JP2013194549A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To appropriately prevent over-compression in a compression chamber, in a gas compressor.SOLUTION: An auxiliary discharge part 46 is formed at a position where a sum S of an opening area S2 of the auxiliary discharge part 46 opened in a range between a rear surface 58b of a vane 58 on an downstream side of a compression chamber 43 and a front surface 58a of a vane 58 on an upstream side and an opening area S1 of a main discharge part 45 is always set at an area not smaller than the overall opening area SA1 or SA2 of a smaller one out of both the discharge parts 45, 46 in a period from a stage where an extension line L1 of the rear surface 58b of the vane 58 on the downstream side in a rotating direction W of the compression chamber 43 passes through the whole of the auxiliary discharge part 46 by rotation of a rotor 50 to a stage where the extension line L1 passes through the whole of the main discharge part 45; and refrigerant gas G is smoothly discharged to the discharge part 45 or 46 through an opening of a sufficient area (area S) from at least one of the auxiliary discharge part 46 and the main discharge part 45 from the compression chamber 43 even when over-compression of the refrigerant gas G of the compression chamber 43 is about to occur.

Description

  The present invention relates to a gas compressor, and more particularly to an improvement of a vane rotary type gas compressor.

  Conventionally, a gas compressor for compressing a gas such as a refrigerant gas and circulating the gas in the air conditioning system is used in the air conditioning system.

  In this gas compressor, a compressor main body that is driven to rotate and compresses gas is housed in a housing, and a discharge chamber into which a high-pressure gas is discharged from the compressor main body is defined. The high-pressure gas is discharged outside.

  As an example of such a gas compressor, a so-called vane rotary type is known.

  In this vane rotary type gas compressor, a compressor main body is accommodated in a housing. The compressor main body includes a substantially cylindrical rotor that rotates integrally with a rotation shaft, A cylinder having a contoured inner peripheral surface that surrounds from the outside of the rotor, a plurality of plate-shaped vanes provided so as to protrude outward from the peripheral surface of the rotor, and rotating shafts protruding from both end surfaces of the rotor Bearings that are freely supported are formed, and provided with side blocks that are in contact with both end surfaces of the rotor and the cylinder and block the both end surfaces, and the outer peripheral surface of the rotor, the inner peripheral surface of the cylinder, and the inner sides of both side blocks. A cylinder chamber, which is a space where gas is sucked, compressed, and discharged, is formed.

  The cylinder chamber is configured such that the protruding tip of each vane protruding from the circumferential surface of the rotor contacts the inner circumferential surface of the cylinder, so that the outer circumferential surface of the rotor, the inner circumferential surface of the cylinder, the inner surfaces of both side blocks, and the rotor Are divided into a plurality of compression chambers by the surfaces of two vanes that follow each other along the rotation direction.

  The contour shape of the inner peripheral surface of the cylinder is set such that the interval between the outer peripheral surface of the rotor and the inner peripheral surface of the cylinder changes for each rotation angle position of the rotor.

  Specifically, on the upstream side in the rotation direction of the rotor, the interval is set so as to increase rapidly from a small state. As the rotor rotates, the volume of the compression chamber expands and is compressed through the suction portion. This corresponds to the process of inhaling gas into the room.

  Next, the interval is set so as to gradually decrease toward the downstream in the rotation direction of the rotor, and the volume of the compression chamber decreases as the rotor rotates, and the gas in the compression chamber is compressed. It corresponds.

  Further, the downstream side in the rotation direction of the rotor is set so that the interval is further reduced, and a process in which the compressed gas in the compression chamber is discharged to the outside of the compression chamber through the discharge portion as the rotor rotates. In response to the above, the suction stroke, compression stroke, and discharge stroke are repeated in this order as the rotor rotates, so that the low-pressure gas sucked from the outside can be discharged as high-pressure gas (Patent Literature). 1).

JP 54-28008 A

  However, since the vane rotary type compressor compresses the gas suddenly, overcompression is likely to occur in the compression chamber, and power loss increases accordingly, and the pressure difference between adjacent compression chambers increases. More efficient than other types of gas compressors (coefficient of performance or COP (Coefficient of Performance)) due to the fact that gas is likely to leak from the compression chamber downstream in the rotation direction to the compression chamber upstream in the rotation direction. Power)) tended to be low.

