JP2008255806A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To form an inner end face of a side block into an indented shape without machining, in a gas compressor. <P>SOLUTION: A male screw 37a is formed on an outer periphery of a boss 37 of a front side block 30, and a male screw 12c screwed with the male screw 37a of the front side block 30 is formed on a front head 12. The front side block 30 is supported by the front head 12 by fastening support with a bolt from an outer end face 39b side and screwing of a boss 37, and elastically deforms an inner end face 39a of the front side block 30 into an indented shape by proceeding screwing. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

  The present invention relates to a gas compressor, and more particularly to an improvement in lubrication of a side block of 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 compressor body is embedded in a substantially cylindrical rotor that rotates integrally with the rotating shaft, a cylinder having an approximately elliptical cross-sectional outline that surrounds the outer periphery of the rotor (columnar peripheral surface), and the rotor. A plate-like vane whose amount of protrusion from the outer peripheral surface of the rotor is variable so that the tip of the protruding side follows the substantially elliptical inner peripheral surface of the cylinder, and at least the rotor and the vane, And two side blocks each having a boss formed on the outer surface of the bearing that supports the rotating shaft protruding from the rotor on both sides.

  Then, the rotation of the rotor is performed by the mutually opposing surfaces of the two vanes 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 (the inner end surfaces facing the rotor). Accordingly, a plurality of compression chambers whose volumes are changed are defined.

  Further, the compressor main body is cantilevered by the housing by fastening the outer portion of the outer end surface of one side block in the rotational radial direction from the boss to the housing, and the outer peripheral surface of the compressor main body An elastic O-ring is interposed between the housing and the inner peripheral surface of the housing.

  The inside of the gas compressor has a suction chamber in a low-pressure atmosphere through which the gas sucked into the compressor body passes on one side of the compressor body, and the other side of the compressor body. In addition, a discharge chamber having a high-pressure atmosphere through which gas discharged from the compressor body passes is formed, and the above-described O-ring also functions to hermetically isolate the suction chamber and the discharge chamber.

In the gas compressor configured as described above, the rotor rotates together with the rotating shaft. At this time, friction occurs between the end surface of the rotor and the inner end surface of the non-rotating side block. Here, the frictional resistance between the two is reduced by the oil film of oil introduced into the compression chamber, but in order to ensure the clearance between the two and the retention of the oil film, the inner end face of the side block is connected to the rotating shaft. It has been proposed to form a concave shape with the penetrating portion as the bottom (Patent Document 1).
JP 2003-129976 A

  However, it is difficult to machine the inner end face of the side block into a concave shape with dimensional accuracy.

  This invention is made | formed in view of the said situation, and it aims at providing the gas compressor which formed the inner side end surface of the side block in the concave shape, without directly machining it.

  The gas compressor according to the present invention elastically deforms the inner end surface of the side block into a concave shape by securing the boss portion of the bearing outer surface of the side block and the housing in a state of being pulled and secures the oil film. It is a thing.

  That is, a gas compressor according to the present invention includes a substantially cylindrical rotor that rotates integrally with a rotating shaft, a cylinder having a substantially elliptical cross-sectional profile that surrounds the outer peripheral surface of the rotor, and the rotor. A plate-like vane that is embedded in the projection and has a variable protruding amount from the outer peripheral surface of the rotor such that a protruding tip follows the substantially elliptical inner peripheral surface of the cylinder, and at least the rotor And two side blocks each having a boss formed on an outer surface of a bearing that covers the rotating shaft protruding from both sides of the rotor and that supports the rotating shaft. The two vanes, the cylinder, the rotor, and the both side blocks that follow each other in the rotational direction of the cylinder define a compression chamber whose volume changes as the rotor rotates. The compressor main body and the compressor main body are housed therein, and one side block of the two side blocks is directly connected to the outer end surface of the two side blocks at the outer portion in the rotational radial direction from the boss. Or a housing that supports the compressor main body by indirectly fastening, and a male screw is formed on the outer peripheral surface of the boss of the one side block, and the housing is screwed to the male screw of the one side block. An internal thread is formed, and the side block is supported by the housing by fastening support from the outer end face side and screwing of the boss.

