51.

  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. This outwardly extending portion 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.

  Then, the front side block 30 and the cylinder 40 are fixed to the front head 12 by bolts, and the outer peripheral portions of the side blocks 20 and 30 are held on the inner peripheral surface of the case 11 and the front head 12 by O-rings. Thus, the compressor body is held at a predetermined position in the housing.

  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 be discharged from the compressor main body to discharge high-pressure refrigerant gas G). A space through which the separated refrigerant gas G passes) is formed, while the front side block 30 and the front head 12 form a low-pressure atmosphere suction chamber 34 for supplying a low-pressure refrigerant gas G to the compressor body, 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.

  The rear side block 20 is provided with a cyclone block 60 (oil separator) that centrifuges the refrigerating machine oil R from the refrigerant gas G. The cyclone block 60 has an outer surface exposed in the discharge chamber 21. Has been placed. A short columnar axial back pressure space 68 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.

  That is, as shown in FIG. 2, the rotor 50 is formed with five slit-like vane grooves 56 radially and at equal angular intervals around the rotation center of the rotor 50. A vane 58 is inserted, and each vane 58 is subjected to a centrifugal force generated by the rotation of the rotor 50 and a freezing applied to a back pressure chamber 59 (a part of the back pressure space) defined by the vane groove 56 and the bottom surface of the vane 58. Due to the hydraulic pressure (back pressure) of the machine oil R, it protrudes toward the inner peripheral surface 49a of the cylinder 40, and the protruding tip of the vane 58 is urged to abut against the inner peripheral surface 49a of the cylinder 40, so that the rotating shaft With the rotation of 51, 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 provided on the reed valve 43. It is overlapped and fixed 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 compressed by the compressor body and passes through the refrigerant gas G discharged through the introduction hole 61a, and the inner peripheral wall surface 61b that centrifuges the refrigerating machine oil R from the refrigerant gas G, and the separated refrigerating machine oil. There is an internal space 63 surrounded by a bottom wall surface 61c where R flows down, and an oil drain hole 61d for discharging the refrigerating machine oil R flowing down to the bottom wall surface 61c toward the oil storage part (the bottom part of the discharge chamber 21) in the direction of arrow F. Is formed.

  Here, as shown in FIG. 3, the oil drain hole 61d is formed such that its bottom edge 61e is positioned lower than the bottom wall surface 61c.

  The inner peripheral wall surface 61b is a surface in which the refrigerant gas G descends while swirling along, and the cyclone block 60 has a centrifugal separation main body 61 composed of an inner peripheral wall surface 61b and a bottom wall surface 61c, and an internal space 63, A substantially cylindrical shape that is arranged substantially coaxially with the space 63 and guides the refrigerant gas G swirling on the inner peripheral wall surface 61b to the outside of the centrifugal separation main body 61 from the end surface side of the inner space 63 opposite to the bottom wall surface 61c. The hollow cylinder part 62 of this.

  The refrigerant gas G guided to the outside of the centrifugal separation body 61 through the hollow cylinder portion 62 is supplied to the outside of the compressor 100 through the discharge chamber 21 and the discharge port 11a.

  In the compressor 100 of the present embodiment, the oil drain hole 61d is formed to extend in the horizontal direction, but is not limited to this form.

  That is, for example, the oil drain hole 61d may be formed such that the bottom edge of the opening on the oil storage section side is lower than the bottom edge of the opening on the internal space 63 side. As described above, the oil drain hole 61d is formed so as to be inclined toward the oil storage section, so that the oil component is less likely to stay on the oil drain hole 61d and is easily drained into the oil storage section.

  In the compressor 100 according to the present embodiment, lubrication between the rotary shaft 51 and the bearing portions 22 and 32, the end faces 50a and 50b of the rotor 50, and the inner end faces 29 and 39 of the side blocks 20 and 30 are provided. The purpose is to lubricate the gap, and hydraulic pressure (back pressure) is applied to the back pressure space (back pressure chamber 59, salai groove 25 and shaft back pressure space 68, which will be described later) to bias the vane 58 toward the inner peripheral surface 49a of the cylinder 40. For example, the refrigerator oil R stored in the lower part of the discharge chamber 21 is guided to each part.