  And such a tendency of low efficiency becomes a problem especially at the time of high rotation operation of the gas compressor.

  This invention is made | formed in view of the said situation, Comprising: The gas compressor which can prevent the overcompression in a compression chamber appropriately is provided.

  The first gas compressor according to the present invention has reached a discharge pressure that causes overcompression in a stage before the compression chamber faces a discharge section (hereinafter referred to as a main discharge section) that discharges compressed gas from the compression chamber. However, since the compression chamber faces another discharge portion (hereinafter referred to as a sub-discharge portion) provided upstream of the main discharge portion in the rotation direction of the rotor, the discharge pressure gas in the compression chamber is The gas is discharged from the compression chamber to the outside through the sub-discharge unit and appropriately prevents the gas in the compression chamber from being overcompressed.

  Moreover, the first gas compressor according to the present invention has a surface (rear surface in the rotation direction) facing the compression chamber of the vane on the downstream side in the rotation direction of the specific compression chamber (front side in the rotation direction) by rotation of the rotor. During the period from when the extension line passes through the entire sub-discharge section to the stage when the extension line passes through the entire main discharge section, the rear face and the rotation direction of the vane downstream of that specific compression chamber Part or all of the opening area of the sub-discharge part and part of the main discharge part opened in the range between the upstream side (rear side in the rotational direction) of the vane and the surface facing the compression chamber (front side in the rotational direction) Alternatively, since the sub-discharge part is formed at a position where the total of all the opening areas is larger than the smaller one of the two discharge parts, the over-compression is performed during the above-described period. Even if it is likely to occur, from the compression chamber, the sub discharge part and the main discharge part From at least one Chi, in which through a sufficiently wide opening i.e. at least towards the opening area is small in the whole of the discharge opening areas over the width of the opening, thereby smoothly discharging the compressed gas to the discharge portion.

  That is, the first gas compressor according to the present invention is a gas compressor in which a compressor main body is housed in a housing, wherein the compressor main body is a substantially cylindrical rotor that rotates integrally with a rotation shaft; A cylinder having a contour-shaped inner peripheral surface that surrounds the rotor from the outer peripheral surface of the rotor, and a predetermined discharge portion, and from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder A plurality of plate-like vanes provided so as to be freely projectable, and two side blocks that block both ends of the rotor and the cylinder, and the vane is provided between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor. A plurality of compression chambers are formed by partitioning the formed space, and each of the formed compression chambers sucks and compresses gas and discharges from the discharge section during one rotation of the rotor. 1 rhino When the pressure of the gas inside the compression chamber reaches the discharge pressure on the upstream side in the rotation direction of the rotor of the discharge portion, the contour shape of the inner peripheral surface of the cylinder is set so as to perform only One or more sub-discharge portions for discharging gas inside the compression chamber are formed, and an extension line of a surface of the vane on the downstream side in the rotation direction of the compression chamber facing the compression chamber is formed by the rotation of the rotor. The period from the stage of passing through the entire sub-discharge part to the stage of passing the extension line through the whole of the discharge part is always the surface facing the compression chamber of the vane on the downstream side in the rotational direction and the upstream side in the rotational direction The total of the opening area of a part or the whole of the sub-discharge part and the part or the whole opening area of the discharge part opened in a range between the surface of the vane facing the compression chamber is the discharge part. And the sub-ejection part The breadth to become such a position above the opening area of the body, wherein the secondary discharge portion.

  On the other hand, the second gas compressor according to the present invention has a discharge pressure at which the compression chamber becomes overcompressed before the compression chamber faces a discharge section (hereinafter referred to as a main discharge section) that discharges the compressed gas from the compression chamber. Even if the pressure reaches, the compression chamber faces another discharge portion (hereinafter referred to as a sub discharge portion) provided upstream of the main discharge portion in the rotation direction of the rotor. The gas is discharged from the compression chamber to the outside through the sub discharge section, and appropriately prevents the gas in the compression chamber from being overcompressed.