  According to the gas compressor according to the present invention configured as described above, the external thread formed on the outer peripheral surface of the boss of the side block and the internal thread formed on the housing are screwed together, and the outer side of the boss is out of the housing. Even after the parts abut, the side block is further elastically deformed by the boss being pulled outward of the compressor body by further screwing, so that the inner end face of the side block can be directly Without machining, it can be formed into a concave shape by elastic deformation.

  In addition, the support rigidity with respect to a housing improves by the increase in the support location of the housing with respect to a compressor main body, Thereby, the vibration displacement of the compressor main body with respect to a housing can also be reduced.

  In the gas compressor according to the present invention, the inner end face of the side block can be formed into a concave shape without being directly machined.

  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 which is an embodiment of a gas compressor according to the present invention, FIG. 2 is a side view showing a front head 12 as viewed from an arrow F in FIG. 1, and FIG. 2 is a cross-sectional view showing a cross section along line AA 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 is also supported by a compressor main body housed in a housing composed of a case 11 and a front head 12, and fastened and supported by bolts to the front head 12, and driven from an external power source (not shown) to the compressor main body. And a power transmission unit 13 for connecting and disconnecting force transmission.

  Then, bolts respectively inserted into bolt holes 12k, 12l, 12m, 12m, 12o, and 12p (see FIG. 2) formed in the front head 12 to be described later pass through the side block 30 of the compressor main body and are connected to the cylinder 40. As a result, the side block 30 is indirectly fastened to the front head 12, whereby the outer end face 39b of the front side block 30 of the compressor body and the front head 12 come into contact with each other. The head 12 is cantilevered.

  The power transmission unit 13 includes a pulley that is rotatably supported by the front head 12 via a radial ball bearing 14 and is wound around a belt that is circulated and driven by an external power source such as an engine.

  The case 11 has a substantially cylindrical shape with one end open, and the front head 12 is fastened and fixed to the case 11 so as to cover the other end of the case 11 that is open.

  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 around the axis by a driving force supplied via the power transmission unit 13, and a columnar rotor 50 that rotates integrally with the rotating shaft 51. The outer peripheral surface of the rotor 50 has an inner peripheral surface 49a having a substantially elliptical cross-sectional outline and is open at both ends, and embedded in the rotor 50 so as to protrude outward of the rotor 50. The protruding amount is variable so that the tip of the protruding side follows the inner peripheral surface 49a of the cylinder 40, and five plate-like vanes 58 arranged at equiangular intervals around the rotating shaft 51 (FIG. 3). And the front side block 30 and the rear side block 20 fixed so as to cover the open end surfaces from the outside of the open end surfaces on both sides of the cylinder 40, respectively.

  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 supported by the bearing portion 32 (bearing) of the front side block 30 and penetrates the front head 12. The penetrating portion is pivotally supported by the front head 12, and the portion extending outward is connected to the power transmission unit 13.

  Here, a boss 37 is formed on the outer peripheral surface (outer surface) of the bearing portion 32 that pivotally supports the rotating shaft 51 in the outer end surface 39 b of the side block 30, and a male screw 37 a is formed on the boss 37.

  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 connected to the rotating shaft 51 and the front shaft 12. Leakage to the outside of the front head 12 from the gap with the head 12 is prevented.

  A portion of the front head 12 corresponding to the boss 37 is formed with a female screw 12c that is screwed into the male screw 37a of the boss 37. The screwing between the male screw 37a and the female screw 12c in the boss 37, the outer end face 39b. And the O-rings 20b and 30b at the outer peripheral portions of the side blocks 20 and 30 are elastically supported by the inner peripheral surface 11b of the case 11 so that the compressor main body is held at a predetermined position in the housing. Has been.

  Similarly, the other side of the projecting portion of the rotating shaft 51 is supported by a bearing portion 22 (bearing) of the rear side block 20, whereby the rotating shaft 51 is supported with respect to the rear side block 20 and the front side block 30. And can be rotated freely.

  A boss 27 is formed on the outer peripheral surface (outer surface) of the bearing portion 22 that pivotally supports the rotating shaft 51 in the outer end surface 29 b of the side block 20, and a male screw 27 a is formed on the boss 27.

