JP2008057389A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To keep oil separation efficiency high at high speed and low at high speed in a gas compressor. <P>SOLUTION: A cyclone block 60 (oil separator) having hollow cylinder parts 62, 66 in roughly cylindrical spaces 63, 67 (turning spaces) surrounded by inner circumference wall surfaces 61a, 65a and bottom wall surfaces 61e, 65e (bottom surfaces), and centrifugally separating refrigerant oil R (oil component) contained in refrigerant gas G (gas), includes two oil separating parts 64, 68 connected in series, and is established to make refrigerant gas G pass through only first oil separation part 64 when flow speed of refrigerant gas G flowing into the cyclone block 60 is relatively high and to make refrigerant gas G pass through both of the oil separating parts 64, 68 in order when flow speed of refrigerant gas G is relatively low. <P>COPYRIGHT: (C)2008,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.

In this oil separator, the gas discharged from the compressor body is lowered while swirling along a predetermined inner peripheral wall surface, whereby the oil is centrifuged and discharged from the bottom, and the oil is separated. The latter gas is exhausted upward from the hollow cylinder (Patent Document 1).
Japanese Patent Laid-Open No. 2003-090286

  By the way, for example, in a vehicle-mounted gas compressor for an air conditioner, since the engine of the vehicle is used as a driving force, the rotational speed of the gas compressor depends on the rotational speed of the engine.

  However, even when the engine is rotating at a low speed, it is necessary to maintain the cooling performance to some extent. This is highly demanded to improve the oil separation efficiency when the gas compressor is rotating at a low speed.

  On the other hand, during high-speed rotation where the cooling performance tends to be excessive, it is effective to cool the compressor body with the oil circulating in the air conditioning system. To that end, it is necessary to secure a certain amount of oil circulating in the air conditioning system. Therefore, it is required to reduce the oil separation efficiency in the gas compressor.

  In contrast, an actual centrifugal oil separator separates oil using the flow rate of the compressed gas discharged from the compressor body, so the oil separation efficiency is low at low speeds and high speeds. It exhibits a characteristic opposite to the required oil separation characteristic described above.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to provide a gas compressor that can increase the oil separation efficiency at a low speed and reduce the oil separation efficiency at a high speed.

  The gas compressor according to the present invention reduces the oil separation efficiency at high speed by passing the compressed gas through only a single oil separation section at high speed and sequentially passing two oil separation sections in series at low speed. In addition, the oil separation performance at low speed is improved.

  That is, the gas compressor according to the present invention includes a hollow cylinder portion extending substantially coaxially with the inner peripheral wall surface in a revolving space surrounded by a compressor main body, an inner peripheral wall surface and a bottom surface inside the housing. The compressed gas is swirled while descending along the inner peripheral wall surface, whereby the oil contained in the compressed gas is centrifuged, and the lowered compressed gas passes through the hollow cylindrical portion. The oil separator has two oil separators connected in series, and when the flow velocity of the compressed gas flowing into the oil separator is relatively high, When the compressed gas passes through only one of the two oil separators and the flow rate of the compressed gas flowing into the oil separator is relatively slow, the compressed gas is the two oil separators. Must be set to pass sequentially through the separator And features.

  According to the gas compressor according to the present invention configured as described above, when the flow velocity of the compressed gas flowing into the oil separator is relatively high, the compressed gas is one of the two oil separation units. The oil separation efficiency at high speed can be lowered because only the gas passes through the oil separator. On the other hand, when the flow velocity of the compressed gas flowing into the oil separator is relatively slow, the compressed gas sequentially passes through the two oil separators. Therefore, the oil separation efficiency at low speed can be increased.

  In the gas compressor according to the present invention, the two oil separation units may have substantially the same configuration or different configurations.

  As a different configuration, for example, the length of the hollow cylindrical portion may be different. Here, the thing with a long length of a hollow cylinder part can make oil separation efficiency higher than a short thing.

  The gas compressor according to the present invention can reduce the oil separation efficiency at high speed and can increase the oil separation efficiency at low speed.