  Moreover, the second gas compressor according to the present invention has a surface (rear surface in the rotation direction) facing the compression chamber of the vane on the downstream side in the rotation direction of the specific compression chamber (front side in the rotation direction) due to the rotation of the rotor. When the extension line passes through the center of the opening of the main discharge section, the center of the opening of the sub-discharge section faces the compression chamber of the vane on the upstream side in the rotation direction (rear side in the rotation direction) of the specific compression chamber Since the sub-discharge portion is formed so as to be arranged on the downstream side in the rotation direction with respect to the extension line of (the front surface in the rotation direction), even if overcompression is likely to occur during the above-described period, the compression chamber From at least one of the sub-discharge part and the main discharge part, the compressed gas smoothly passes through an opening having a sufficiently wide opening, that is, an opening having a width larger than the entire opening area of the discharge part having a smaller opening area. Is discharged to the discharge portion.

  That is, the second gas compressor according to the present invention is a gas compressor in which a compressor main body is housed in a housing, wherein the compressor main body is a substantially cylindrical rotor that rotates integrally with a rotating shaft, and a rotor. The cylinder has a contour-shaped inner peripheral surface that surrounds the outer peripheral surface of the rotor from the outside, and is provided so as to protrude from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder. A plurality of plate-like vanes and two side blocks that block both ends of the rotor and the cylinder, and the vanes are divided into a plurality of spaces by partitioning a space formed between the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor. The inner circumferential surface of the cylinder is such that each of the formed compression chambers performs gas suction, compression, and discharge from the discharge section for only one cycle during the period of one rotation of the rotor. The contour shape of One or more sub-discharge sections that discharge the gas inside the compression chamber when the pressure of the gas inside the compression chamber reaches the discharge pressure on the upstream side of the rotation direction of the rotor of the discharge section, When the extension of the surface of the vane facing the compression chamber downstream of the rotation direction in the compression chamber passes through the center of the discharge portion opening due to the rotation of the rotor, the center of the sub discharge portion opening is the rotation direction in the compression chamber. The sub-discharge part is formed at a position where the upstream vane is arranged downstream of the extension line of the surface facing the compression chamber.

  The gas compressor according to the present invention can appropriately prevent over-compression in the compression chamber.

  In addition, according to the gas compressor according to the present invention, during one rotation of the rotor, the gas is sucked, compressed, and discharged from the discharge unit for only one cycle. The required power can be reduced.

It is a cross-sectional view of the vane rotary compressor which is one Embodiment of the gas compressor which concerns on this invention. It is sectional drawing along the AA line of the compressor part of the vane rotary compressor shown in FIG. FIG. 2 is a diagram schematically showing a positional relationship between a main discharge portion and a sub discharge portion in the compressor of Embodiment 1, wherein (a) is an extension line on the rear surface of the vane on the downstream side in the rotation direction of the compression chamber. (B) shows the state of the stage where the extension line of the rear surface of the vane on the downstream side in the rotation direction of the compression chamber has passed through the entire discharge hole of the main discharge part. . FIG. 4 is a diagram schematically showing a discharge hole of a main discharge portion and a discharge hole of a sub discharge portion that open to one compression chamber during the period shown in FIG. 3, and (a) is a cross-section corresponding to FIG. b) shows the opening of each discharge hole by the arrow B in (a). It is the figure which showed typically the positional relationship of the 1st sub discharge part and the 2nd sub discharge part in the compressor of the modification 1, (a) is the rear surface of the vane of the downstream of the rotation direction of a compression chamber. A state in which the extension line has passed through the entire discharge hole of the second sub-discharge section, (b) is an extension line on the rear surface of the vane on the downstream side in the rotation direction of the compression chamber, and the discharge line of the first sub-discharge section The state of the stage which passed through the whole of each is shown. FIG. 6 is a diagram schematically showing a discharge hole of a main discharge portion and a discharge hole of a sub discharge portion that open in one compression chamber during the period shown in FIG. 5, (a) is a cross-section corresponding to FIG. b) shows the opening of each discharge hole by the arrow B in (a). FIG. 7 is a view corresponding to FIG. 6, illustrating a second modification of the compressor of the first embodiment, where (a) is a cross-section corresponding to FIG. 5, and (b) is an opening of each discharge hole by arrow B in (a). Indicates. 6 is a diagram corresponding to FIGS. 6 and 7, showing a compressor according to Embodiment 2, wherein (a) shows a cross-section corresponding to FIG. 5, and (b) shows an opening of each discharge hole by arrow B in (a). .

  Hereinafter, specific embodiments of a gas compressor according to the present invention will be described in detail with reference to the drawings.