  With the compressor main body housed inside the case 11, the rear side block 20 and the case 11 form a high-pressure atmosphere discharge chamber 21 through which high-pressure refrigerant gas G is discharged from the compressor main body. The side block 30 and the front head 12 form a low-pressure atmosphere suction chamber 34 that supplies 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 is connected to the suction port 12a. Communicating with The suction chamber 34 and the discharge chamber 21 are hermetically isolated by O-rings 20b and 30b disposed on the outer peripheral surfaces of the both side blocks 20 and 30 described above.

  A cyclone block 60 (oil separator) having a metal mesh 61 for separating the refrigerating machine oil R (oil content) from the refrigerant gas G discharged from the compression chamber 48 is attached to the outer end surface 29 b of the rear side block 20. Yes.

  The cyclone block 60 is fastened by a bolt at an outer portion in the rotational radius direction from the boss 27 from the outer end surface 29 b side of the rear side block 20.

  Further, a female screw 60 a that is screwed to the male screw of the boss 27 is formed at a portion corresponding to the boss 27 of the rear side block 20, and the cyclone block 60 is screwed between the female screw 60 a and the male screw 27 a of the boss 27, and the rear side block 20. It is supported by the compressor body by fastening with bolts.

  The cyclone block 60 is disposed in the discharge chamber 21, and a short columnar axial back pressure space 66 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. 3, 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. Each vane 58 is inserted into a cylinder by centrifugal force generated by the rotation of the rotor 50 and hydraulic pressure of the refrigerating machine oil R applied to the back pressure chamber 59 defined by the bottom surface of the vane groove 56 and the vane 58. 40 is protruded toward the inner peripheral surface 49a of the cylinder 40, and the protruding tip of the vane 58 is urged to abut on the inner peripheral surface 49a of the cylinder 40. Follow the 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 11 b of the case 11. Yes.

  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 connected to the communication hole 20 a formed in the rear side block 20 and the cyclone fixed to the rear side block 20. It is discharged into the discharge chamber 21 through the wire mesh 61 of the block 60.

  On the other hand, the refrigerating machine oil R separated from the refrigerant gas G by the metal mesh 61 of the cyclone block 60 is dropped onto the bottom of the discharge chamber 21 and is stored at the bottom as described above.

  Further, the compressor 100 has a purpose of lubrication between the rotary shaft 51 and the bearing portions 22 and 32, lubrication between each end face of the rotor 50 and the inner end face of each side block 20 and 30, and the vane 58. Discharge chamber 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 66, which will be described later) so as to urge the cylinder 40 toward the inner peripheral surface 49a. 21 is provided with a structure that guides the refrigerating machine oil R stored in the lower portion of 21 to each part.

  That is, the oil passage 23 reaching the bearing portion 22 is formed in the rear side block 20, and the oil passage 23 of the bearing portion 22 is formed on the inner end surface 29 a of the rear side block 20 (the surface facing the end surface 50 a of the rotor 50). A Sarai groove 25 (intermediate pressure supply groove) which is a recess communicating 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 is formed 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 66 communicates with the salai groove 25 through the back pressure communication passage 28 without pressure loss.

  As a result, the back pressure chamber 59, the Sarai groove 25, the back pressure communication path 28, and the shaft back pressure space 66 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. 3) over a predetermined angle 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 passes through a minute gap between the bearing portion 32 and the rotary shaft 51 and is lowered to the intermediate pressure Pv, and is formed on the inner end face 39a of the front side block 30. It is guided to the saray 35 or the like which is a concave portion.

  The salai groove 35 of the front side block 30 also has a back pressure chamber 59 of the vane groove 56 exposed to the end surface 50b of the rotor 50 as the rotor 50 rotates, like the saray groove 25 of the rear side block 20. Only while passing through the Sarai groove 35 of the side block 30, it communicates with the back pressure chamber 59 of the rotor 50.

  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 projecting output of the vane 58 (intermediate pressure Pv or High pressure Pd) is applied, but a minute gap is formed between the end surfaces 50a, 50b of the rotor 50 and the inner end surfaces 29a, 39a of the side blocks 20, 30 including the angular range where the back pressure chamber 59 does not communicate. Also penetrate between the end faces 50a and 29a, between the end faces 50b and 39a, between the inner end faces 29a and 39a of the side blocks 20 and 30, and the side surfaces of the vanes 58, and between the tip of the vane 58 and the cylinder 40. It also serves to reduce the sliding frictional force at the sliding portion, such as between the inner peripheral surface 49a, cool the generated frictional heat, and wash away the wear powder generated by the friction.