  That is, the oil passage 23 reaching the bearing portion 22 is formed in the rear side block 20, and the inner end surface (surface facing the end surface 50 a of the rotor 50) 29 of the rear side block 20 is formed on the oil passage 23 in the bearing portion 22. A salai groove 25 is formed as a recess that communicates with the back pressure chamber 59 of the rotor 50 through the minute gap (throttle) between the bearing portion 22 and the rotating shaft 51 from the opening.

  Further, the oil passage 23 extending to the bearing portion 22 is a space formed between the rear side block 20 and the cyclone block 60 via a minute gap (throttle) between the bearing portion 22 and the rotating shaft 51. The shaft back pressure space 68 also communicates with the saray groove 25 via 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. Reduced refrigeration oil R is supplied.

  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 passes through a minute gap between the bearing portion 32 and the rotary shaft 51 and is lowered to the intermediate pressure Pv, and the inner end face of the front side block 30 (of the rotor 50) is formed. The surface facing the end face 50b) 39 is guided to the Sarai groove 35, which is a recess formed in the surface 39.

  The salai groove 35 of the front side block 30 communicates with the back pressure chamber 59 of the rotor 50, and the intermediate pressure Pv of the salai groove 35 in the back pressure space 59 of the vane groove 56, similarly to the salai groove 25 of the rear side block 20. The refrigerating machine oil R is supplied, and the vane 58 receives the intermediate pressure Pv of the supplied refrigerating machine oil R and protrudes toward the inner peripheral surface 49 a of the cylinder 40.

  Further, the rear side block 20 prevents the vane 58 from separating from the inner peripheral surface 49a of the cylinder 40 due to the high pressure in the compression chamber 48 at the end of the compression stroke (the pressure in the compression chamber 48 is the highest). For the purpose, in order to supply the refrigerating machine oil R of higher pressure (≈Pd) to the back pressure chamber 59, the high pressure oil passage 27 branches from the oil passage 23 and extends directly to the inner end face 29 of the rear side block 20 without passing through the throttle. Is formed. A similar high pressure oil passage 37 is also formed in the front side block 30.

  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 surfaces 50a, 50b of the rotor 50 and the end surfaces 29, 39 of the side blocks 20, 30, respectively, and between these end surfaces 50a, 29, the end surface 50b, The sliding frictional force at the sliding portion is reduced, such as between 39, between the end surfaces 29, 39 of the side blocks 20, 30 and the side surface of the vane 58, and between the tip of the vane 58 and the inner peripheral surface 49 a of the cylinder 40. ing.

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

  According to the compressor 100 according to the present embodiment configured as described above, the high-pressure refrigerant gas G introduced into the internal space 63 of the centrifugal separation body 61 from the introduction hole 61a of the cyclone block 60 is the inner peripheral wall surface 61b. In this turning process, the refrigerating machine oil R is centrifuged by the centrifugal force, and the separated refrigerating machine oil R flows down to the bottom wall surface 61c along the inner peripheral wall surface 61b.

  The refrigerant gas G from which the refrigerating machine oil R has been separated while descending to the bottom wall surface 61c is reversed from the bottom wall surface 61c, rises in the center of the internal space 63, passes through the inside of the hollow cylindrical portion 62, and passes through the bottom wall surface 61c. From the opposite end face side, the air is exhausted to the outside of the centrifugal separation body 61 (discharge chamber 21), passes through the discharge chamber 21, and is discharged to the air conditioning system through the discharge port 11a.

  On the other hand, the refrigerating machine oil R separated from the refrigerant gas G and flowing down to the bottom wall surface 61c is discharged from the internal space 63 to the oil storage part (the bottom part of the discharge chamber 21) through the oil discharge hole 61d. Since the bottom edge 61e is formed to be lower than the bottom wall surface 61c, when the refrigerating machine oil R that has flowed down on the bottom wall surface 61c flows into the oil drainage hole 61d, the bottom edge 61e of the oil drainage hole 61d is The refrigerating machine oil R on the bottom wall surface 61c smoothly flows into the oil discharge hole 61d without being overridden, and the refrigerating machine oil R is prevented from excessively stagnating on the bottom wall surface 61c, and the central portion of the internal space 63 As a result, the refrigerating machine oil R rising by the refrigerant gas G is suppressed from being wound, and excessive discharge of the refrigerating machine oil R to the outside of the compressor 100 can be suppressed.