(Embodiment 1)
An electric vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of the first gas compressor according to the present invention, is installed in an automobile or the like, an evaporator, a gas compressor, a condenser, and an expansion. It is used as a gas compressor in an air conditioning system having a valve. The working medium of this air conditioning system is refrigerant gas G (gas).

  As shown in FIG. 1, the compressor 100 has a configuration in which a motor 90 and a compressor main body 60 are accommodated in a housing 10 mainly composed of a main body case 11 and a front cover 12.

  The main body case 11 has a substantially cylindrical shape, and is formed such that one end portion of the cylindrical shape is closed, and the other end portion is opened.

  The front cover 12 is formed in a lid shape so as to close the opening while being in contact with the opening-side end portion of the main body case 11. In this state, the front cover 12 is fastened to the main body case 11 by a fastening member. And a housing 10 having a space inside is formed.

  The front cover 12 is formed with a suction port 12 a through which the low-pressure refrigerant gas G is introduced from the evaporator of the air conditioning system into the housing 10 through the inside and the outside of the housing 10.

  On the other hand, the main body case 11 is formed with a discharge port 11a through which the high-pressure refrigerant gas G is discharged from the inside of the housing 10 to the condenser of the air conditioning system through the inside and the outside of the housing 10.

  The motor 90 provided inside the main body case 11 constitutes a multiphase brushless DC motor including a permanent magnet rotor 90a and an electromagnet stator 90b.

  The stator 90b is fitted and fixed to the inner peripheral surface of the main body case 11, and the rotating shaft 51 is fixed to the rotor 90a.

  The motor 90 excites the electromagnet of the stator 90b with the electric power supplied via the power connector 90c attached to the front cover 12, thereby rotating the rotor 90a and the rotating shaft 51 around the axis.

  A configuration including an inverter circuit 90d or the like may be employed between the power connector 90c and the stator 90b.

  Although the compressor 100 of the present embodiment is an electric one as described above, the gas compressor according to the present invention is not limited to an electric one, and may be a mechanical one. If the compressor 100 of the embodiment is mechanical, instead of providing the motor 90, the rotating shaft 51 protrudes from the front cover 12 to the outside, and the front end of the protruding rotating shaft 51 has a vehicle engine. What is necessary is just to set it as the structure provided with the pulley, the gearwheel, etc. which receive motive power transmission from these.

  The compressor main body 60 accommodated in the housing 10 together with the motor 90 is arranged side by side with the motor 90 along the direction in which the rotating shaft 51 extends, and is fixed to the main body case 11 by a fastening member 15 such as a bolt. Has been.

  The compressor body 60 includes a rotating shaft 51 rotated by a motor 90, a substantially cylindrical rotor 50 that rotates integrally with the rotating shaft 51, and the rotor 50 outside the outer peripheral surface 52 (see FIG. 2). A cylinder 40 having a contoured inner peripheral surface 41 surrounding from the side, five plate-like vanes 58 provided so as to protrude from the outer peripheral surface 52 of the rotor 50 toward the inner peripheral surface 41 of the cylinder 40, and the rotor 50 and two side blocks (front side block 20 and rear side block 30) that block both ends of the cylinder 40 are provided.

  Here, the rotating shaft 51 is rotatably supported by bearings 12 b formed on the front cover 12 and bearings 27 and 37 formed on the side blocks 20 and 30 of the compressor body 60, respectively.

  As shown in FIG. 1, the compressor main body 60 divides the space inside the housing 10 into a left space and a right space sandwiching the compressor main body 60.

  And the sealing members, such as O-ring, are installed in the outer peripheral surface of both the side blocks 20 and 30 over the perimeter of the outer peripheral surface, respectively, and these sealing members are all over the inner peripheral surface of the main body case 11. By contacting, airtightness between the left and right spaces sandwiching the compressor main body 60 of FIG. 1 is maintained.

  Among the two spaces partitioned inside the housing 10, the space on the left side of FIG. 1 sandwiching the compressor body 60 is a low-pressure atmosphere suction chamber into which low-pressure refrigerant gas G is introduced from the evaporator through the suction port 12a. The space on the right side of FIG. 1 across the compressor body 60 is a high-pressure atmosphere discharge chamber 14 through which a high-pressure refrigerant gas G is discharged to the condenser through the discharge port 11a.