  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 a cross section taken along line BB in the compressor 100 shown in FIG. 1, and FIG. 4 is a diagram showing a hollow cylinder portion 62 of the centrifugal cyclone block 60 shown in FIG. It is sectional drawing which extracted 66. 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. 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 the side blocks 20, 30 is an inner periphery of the case 11 and the front head 12 by an O-ring. By being held by the surface, the compressor main 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 has a substantially cylindrical space 63 (a swirl space) surrounded by an inner peripheral wall surface 61a that swirls the high-pressure refrigerant gas G discharged from the discharge chamber 45 and a bottom wall surface 61e (bottom surface) continuous with the inner peripheral wall surface 61a. ), And the refrigerant gas G is swung while descending along the inner peripheral wall surface 61a, whereby the centrifugal separation main body 61 that centrifuges the refrigerating machine oil R contained in the refrigerant gas G, and the substantially cylindrical space 63 A hollow cylindrical hollow tube that extends substantially coaxially with the inner peripheral wall surface 61a and guides the swung refrigerant gas G from the end surface (upper surface in FIG. 1) opposite to the bottom wall surface 61e to the outside of the centrifugal separation body 61. As shown in FIG. 3, a first oil separation part 64 having a part 62 and a second oil separation part 68 having the same configuration as the first oil separation part 64 are arranged in series in the depth direction of the paper surface of FIG. 1. It is connected.

  That is, the first oil separation part 64 includes a centrifugal separation body part 61 and a hollow cylinder part 62, and the second oil separation part 68 is also continuous with the inner peripheral wall surface 65a for turning the refrigerant gas G and the inner peripheral wall surface 65a. The refrigerant gas G is contained in the refrigerant gas G by swirling while descending along the inner peripheral wall surface 65a. The centrifugal main body 65 that centrifuges the refrigerating machine oil R, and the end surface on the opposite side of the bottom wall surface 65e of the swirling refrigerant gas G extending substantially coaxially with the inner peripheral wall surface 65a in the substantially cylindrical space 67 (in FIG. 1) A hollow cylindrical portion 66 that is guided from the upper surface side to the outside of the centrifugal separation main body portion 65.

  In the compressor 100 of the present embodiment, the two centrifugal separation body portions 61 and 65 are integrally configured, and the two oil separation portions 64 and 68 are integrated, but this is limited to this embodiment. Instead, both oil separation parts 64 and 68 may be separate.

  In addition, on the same surface as the bottom wall surfaces 61e and 65e of the oil separation portions 64 and 68, the refrigeration machine oil R that has been centrifuged and flown down to the bottom wall surfaces 61e and 65e is formed on the peripheral wall where the inner peripheral wall surfaces 61a and 65a are formed. Are formed at the bottom of the discharge chamber 21.

  On the other hand, the compressed refrigerant gas G after the refrigerating machine oil R is separated rises from the bottom wall surfaces 61e and 65e through the central portions of the substantially cylindrical spaces 63 and 67 and the interiors 62a and 66a of the hollow cylindrical portions 62 and 66. Then, the air is exhausted from the upper end openings 62c and 66c of the hollow cylindrical portions 62 and 66, and is supplied to the outside of the compressor 100 through the discharge chamber 21 and the discharge port 11a.

  Here, a valve 69 whose opening degree increases as the flow rate of the refrigerant gas G passing through the interior 62a of the hollow cylinder portion 62 increases is provided at the upper end opening 62c of the hollow cylinder portion 62 of the first oil separation portion 64. It has been.

  The valve 69 has the same configuration as, for example, a discharge valve disposed in the discharge chamber 65, and the plate spring-like reed valve 69a (plate spring of a plate-like elastic body) and excessive elastic deformation of the reed valve 69a. The reed valve 69a and the valve support 69b are fixed to the centrifugal separation main body 61 together with the hollow cylinder 62 by a screw 69c.

  As the valve 69, another type of elastic member or the like can be applied instead of the above-described leaf spring-shaped reed valve 69a.

  Further, the valve 69 in the compressor 100 of the present embodiment is an analog valve having a correspondence relationship in which the flow rate of the refrigerant gas G and the opening degree of the valve 69 continuously change, but the flow rate of the refrigerant gas G is A digital one having a discrete correspondence relationship in which the opening degree is zero (closed) until a predetermined threshold value set in advance is exceeded, and when the threshold value is exceeded, the opening degree is not zero (open). It may be.

  A portion of the hollow cylinder portion 62 on the upstream side of the valve 69 communicates the interior 62 a of the hollow cylinder portion 62 of the first oil separation portion 64 and the substantially cylindrical space 67 of the second oil separation portion 68. A hole 62b that continues to the communication hole 61d is formed.