  The refrigerating machine oil R that has permeated the sliding portions is mixed with 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. .

  While the discharged refrigerant gas G passes through the metal mesh 61 of the cyclone block 60, a part of the refrigerating machine oil R mixed in the refrigerant gas G is aggregated and separated from the refrigerant gas G by the metal mesh. Circulates in the air conditioning system through the discharge port 11 a of the discharge chamber 21, while the separated refrigerating machine oil R is dripped and stored in the lower part of the discharge chamber 21 and circulates mainly in the compressor 100.

  According to the compressor 100 of the present embodiment configured as described above, the male screw 37a formed on the outer peripheral surface of the boss 37 of the front side block 30 and the female screw 12c formed on the front head 12 are screwed together, and the front head From the state where each boss bottom surface 12r of the 12 bolt holes 12k to 12p is in contact with the outer end surface 39b of the front side block 30 shown in FIG. 4A, as shown in FIG. The male screw 37a of the boss 37 of the block 30 and the female screw 12c formed on the front head 12 can be screwed together.

  In the case where the screwing is advanced, an axial force acts on the boss 37 of the front side block 30 in the direction J toward the front head 12, and the front side block 30 is moved to the inner side by the action of the axial force. It elastically deforms in the direction in which the gap S between the end surface 39a and the end surface 50b of the rotor 50 widens.

  Thereby, the inner end surface 39a of the front side block 30 is formed in a concave shape without machining, and between the both end surfaces 39a and 50b, or between the side end surface of the vane 58 and the inner end surface 39a of the front side block 30. , The clearance and the retention of the oil film of the refrigerating machine oil R can be ensured.

  From the state in which each boss bottom surface 12r of the bolt holes 12k to 12p of the front head 12 is in contact with the outer end surface 39b of the front side block 30, a screw between the male screw 37a of the front side block 30 and the female screw 12c of the front head 12 is further provided. In order to be able to advance the alignment, the male screw 37a of the front side block 30 and the front head in the state where each boss bottom surface 12r of the bolt holes 12k to 12p of the front head 12 is in contact with the outer end surface 39b of the front side block 30. Needless to say, the compressor 100 according to the present embodiment has an allowance for the screwing allowance so that the screwing allowance can be further advanced with the twelve female screws 12c. is doing.

  Further, in the compressor 100 according to the present embodiment, at least a portion of the inner end surface 39a of the front side block 30 that is in sliding contact with the rotor 50 is formed into a flat surface before being screwed to the front head 12, so Machining (for example, grinding) of the inner end face 39a of the side block 30 is very simple, and the manufacturing cost can be reduced as compared with the case of forming the concave shape by machining.

  The formation of the male screw 37a on the boss 37 and the formation of the female screw 12c on the front head 12 is smaller than the cost of machining the inner end face 39a into a concave shape with high accuracy. Can be reduced.

  Further, since the number of support portions of the front head 12 with respect to the compressor body increases, the support rigidity with respect to the housing (in FIG. 4, the rigidity with respect to bending in the direction orthogonal to the rotation shaft 51, etc.) is improved. The vibration displacement of the machine body can be reduced.

  Furthermore, according to the compressor 100 of the present embodiment, the male screw 27a formed on the outer peripheral surface of the boss 27 of the rear side block 20 and the female screw 60a formed on the cyclone block 60 are screwed together, and the bottom surface 60b of the cyclone block 60 is formed. From the state of contact with the outer end surface 29b of the rear side block 00 shown in FIG. 5A, the male screw 27a of the boss 27 of the rear side block 20 and the cyclone block 60 are further formed as shown in FIG. 5B. The screwing with the female screw 60a can be advanced.

  In the case where the screwing is advanced, an axial force acts on the boss 27 of the rear side block 20 in a direction J ′ toward the cyclone block 60, and the rear side block 20 has its inner end face by the action of this axial force. It is elastically deformed in the direction in which the gap S ′ between 29a and the end face 50a of the rotor 50 is widened.