  As shown in FIG. 2, the compressor main body 60 has a substantially C-shaped single body surrounded by an inner peripheral surface 41 of the cylinder 40, an outer peripheral surface 52 of the rotor 50, and both side blocks 20 and 30. A cylinder chamber 42 is formed.

  Specifically, the cylinder 40 is arranged so that the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are close to each other within one round (angle 360 [degrees]) around the axis of the rotary shaft 51. The outline shape of 40 inner peripheral surfaces 41 is set, and thereby the cylinder chamber 42 forms a single space.

  The proximity portion 48 formed as a portion where the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are closest to each other in the contour shape of the inner peripheral surface 41 of the cylinder 40 is the inner peripheral surface 41 of the cylinder 40. And the outer peripheral surface 52 of the rotor 50 from the remote part 49 formed as the farthest part, along the rotational direction W of the rotor 50 (clockwise direction in FIG. 2), the angle is 270 degrees or more (360). Less than [degree]) is formed at a distant position.

  The contour shape of the inner peripheral surface 41 of the cylinder 40 is such that the distance between the outer peripheral surface 51 of the rotor 50 and the inner peripheral surface 41 of the cylinder 40 is monotonous from the remote portion 49 to the proximity portion 48 along the rotational direction W. The shape is set to decrease.

  The vane 58 is fitted in a vane groove 59 formed in the rotor 50, and protrudes outward from the outer peripheral surface 52 of the rotor 50 due to back pressure by the refrigerating machine oil R supplied to the vane groove 59.

  The vane 58 partitions the single cylinder chamber 42 into a plurality of compression chambers 43, and one compression chamber 43 is formed by the two vanes 58 that move back and forth along the rotation direction W of the rotor 50. Therefore, in the present embodiment in which five vanes 58 are installed around the rotation shaft 51 at an equal angular interval of 72 degrees, five compression chambers 43 are formed.

  However, since the compression chamber 43 is partitioned by the proximity portion 48 and the single vane 58 at the upstream end portion and the downstream end portion of the cylinder chamber 42, six compressions are performed during many periods during the rotation of the rotor 50. There is a period in which five compression chambers 43 are formed only when the chamber 43 is formed and the vane 58 passes through the proximity portion 48.

  The internal volume of the compression chamber 43 obtained by partitioning the cylinder chamber 42 with the vane 58 monotonously decreases along the rotation direction W until the compression chamber 43 reaches the proximity portion 48 from the remote portion 49.

  A suction hole 23 that is formed in the front side block 20 and communicates with the suction chamber 13 faces the upstream portion of the cylinder chamber 42 in the rotation direction W of the rotor 50.

  On the other hand, in the portion of the cylinder chamber 42 on the downstream side in the rotational direction W of the rotor 50, two discharge holes 45b and 46b respectively communicating with the two discharge portions 45 and 46 formed in the cylinder 40 respectively face. Yes.

  Each compression chamber 43 performs the suction of the refrigerant gas G through the suction hole 23, the compression of the refrigerant gas G, and the discharge of the refrigerant gas G to the discharge portions 45 and 46 during one rotation of the rotor 50 for one cycle. Further, the contour shape of the inner peripheral surface 41 of the cylinder 40 is set.

  On the upstream side in the rotational direction W of the rotor 50, the contour shape of the inner peripheral surface 41 is set so that the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 increases rapidly from a small state. In the angle range including the remote portion 49, the volume of the compression chamber 43 increases with the rotation of the rotor 50 in the rotation direction W, and the stroke in which the refrigerant gas G is sucked into the compression chamber 43 through the suction hole 23 (suction) Process).

  Next, the contour shape of the inner peripheral surface 41 is set so that the distance between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 gradually decreases toward the downstream in the rotation direction W of the rotor 50. In this range, the volume of the compression chamber 43 decreases with the rotation of the rotor 50, and a stroke (compression stroke) in which the refrigerant gas G in the compression chamber 43 is compressed.

  Further, on the downstream side in the rotation direction W of the rotor 50, the interval between the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 is further reduced, and the compression of the refrigerant gas G further proceeds. When the discharge pressure is reached, the refrigerant gas G becomes a stroke (discharge stroke) discharged to the discharge portions 45 and 46 through discharge holes 45b and 46b described later.

  As the rotor 50 rotates, the compression chambers 43 repeat the suction stroke, the compression stroke, and the discharge stroke in this order, so that the low-pressure refrigerant gas G sucked from the suction chamber 13 is increased to a high pressure. 60.