  Thereby, when the opening degree of the reed valve 69a is large, the refrigerant gas G introduced into the first oil separation part 64 is discharged to the outside from the hollow cylinder part 62 after the refrigerating machine oil R is separated, and the second oil separation part The refrigeration oil R is substantially separated only by the first oil separation unit 64.

  On the other hand, when the opening degree of the reed valve 69a is zero or when the opening degree is small, the refrigerant gas G introduced into the first oil separation part 64 is separated from the refrigerating machine oil R and then is released from the hollow cylinder part 62 to the outside. The refrigerant gas G is introduced into the second oil separation portion 68 from the opening 65b facing the substantially cylindrical space 67 through the hole 62b and the communication hole 61d formed in the hollow cylindrical portion 62, and the refrigerant gas G The refrigeration machine oil R is separated by the two oil separation parts 64 and 66 after passing through the separation parts 64 and 68.

  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 50 b) 39 is guided to the salai groove 35, which is a recess formed in the recess 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 25 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 flow rate of the high-pressure refrigerant gas G introduced into the substantially cylindrical space 63 of the first oil separator 64 from the introduction hole 61a of the cyclone block 60 is high. When the rotational speed is relatively high, that is, when the rotational speed of the compressor body is high (when the rotational speed per unit time is large), since the opening degree of the reed valve 69a is large, the refrigerant introduced into the first oil separation unit 64 After separation of the refrigerating machine oil R, the gas G is discharged to the outside from the hollow cylindrical part 62 and hardly flows into the second oil separating part 68. In practice, the refrigerating machine oil R is separated only by the first oil separating part 64. Is called.

  On the other hand, when the flow rate of the high-pressure refrigerant gas G introduced into the substantially cylindrical space 63 of the first oil separation portion 64 from the introduction hole 61a is relatively small, that is, when the rotational speed of the compressor body is low (unit time) When the number of revolutions is small), since the opening degree of the reed valve 69a is zero or the opening degree is small, the refrigerant gas G introduced into the first oil separation unit 64 is separated from the refrigerating machine oil R, It becomes difficult to be discharged from the hollow cylindrical portion 62 to the outside, and is introduced into the second oil separation portion 68 from the opening 65b facing the substantially cylindrical space 67 through the hole 62b and the communication hole 61d formed in the hollow cylindrical portion 62. The refrigerant gas G passes through the two oil separators 64 and 68, and the two oil separators 64 and 66 separate the refrigerating machine oil R, respectively.

  And when passing only the 1st oil separation part 64 and performing separation of refrigerating machine oil R only by this 1st oil separation part 64, it passes through two oil separation parts 64 and 68 one by one, and both oils The separation efficiency of the refrigerating machine oil R from the refrigerant gas G is lower than that in the case where the refrigerating machine oil R is separated by the separation units 64 and 68, while the two oil separation units 64 and 68 are sequentially passed through to separate both oils. When the refrigerating machine oil R is separated by the parts 64 and 68, the refrigerant gas G is passed more than when the refrigerating machine oil R is separated only by the first oil separating part 64 through the first oil separating part 64. Separation efficiency of refrigeration oil R from is high.

  Therefore, when the rotation speed of the compressor body is low, the separation efficiency of the refrigerating machine oil R from the refrigerant gas G can be increased. As a result, in particular, in the case where the engine of the vehicle is used as the power source of the rotational driving force transmitted to the transmission mechanism 13, the oil separation efficiency is improved even when the engine rotates at a low speed. Can be improved.

  Further, when the rotation speed of the compressor body is high, the separation efficiency of the refrigerating machine oil R from the refrigerant gas G can be lowered. As a result, prevention of excessive outflow of the refrigerating machine oil R to the air conditioning system at the time of high-speed rotation, where the cooling performance is likely to be excessive, is mitigated, and the cooling action of the compressor main body by the refrigerating machine oil R returned to the compressor body from the air conditioning system The volume efficiency of the compressor 100 can be improved by being promoted.

  Whether the rotational speed is high or low may be determined based on, for example, about 4000 rpm, and is high when the rotational speed is higher than about 4000 rpm, and low when the rotational speed is lower than about 4000 rpm. , Can be determined.

