JP2008169811A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To enhance followability of a vane tip end to an inner circumference surface of a cylinder in a gas compressor. <P>SOLUTION: For a back pressure chamber 59 of a vane groove 56 corresponding to a vane 58 when a tip end at a protruding side of the vane 58 passes at a short diameter position of an inner circumference face 49a in a substantially elliptical shape of the cylinder, a high pressure hole 27 for supplying an energizing force pd (>Ps) higher than a pressure (approximately Ps) in a compression chamber 48 in an intake stroke is formed in an end face 26 in a side block 20. When the tip end of the protruding side of the vane 58 passes the short diameter position of the substantially elliptical shape of the inner circumference face 49a of the cylinder, the vane 58 is appropriately protruded (following) so that the tip end of the protruding side of the vane 58 continues to abut on the inner circumference face 49a following the substantially elliptical shape of the inner circumference face of the cylinder 49a. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to a gas compressor, and in particular, to an improvement in back pressure (biasing force) supplied to a vane.

  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 the rotor and vanes are connected to both end surface sides of the rotor It is the structure provided with two side blocks which cover from.

  Then, a plurality of surfaces whose two vanes are opposite to 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 have a plurality of volumes whose volume changes as the rotor rotates. A compression chamber is 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. A discharge chamber having a high-pressure atmosphere through which gas discharged from the compressor body passes is formed on the other side of the body.

  Here, in the side block that defines the discharge chamber, a discharge path for guiding the high-pressure gas compressed in the compression chamber to the discharge chamber is formed, and refrigerating machine oil or the like mixed with the discharged gas is formed. A cyclone block for separating the lubricating oil is attached, and while the high-pressure gas led from the discharge path to the cyclone block passes through the cyclone block, the refrigerating machine oil mixed in this gas is separated, The gas is discharged into the discharge chamber, while the separated refrigeration oil is dropped and stored in the lower portion of the discharge chamber.

  An oil path extending from the bottom of the discharge chamber to the bearing that supports the rotating shaft is formed inside the side block, and the refrigerating machine oil stored in the lower portion of the discharge chamber is compressed into the discharge chamber. Under the high pressure of the gas, it flows into the oil passage from the opening at the bottom and reaches the bearing at the outlet.

  The refrigerating machine oil that has reached the bearing portion passes through a minute gap between the rotating shaft and the bearing portion, and reaches the end surface of the side block that faces the end surface of the rotor.

  At this time, since the minute gap between the rotating shaft and the bearing portion acts as a throttle on the refrigeration machine oil that is a fluid, it receives pressure loss due to the throttle from the high pressure state in the oil passage, and at the end face of the side block. Is an intermediate pressure lower than the pressure (high pressure) in the discharge chamber and higher than the pressure (low pressure) in the suction chamber.

  A substantially fan-shaped recess (Saray groove; intermediate pressure supply groove) is formed over a predetermined angle range around the center of the bearing portion of the above-described end face of the side block facing the rotor end face. The refrigerating machine oil that reaches the end face of the side block after being reduced to the intermediate pressure by passing through the gap flows into the Saray groove and fills the Saray groove.

  On the other hand, since the vane groove (vane embedded space) penetrates to both end faces of the rotor, the vane groove exposed on the end face of the rotor passes through the Sarai groove of the side block as the rotor rotates. During this time, the vane groove and the Sarai groove communicate with each other, and intermediate pressure refrigerating machine oil is supplied to the vane groove. The vane receives the intermediate pressure of the supplied refrigerating machine oil and moves toward the inner peripheral surface of the cylinder. Protruding.

In addition, the space part which the vane does not occupy among the space of the vane groove and the space part of the Sarai groove are back pressure spaces on which an intermediate pressure for projecting the vane acts (Patent Document 1).
JP 2005-273550 A

  By the way, the amount of protrusion of the vane becomes the smallest when the tip of the vane on the protruding side passes through the substantially elliptical minor axis position of the inner peripheral surface of the cylinder, and needs to increase after passing through this minor axis position. .

  Here, the vane protruding side regardless of whether the vane protruding side tip approaches the minor diameter position or the vane protruding side tip moves away from the minor diameter position as the rotor rotates. The amount of protrusion at the tip is physically determined by the back pressure acting on the embedded end of the vane (the pressure of refrigeration oil acting on the back pressure space) and the pressure from the cylinder inner peripheral surface acting on the tip of the vane on the protruding side. Follows the balance with the pressure, but the followability of the vane when the rotor rotates fast or when the rotor starts rotating is appropriate in the stroke where the tip of the vane protrudes closer to the short diameter position. It may not always be appropriate in the process of moving the tip away from the minor axis position.