  Each of the discharge portions 45 and 46 includes a space surrounded by the cylinder 40, both side blocks 20 and 30, and the main body case 11 (hereinafter referred to as discharge chambers 45 a and 46 a), discharge chambers 45 a and 46 a, and a compression chamber 43. When the pressure of the refrigerant gas G in the compression chamber 43 is equal to or higher than the pressure (discharge pressure) in the discharge chambers 45a and 46a, the pressure difference is caused to warp toward the discharge chambers 45a and 46a. And the discharge valves 45c and 46c which open the discharge holes 45b and 46b, and close the discharge holes 45b and 46b by the elastic force when the pressure of the refrigerant gas G is less than the pressure (discharge pressure) in the discharge chambers 45a and 46a. And valve supports 45d and 46d for preventing the discharge valves 45c and 46c from excessively warping toward the discharge chambers 45a and 46a.

  Of the two discharge parts 45 and 46, the discharge part provided on the downstream side in the rotation direction W of the rotor 50, that is, the discharge chamber 45 a of the discharge part 45 near the proximity part 48 is connected to the rear side block 30. It communicates with the cyclone block 70 attached to the outer surface of the rear side block 30 (the surface facing the discharge chamber 14) through the formed discharge passage 38.

  Similarly, the discharge chamber 46 a of the discharge portion 46 provided on the upstream side in the rotation direction W of the rotor 50, that is, the discharge portion 46 far from the proximity portion 48, of the two discharge portions 45 and 46 is the rear side block 30. It communicates with the cyclone block 70 through the discharge passage 39 formed in the above.

  The cyclone block 70 mainly separates the refrigerating machine oil R mixed with the refrigerant gas G from the refrigerant gas G, and is discharged into the discharge chambers 45a and 46a and introduced through the discharge passages 38 and 39. The refrigerating machine oil R is centrifuged by rotating the gas G in a spiral shape.

  The refrigerating machine oil R separated from the refrigerant gas G accumulates at the bottom of the discharge chamber 14, and the high-pressure refrigerant gas G after the refrigerating machine oil R is separated is discharged into the discharge chamber 14 and then passes through the discharge port 11a. And discharged to the condenser.

  The refrigerating machine oil R stored at the bottom of the discharge chamber 14 is supplied with oil passages 34a formed in the rear side block 30 and salai grooves that are back pressure supply recesses formed in the rear side block 30 due to the high pressure atmosphere in the discharge chamber 14. 31, 32, and oil passages 34 a and 34 b formed in the rear side block 30, an oil passage 44 formed in the cylinder 40, an oil passage 24 formed in the front side block 20, and the front side block 20. The back pressure is supplied to the vane groove 59 of the rotor 50 through the Sarai grooves 21 and 22 which are recesses for supplying the back pressure, and the back pressure causes the vane 58 to protrude outward.

  The refrigerating machine oil R starts to ooze out from the gap between the vane 58 and the vane groove 59, the gap between the rotor 50 and the side blocks 20, 30, and the like, and is formed between the rotor 50 and the side blocks 20, 30. A lubricating portion and a cooling function are also exerted in a contact portion between them and a contact portion between the vane 58 and the cylinder 40 or both side blocks 20 and 30, and a part of the refrigerating machine oil R is used as a refrigerant in the compression chamber 43. In order to be mixed with the gas G, the refrigerating machine oil R is separated by the cyclone block 70.

  Of the two salai grooves 31 and 32 formed in the rear side block 30, the salai grooves 31 are formed in the upstream portion of the rotor 50 in the rotation direction W (corresponding to the suction stroke and the compression stroke). The refrigerating machine oil R is supplied from the oil passage 34 a through the narrow gap between the bearing 37 and the outer peripheral surface of the rotary shaft 51 to the Saray groove 31, and therefore, between the bearing 37 and the outer peripheral surface of the rotary shaft 51. The pressure loss at the time of passing through the narrow gap becomes an intermediate pressure (pressure higher than the suction pressure that is the atmosphere of the suction chamber 13) lower than the high pressure (pressure close to the discharge pressure) that is the atmosphere of the discharge chamber 14.