  Further, in the compressor 100 of the present embodiment, since the opening degree of the valve 69 continuously changes according to the flow rate of the refrigerant gas G, when the operation of the compressor body is in the range from low speed to high speed. The refrigerant gas G passes through both the oil separation parts 64 and 68, but as the rotational speed approaches higher, the opening of the valve 69 increases and the amount of the refrigerant gas G flowing into the second oil separation part 68 The oil separation efficiency decreases and the oil separation efficiency decreases. On the other hand, as the rotational speed approaches a lower speed, the opening degree of the valve 69 decreases, and the amount of the refrigerant gas G that circulates into the second oil separation unit 68 increases. Separation efficiency is improved.

  Note that, as described above, in a gas compressor to which the valve 69 has an opening degree that varies discretely according to the flow rate of the refrigerant gas G, the rotational speed of the compressor body exceeds approximately 4000 rpm, for example. In this case, the opening degree of the valve 69 becomes 100%, and the opening degree of the valve 69 can be set to 0% when the rotational speed of the compressor main body is less than about 4000 rpm.

  In the compressor 100 of the present embodiment, the hollow cylinder part 66 (length L66) of the second oil separation part 68 is formed longer than the hollow cylinder part 62 (length L62) of the first oil separation part 64 ( L66> L62), the lengths of both hollow cylindrical portions 62, 66 may be the same (L62 = L66), and the hollow cylindrical portion 62 of the first oil separating portion 64 is the same as that of the second oil separating portion 68. It may be formed longer than the hollow cylindrical portion 66 (L62> L66).

  As the length of the hollow cylindrical portions 62 and 66 increases, the physical length of the process in which the centrifugal separation action is performed increases. Therefore, the longer the length of the hollow cylindrical portions 62 and 66, the higher the oil separation efficiency. However, as in this embodiment, by forming the hollow cylinder part 66 of the second oil separation part 68 longer than the hollow cylinder part 62 of the first oil separation part 64, the oil separation efficiency at low speed can be achieved. The effect of the present invention, that is, the improvement of the above and the suppression of the oil separation efficiency at high speed, can be made more remarkable.

  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 sectional drawing by the surface along the BB line in FIG. It is sectional drawing which extracted the hollow cylinder part of the cyclone block of the centrifugal separation system shown in FIG.

Explanation of symbols

60 Cyclone block (oil separator)
61, 65 Centrifugal body 61a, 65a Inner peripheral wall surface 61c, 65c Oil drain hole 61e, 65e Bottom wall surface (bottom surface)
62, 66 Hollow cylinder part 63, 67 Substantially cylindrical space (swirl space)
64 1st oil separation part 68 2nd oil separation part 69 Valve 69a Reed valve 100 Compressor (gas compressor)
G Refrigerant gas R Refrigeration machine oil

Claims (6)

The housing has a compressor main body for compressing gas, and a hollow cylindrical portion extending substantially coaxially with the inner peripheral wall surface in a swirling space surrounded by the inner peripheral wall surface and the bottom surface. In the gas compressor comprising: an oil separator that centrifuges the oil content contained in the compressed gas by descending along the wall surface, and the compressed gas after the descent passes through the hollow cylindrical portion.
The oil separator has two oil separators connected in series, and when the flow velocity of the compressed gas flowing into the oil separator is relatively high, the compressed gas flows into the two oil separators. When the flow rate of the compressed gas that passes through only one of the oil separators and flows into the oil separator is relatively slow, the compressed gas is set so as to sequentially pass through the two oil separators. A gas compressor characterized by having   The oil separation part has the swirl space and the hollow cylinder part, respectively, and the hollow cylinder part of one oil separation part communicates with the swirl space of the other oil separation part, and the one oil A valve whose opening degree increases as the flow rate of the compressed gas passing through the hollow cylinder portion increases downstream from the portion communicating with the other swirling space of the hollow cylinder portion of the separation portion. The gas compressor according to claim 1.   The gas compressor according to claim 1 or 2, wherein the hollow cylinder part of the other oil separation part is longer than the hollow cylinder part of the one oil separation part.   The gas compressor according to any one of claims 1 to 3, wherein the valve is a leaf spring of a plate-like elastic body.   The gas compressor according to claim 4, wherein the valve has a valve support that prevents excessive deformation of the leaf spring.   The gas compressor according to any one of claims 1 to 5, wherein an in-vehicle engine is used as a power source of driving force for rotationally driving the compressor main body.

Images