  That is, in the process in which the tip of the vane protruding side moves away from the short diameter position, the amount of protrusion of the vane increases, so that the volume of the back pressure space increases, and thereby the refrigerating machine oil acting on the back pressure space. Pressure cannot follow this increase in volume, and the protruding end of the vane may be separated from the inner peripheral surface of the cylinder, making it impossible to maintain the airtightness of the compression chamber.

  Also, if the tip of the vane on the protruding side is momentarily separated from the inner peripheral surface of the cylinder, when it comes into contact with the inner peripheral surface of this cylinder again, it acts as an impact force on the tip of the vane, and noise is generated. Or damage to the vane tip.

  This invention is made | formed in view of the said situation, and it aims at providing the gas compressor which can improve the followable | trackability of the vane front-end | tip with respect to the internal peripheral surface of a cylinder.

  In the gas compressor according to the present invention, when the vane passes through the minor axis position of the cylinder whose inner peripheral surface is substantially elliptical, a biasing force higher than the pressure in the compression chamber acts as the vane back pressure against the vane. By doing so, the thrust output of the vane is improved, and the followability to the inner peripheral surface of the cylinder is improved.

  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 that cover the vanes from both end face sides of the rotor, and the two vanes, the cylinder, the rotor, and the both side blocks that follow each other in the rotational direction of the rotor, A compression chamber whose volume changes with rotation is defined, and the tip of the protruding side of the vane passes through the substantially elliptical minor axis position of the cylinder. And a high-pressure hole that projects toward the inner peripheral surface of the cylinder and supplies a biasing force higher than the pressure in the compression chamber in the suction stroke is formed in the end surface of the side block. To do.

  Here, the high-pressure hole is specifically, for example, in the back pressure space of the vane groove (vane embedding space) of the vane when the tip of the vane protruding side passes through the substantially elliptical short axis position of the cylinder. What is necessary is just to be formed in the position of a corresponding side block.

  In a vane rotary type gas compressor, the range where the tip of the vane on the protruding side extends from the short axis position of the cylinder to the long diameter position is generally a suction stroke for sucking the gas to be compressed into the compression chamber. The pressure in the compression chamber is as low as atmospheric pressure.

  Therefore, it is sufficient that the urging force by the newly formed high-pressure hole is a pressure exceeding the pressure in the compression chamber, that is, the atmospheric pressure.

  According to the gas compressor according to the present invention configured as described above, when the tip of the vane on the protruding side passes through the substantially elliptical minor axis position of the cylinder, the vane is disposed on the inner periphery of the cylinder with respect to the vane. Because the biasing force higher than the pressure in the compression chamber during the suction stroke is supplied from the high-pressure hole formed in the end surface of the side block, the tip of the vane on the protruding side has a substantially elliptical shape. When passing through the minor axis position, it is possible to prevent the follow-up delay of the vane from occurring and improve the follow-up performance.

  With the gas compressor according to the present invention, the followability of the vane tip with respect to the inner peripheral surface of the cylinder can be improved.

  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, and FIG. 2 is a view showing a cross section taken 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.

  Further, the compressor 100 is attached to the front body 12 and a compressor main body housed in a housing composed of the case 11 and the front head 12, and transmits driving force from an external power source (not shown) to the compressor main body. And an electromagnetic clutch 13 for connecting and disconnecting. The compressor body is fixed to the front head 12 by a plurality of bolts.

  The electromagnetic clutch 13 is rotatably supported by the front head 12 via a radial ball bearing 14, has an annular space inside, and is circularly driven by an external power source such as an engine on a circular outer peripheral surface. A pulley around which a belt or the like is wound, an annular electromagnetic coil that is fixedly supported by the front head 12 and accommodated in the annular space of the pulley and generates a magnetic attractive force by energization, and a compressor main body to be described later An armature that is fixed to the rotating shaft 51 and that is arranged in a disc-like manner so as to face the end face of the pulley with a predetermined gap, and is attracted to the end face of the pulley by the magnetic attractive force generated by the electromagnetic coil. The connection / disconnection between the armature and the end face of the pulley is switched according to the magnetic attractive force generated by energizing the electromagnetic coil.

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

  The compressor main body accommodated in the housing includes a rotating shaft 51 that rotates about the axis by a driving force supplied via the armature of the electromagnetic clutch 13, and a columnar rotor 50 that rotates integrally with the rotating shaft 51. And an inner peripheral surface 49a having a substantially elliptical cross-sectional outline surrounding the outer peripheral surface of the rotor 50, and embedded in the rotor 50 so as to protrude toward the outer side of the rotor 50, and a cylinder 40 open at both ends. 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 equal angular intervals around the rotation shaft 51, and the cylinder The front side block 30 and the rear side block 20 are fixed so as to cover the open end faces from the outside of the open end faces of the both sides 40.