  Of the two salai grooves 21 and 22 formed in the front side block 20, the refrigerating machine oil R supplied to the salai groove 21 formed in the upstream portion of the rotation direction W of the rotor 50 is also in the salai groove 31. Similar to the refrigerating machine oil R to be supplied, it has an intermediate pressure.

  On the other hand, the refrigerating machine oil R supplied to the Saray groove 32 formed in the downstream part of the rotor 50 in the rotational direction W (mainly the part corresponding to the discharge stroke) of the two Saray grooves 31 and 32 is oil. Since the pressure is supplied from the passage 34a without any pressure loss, the pressure is close to the high pressure that is the atmosphere of the discharge chamber 14 (higher than the medium pressure).

  Of the two salai grooves 21 and 22, the refrigerating machine oil R supplied to the sarai groove 22 formed in the downstream portion of the rotation direction W of the rotor 50 is the same as the refrigerating machine oil R supplied to the sarai groove 32. High pressure.

  Then, when the vane groove 59 penetrating to both end faces of the rotor 50 is connected to the Sarai grooves 21, 31, 22, 32 of the side blocks 20, 30 by the rotation of the rotor 50, the connected Saray grooves 21. , 31, 22, 32 are supplied to the vane groove 59, and the pressure of the supplied refrigerator oil R becomes a back pressure that causes the vane 58 to protrude.

  Next, the two discharge parts 45 and 46 in the compressor 100 of this embodiment will be described in detail.

  First, along the rotation direction W of the rotor 50, the discharge unit 45 formed on the upstream side immediately before the proximity unit 48 performs only one compression cycle of suction, compression, and discharge for each rotation of the rotor 50. This corresponds to the original single discharge part in a gas compressor having only a single discharge part, and can be called a main discharge part.

  Therefore, in the following description, in order to clarify the distinction between the main discharge unit 45 and the secondary discharge unit 46, the discharge unit 45 is referred to as the main discharge unit 45 as necessary, and the main discharge unit 45 is referred to. On the other hand, the discharge part 46 formed on the upstream side in the rotation direction W may be referred to as a sub-discharge part 46.

  As described above, the main discharge part 45 is compressed by the action of the discharge valve 45c so that the compression chamber 43 facing the discharge hole 45b of the main discharge part 45 (when the compression chamber 43 needs to be distinguished from the other compression chambers 43). Is referred to as the pressure of the refrigerant gas G in the compression chamber 43A) becomes higher than the pressure (discharge pressure) in the discharge chamber 45a, the refrigerant gas G in the compression chamber 43 is discharged through the discharge hole 45b. It is configured to be discharged into the chamber 45a.

  A compression chamber 43 adjacent to the compression chamber 43A on the upstream side in the rotation direction W of the rotor 50 with respect to the compression chamber 43A (when it is necessary to distinguish this compression chamber 43 from other compression chambers 43, the compression chamber 43B) is larger than the volume of the compression chamber 43A when the compression chamber 43A faces the discharge hole 45b of the main discharge portion 45, but to a position where the compression chamber 43B faces the discharge hole 45b of the main discharge portion 45. Before the rotation, the pressure of the refrigerant gas G compressed in the compression chamber 43B may reach the above-described discharge pressure.

  In such a case, in the gas compressor in which only one discharge portion (only the main discharge portion 45) is formed, the volume of the compression chamber 43B is further reduced by the further rotation of the rotor 50, and thus the inside of the compression chamber 43B. Although the pressure of the refrigerant gas G exceeds the discharge pressure, the refrigerant gas G exceeding the discharge pressure is not discharged before the compression chamber 43B rotates to the position facing the discharge hole 45b of the main discharge portion 45. Of the two vanes 58 and 58 partitioning 43B, the cylinder 40 is applied to the cylinder 40 by the resultant force of the back pressure from the vane groove 59 by the refrigerating machine oil R of the vane 58 upstream in the rotation direction W and the centrifugal force acting on the vane 58. When the load for pushing back the vane 58 from the cylinder 40 on the tip side due to the internal pressure of the compression chambers 43A and 43B exceeds the pressing load of the vane 58, the vane 58 protrudes. Tip will produce the chattering away momentarily from the inner peripheral surface 41 of the cylinder 40.