  Since the oil drain hole 61d is formed to extend in a substantially horizontal direction, the refrigerating machine oil R discharged from the oil drain hole 61d is directly on the oil surface Rs of the refrigerating machine oil R stored in the bottom of the discharge chamber 21. Therefore, the mist of the refrigerating machine oil R that is likely to be generated due to the collision between the oil surface Rs and the discharged refrigerating machine oil R can be prevented. 100 Excessive discharge of the refrigerating machine oil R to the outside can also be prevented.

  Further, the cyclone block 60 of the compressor 100 of the present embodiment has an inner peripheral wall surface 61b on which the compressed refrigerant gas G turns, and the cyclone block 60 includes an inner peripheral wall surface 61b and a bottom wall surface 61c. In the inner space 63, the centrifugal separation body 61 is disposed substantially coaxially with the inner space 63, and the refrigerant gas G swirling on the inner peripheral wall surface 61b is passed through the end surface of the inner space 63 opposite to the bottom wall surface 61c. The refrigerant gas G from which the refrigerating machine oil R has been separated is smoothly exhausted to the outside of the cyclone block 60 by the configuration having the substantially cylindrical hollow cylinder portion 62 that leads to the outside of the centrifugal separation body portion 61 from the side. Can do.

  In addition, although the compressor 100 which concerns on this embodiment is formed by extending the oil drain hole 61d of the cyclone block 60 in the substantially horizontal direction, the gas compressor which concerns on this invention is limited to this form. is not.

  That is, the oil drain hole 61d is formed so that the bottom edge of the opening on the oil storage part side, which is the bottom of the discharge chamber 21, is lower than the bottom edge of the opening on the internal space 63 side. Also good. According to the compressor 100 having the cyclone block 60 in which the oil drain hole 61d is formed as described above, the refrigerating machine oil R on the bottom edge of the oil drain hole 61c is also likely to flow down toward the opening on the oil storage section side. Retention of the refrigerating machine oil R in the hole 61c can also be suppressed.

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

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 an expanded sectional view which shows the cyclone block in the compressor shown in FIG.

Explanation of symbols

60 Cyclone block (oil separator)
61 Centrifugal body 61a Inlet hole 61b Inner peripheral wall surface 61c Bottom wall surface 61d Oil drain hole 61e Bottom edge 62 Hollow cylinder portion 63 Internal space 100 Compressor (gas compressor)
G Refrigerant gas R Refrigeration machine oil

Claims (3)

Inside the housing are a compressor main body for compressing gas, an inner peripheral wall surface through which the compressed gas compressed and discharged by the compressor main body is passed and centrifugally separated from the compressed gas, and the separated oil component. An oil separator having an internal space surrounded by a bottom wall surface that flows down, wherein the oil separator is provided with an oil drain hole that discharges the oil that has flowed down to the bottom wall surface to an oil storage section. ,
The gas drainage compressor is characterized in that the oil drainage hole is formed so that a bottom edge thereof is positioned lower than the bottom wall surface.   2. The gas according to claim 1, wherein the oil drainage hole is formed such that a bottom edge of the opening on the oil storage section side is positioned lower than a bottom edge of the opening on the inner space side. Compressor. The inner peripheral wall surface is a surface on which the compressed gas revolves,
The oil separator is disposed in the inner space with a centrifugal separation main body portion composed of the inner peripheral wall surface and the bottom wall surface, and is disposed substantially coaxially with the inner space, and the gas swirling the inner peripheral wall surface 3. The gas compression according to claim 1, further comprising: a substantially cylindrical hollow tube portion that leads to an outside of the centrifugal separation main body portion from an end surface side opposite to the bottom wall surface in the internal space. Machine.

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