  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 armature of the electromagnetic clutch 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 the state where the compressor main body is accommodated in the case 11, the rear side block 20 and the case 11 form a high-pressure atmosphere discharge chamber 21 from which high-pressure refrigerant gas G is discharged from the compressor main body. 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 sucks. It communicates with the port 12a. The suction chamber 34 and the discharge chamber 21 are hermetically isolated by the above-described O-ring or the like.

  Further, a cyclone block 60 for separating the refrigerating machine oil R from the refrigerant gas G is attached to the rear side block 20, and the cyclone block 60 is disposed in the discharge chamber 21, and the rear side block 20 and the cyclone block are arranged. A short columnar axial back pressure space 66 is formed between 60 and 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. 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 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 connected to the communication hole 20 a formed in the rear side block 20 and the cyclone fixed to the rear side block 20. The oil is discharged into the discharge chamber 21 through the oil separator 60a of the block 60.

  On the other hand, the refrigerating machine oil R separated from the refrigerant gas G by the cyclone block 60 and the oil separator 60a 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. The discharge chamber is used for the purpose of supplying hydraulic pressure (back pressure) to the back pressure space (back pressure chamber 59, salai groove 25 and shaft back pressure space 68, which will be described later) to urge the cylinder 40 toward the inner peripheral surface 49a of the cylinder 40. 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, an oil passage 23 reaching the bearing portion 22 is formed in the rear side block 20, and the inner end surface 26 (surface facing the end surface 50 a of the rotor 50) of the rear side block 20 is formed on the oil passage 23 in the bearing portion 22. 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 shaft back pressure space 68, and the shaft back pressure space 68 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. 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 36 of the front side block 30. It is guided to the Sarai groove 35, which is a concave portion.

  The salai groove 35 of the front side block 30 also 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.

  On the other hand, the end surface 26 of the rear side block 20 and the end surface 36 of the front side block 30 respectively correspond to the end of the protruding side of the vane 58 when passing through the minor axis position of the substantially elliptical inner peripheral surface 49a of the cylinder 40. High-pressure holes 27 and 37 for supplying an urging force Pd higher than the pressure in the compression chamber 48 in the suction stroke, which protrudes toward the inner peripheral surface 49 a of the cylinder 40, are formed on the vane 58.

  Specifically, as the rotor 50 rotates, the back pressure chamber 59 of the vane groove 56 exposed on the end surface 50 a of the rotor 50 passes through the high pressure hole 27 of the rear side block 20 and the high pressure hole 37 of the front side block 30. The back pressure space 59 of the vane groove 56 and the high-pressure holes 27 and 37 are only during the operation (while the tip of the protruding side of the vane 58 passes the short diameter position of the substantially elliptical inner peripheral surface 49a of the cylinder 40). , The high pressure Pd refrigerating machine oil R of the high pressure holes 27 and 37 is supplied to the back pressure space 59 of the vane groove 56, and the vane 58 corresponding to the vane groove 56 has a high pressure of the supplied refrigerating machine oil R. Receiving Pd, it protrudes toward the inner peripheral surface 49a of the cylinder 40.

  Since the high-pressure hole 27 communicates with the oil passage 23 without passing through a minute gap (throttle) between the bearing portion 22 and the peripheral surface portion of the rotating shaft 51, the intermediate pressure supplied to the salai groove 25. The refrigerating machine oil R having a pressure Pd higher than Pv can be supplied to the back pressure chamber 59 of the vane groove 56 of the rotor 50, and the thrust output of the vane 58 toward the inner peripheral surface 49a of the cylinder 40 can be increased. .

  Similarly, the high-pressure hole 37 communicates with the oil passage 33 without passing through a minute gap (throttle) between the bearing portion 32 and the peripheral surface portion of the rotating shaft 51, and is thus supplied to the Saray groove 35. The refrigerating machine oil R having a pressure Pd higher than the intermediate pressure Pv can be supplied to the back pressure chamber 59 of the vane groove 56 of the rotor 50, and the projecting output of the vane 58 toward the inner peripheral surface 49a of the cylinder 40 is increased. be able to.