  Thus, the inner end surface 29a of the rear side block 20 is formed into a concave shape without machining, and the clearance between the both end surfaces 29a and 50a, or between the side end surface of the vane 58 and the inner end surface 29a of the rear side block 20 is determined. And the retention of the oil film of the refrigerator oil R can be ensured.

  In order to further advance the screwing of the male screw 27a of the rear side block 20 and the female screw 60a of the cyclone block 60 from the state in which the bottom surface 60b of the cyclone block 60 is in contact with the outer end surface 29b of the rear side block 20, In a state where the bottom surface 60b of the cyclone block 60 is in contact with the outer end surface 29b of the rear side block 20, there is a margin of screwing allowance that can further advance the screwing of the male screw 27a of the rear side block 20 and the female screw 60a of the cyclone block 60. Needless to say, the compressor 100 according to the present embodiment has a margin for the screwing allowance. Even if the margin of the screwing allowance between the male screw 27a and the female screw 60a is zero (a state where the screwing allowance is completely used up), the male screw 27a is provided so as to secure the shaft back pressure space 66. Alternatively, the thread cutting range of the female screw 60a is set.

  Further, in the compressor 100 according to the present embodiment, at least a portion of the inner end surface 29a of the rear side block 20 that is in sliding contact with the rotor 50 is formed into a flat surface before being screwed to the cyclone block 60. Therefore, the rear side block The machining (for example, grinding) of the inner end face 29a of the 20 is very simple, and the manufacturing cost can be reduced as compared with the case of forming the concave shape by machining.

  The formation of the male screw 27a on the boss 27 and the formation of the female screw 60a on the cyclone block 60 is smaller than the cost of machining the inner end face 29a into a concave shape with high accuracy, and therefore the manufacturing cost of the compressor 100 as a whole is small. Can be reduced.

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 a side view which shows the front head by the arrow F in FIG. It is sectional drawing which shows the cross section along the AA in FIG. It is sectional drawing which expanded the screwing part of a front side block and a front head typically. It is sectional drawing which expanded the screwing part of a rear side block and a cyclone block typically.

Explanation of symbols

12 Front head (part of housing)
12c Female thread 30 Front side block (side block)
37 Boss 37a Male thread 39a Inner end face 39b Outer end face 40 Cylinder 50 Rotor 51 Rotating shaft 100 Compressor (Gas compressor)

Claims (3)

A substantially cylindrical rotor that rotates integrally with the rotation shaft, a cylinder that surrounds the outer peripheral surface of the rotor, a cylinder having a substantially elliptical cross-sectional outline, and embedded in the rotor, the tip on the protruding side is the A plate-like vane whose amount of protrusion from the outer peripheral surface of the rotor is variable so as to follow the substantially elliptical inner peripheral surface of the cylinder, at least the rotor and the vane, And two side blocks each having a boss formed on an outer surface of a bearing that supports the rotating shaft that protrudes from the rotor on both sides, and the two vanes follow each other in the rotational direction of the rotor. A compressor body in which a compression chamber whose volume changes with the rotation of the rotor is defined by the cylinder, the rotor, and the both side blocks;
The compressor main body is housed therein, and one side block of the two side blocks is fastened from the outer end face side at an outer portion in the rotational radial direction from the boss, and the compressor A housing for supporting the main body,
A male screw is formed on the outer peripheral surface of the boss of the one side block,
The housing is formed with a female screw that is screwed into the male screw of the one side block,
The gas compressor according to claim 1, wherein the side block is supported by the housing by fastening support from the outer end face side and screwing of the boss. An oil separator that separates oil from the gas discharged from the compression chamber;
The oil separator is fastened from the side of the outer end surface of the other side block of the two side blocks to the outer portion in the rotational radius direction of the boss,
A male screw is formed on the outer peripheral surface of the boss of the other side block,
The oil separator is formed with a female screw that is screwed into the male screw of the other side block,
The gas compressor according to claim 1, wherein the oil separator is supported by fastening to the side block and screwing to the boss.   2. The inner end face of the side block on the side facing the rotor, at least a portion in sliding contact with the rotor is formed in a plane before being screwed into the housing. 2. The gas compressor according to 2.

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