  Here, the high-pressure holes 27 and 37 and the Sarai grooves 25 and 35 are arranged so as not to communicate with each other via the back pressure chamber 59 of the vane groove 56. That is, the high-pressure holes 27 and 37 communicate with the back pressure space 59 of the vane groove 56 only while the tip of the vane 58 on the protruding side passes through the short-diameter position on the substantially elliptical inner peripheral surface 49 a of the cylinder 40. The back pressure space 59 of the vane groove 56 does not communicate with the salai grooves 25 and 35 during the period in which the high pressure holes 27 and 37 and the back pressure space 59 of the vane groove 56 communicate with each other. The rotation of the rotor 50 advances, the tip of the vane 58 on the protruding side passes through the short-diameter position of the substantially elliptical inner peripheral surface 49a of the cylinder 40, and the back pressure space 59 of the vane groove 56 becomes the high-pressure hole 27. , 37, the back pressure space 59 of the vane groove 56 communicates with the Sarai grooves 25, 35.

  As a result, the pressure (high pressure Pd) of the refrigerating machine oil R supplied to the high-pressure holes 27 and 37 is reduced by the merging of the refrigerating machine oil R having the intermediate pressure Pv supplied to the salai grooves 25 and 35. On the other hand, the pressure (intermediate pressure Pv) of the refrigerating machine oil R supplied to the Sarai grooves 25 and 35 is increased by the merge of the high-pressure Pd refrigerating machine oil R supplied to the high-pressure holes 27 and 37. Is preventing.

  When the back pressure chamber 59 of the vane groove 56 of the rotor 50 communicates with the refrigerating machine oil R supplied to the Sarai grooves 25 and 35 and the high pressure holes 27 and 37, the vane 58 protrudes from the back pressure chamber 59. Force (intermediate pressure Pv or high pressure Pd) is applied, but between the end faces 50a, 50b of the rotor 50 and the end faces 26, 36 of the side blocks 20, 30 including the angular range where the back pressure chamber 59 does not communicate. Or the like, and between the end surfaces 50a and 26, between the end surfaces 50b and 36, between the end surfaces 26 and 36 of the side blocks 20 and 30, and the side surface of the vane 58, and the tip of the vane 58, The sliding frictional force in the sliding part such as between the inner peripheral surface 49a of the cylinder 40 is reduced, the generated frictional heat is cooled, and the wear powder generated by the friction is washed away.

  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 refrigerant gas G passes through the cyclone block 60, a part of the refrigerating machine oil R mixed in the refrigerant gas G is separated from the refrigerant gas G, and the refrigerant gas G is discharged into the discharge chamber 21, and the air conditioning system. On the other hand, the separated refrigerating machine oil R is dropped 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, when the tip of the protruding side of the vane 58 passes the short diameter position of the substantially elliptical inner peripheral surface 49a of the cylinder 40, the vane 58 The urging force higher than the pressure (approximately Ps) in the compression chamber 48 in the suction stroke, which causes the vane 58 to protrude toward the inner peripheral surface 49a of the cylinder 40, is applied to the end surfaces 26 of the side blocks 20, 30. , 36 is supplied from the high-pressure holes 27, 37, so that the protrusion of the vane 58 protrudes when the tip of the protrusion side of the vane 58 passes through the substantially elliptical minor axis position of the inner peripheral surface 49a of the cylinder 40. An appropriate protrusion (follow-up) that keeps the tip on the side in contact with the inner peripheral surface 49a according to the substantially elliptical shape of the inner peripheral surface 49a of the cylinder 40 can be ensured.

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

Explanation of symbols

20, 30 Side block 21 Discharge chamber 25, 35 Salai groove (intermediate pressure supply groove)
26, 36 Side block end surfaces 27, 37 High pressure holes 28, 38 Back pressure communication passage 40 Cylinder 48 Compression chamber 49a Inner peripheral surface 50 Rotor 50a, 50b Rotor end surface 56 Vane groove 58 Vane 59 Back pressure chamber 100 Compressor (Gas compressor )

Claims (2)

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, With two side blocks covering from
A compression chamber whose volume changes with the rotation of the rotor is defined by the two vanes, the cylinder, the rotor, and the both side blocks that follow each other in the rotation direction of the rotor,
The vane protrudes toward the inner peripheral surface of the cylinder with respect to the vane when the tip of the protruding side of the vane passes through the substantially elliptical minor axis position of the cylinder. A gas compressor characterized in that a high-pressure hole for supplying an urging force higher than the pressure is formed in an end face of the side block.   An intermediate pressure supply groove formed on an end surface of the side block for supplying an urging force for projecting a vane defining the compression chamber corresponding to a compression stroke toward an inner peripheral surface of the cylinder; and the high pressure hole; 2. The gas compressor according to claim 1, wherein the intermediate pressure supply groove and the high pressure hole are formed so as not to communicate with each other through the embedded space of the vane formed in the rotor.

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