  However, in the compressor 100 of the present embodiment, when the pressure of the refrigerant gas G inside the compression chamber 43B reaches the discharge pressure before reaching the discharge hole 45b of the main discharge portion 45, the inside of the compression chamber 43B Since the sub discharge part 46 for discharging the refrigerant gas G to the outside of the compression chamber 43B is provided on the upstream side of the main discharge part 45 in the rotation direction W of the rotor 50, the refrigerant gas G inside the compression chamber 43B Even when the pressure reaches the discharge pressure before reaching the discharge hole 45b of the main discharge portion 45, the refrigerant gas G inside the compression chamber 43B is discharged into the discharge chamber through the discharge hole 46b of the sub discharge portion 46. The over-compression that is discharged to 46a and the pressure of the refrigerant gas G in the compression chamber 43B exceeds the discharge pressure can be appropriately prevented.

  Therefore, the vane 58 partitioning the compression chamber 43B does not generate chattering.

  Furthermore, the compressor 100 according to the present embodiment rotates the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 (for example, the compression chamber 43B) as shown in FIG. The extension line L1 of the surface 58b facing the compression chamber 43B (hereinafter simply referred to as the rear surface 58b) passes through the entire discharge hole 46b of the sub-discharge section 46 (the state shown in FIG. 3A). As shown in FIG. 4, the extension line L1 is always in the rotational direction W of the compression chamber 43B during the period up to the stage where the extension line L1 passes through the entire discharge hole 45b of the main discharge portion 45 (state shown in FIG. 3B). The downstream side vane 58 (the right side vane 58 of the two vanes 58 and 58 depicted by the solid line in each of FIGS. 3A, 3B, 4A, and 4B). The rear surface 58b and the vane 58 on the upstream side in the rotation direction W (FIG. 3A) 4B and 4B, a surface 58a (hereinafter, simply referred to as a compression chamber 43B) of a vane 58 on the left side of the two vanes 58 drawn by a solid line. Between the front surface 58a) and a part or all of the opening area S2 of the discharge hole 46b of the sub-discharge part 46 opened to the compression chamber 43B and part or all of the discharge hole 45b of the main discharge part 45. At a position where the total S (= S1 + S2) with the opening area S1 is larger than the entire opening area of the smaller one of the discharge holes 45b and 46b of both the discharge parts 45 and 46, the sub-discharge part 46 A discharge hole 46b is formed.

  3 and 4 describe the inner peripheral surface 41 of the cylinder 40 in a planar shape, and also describe the posture and positional relationship in which the vanes 58 are orthogonal to the inner peripheral surface 41 and parallel to each other. However, such a schematic description is for convenience of explaining the positional relationship between the discharge holes 45b and 46b of the discharge portions 45 and 46 and the compression chamber 43 in an easy-to-understand manner. FIG. 3 schematically illustrates the first embodiment in which the contour shape of the surface 41 is a curve and each vane 58 is in contact with the inner peripheral surface 41 at an inclined angle other than an angle of 90 degrees. , 4 does not cause inconsistencies.

  Here, the opening area of the discharge holes 45b and 46b may be an area on the surface along the inner peripheral surface 41 of the cylinder 40, or when the vane 58 passes through the discharge holes 45b and 46b. The projected area may be a plane perpendicular to the extension line L1 of the rear surface 58b of the vane 58 or the extension line L2 of the front surface 58a.

  Note that the entire opening area SA1 of the discharge hole 45b of the main discharge part 45 and the entire opening area SA2 of the discharge hole 46b of the sub-discharge part 46 in the compressor 100 of the present embodiment are set equal to each other. In the compressor 100, the discharge hole 46b of the sub-discharge portion 46 is formed so that SA1 ≦ S or SA2 ≦ S.

  In the compressor 100 of the present embodiment, the discharge hole 46b of the sub-discharge part 46 thus has a partial or total opening area S2 of the discharge hole 46b of the sub-discharge part 46 opened in the compression chamber 43 and the main discharge part 45. A sum S (= S1 + S2) of a part or all of the opening area S1 of the discharge holes 45b is equal to or larger than the entire opening area SA1 or the opening area SA2 of one of the discharge holes 45b and 46b of both the discharge portions 45 and 46. Since it is formed at such a position (SA1 ≦ S or SA2 ≦ S), the extension line L1 of the rear surface 58b of the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 has a secondary line L1. The stage where the extended line L1 passes through the entire discharge hole 45b of the main discharge section 45 from the stage where the entire discharge hole 46b of the discharge section 46 has passed (state of FIG. 3A) (state of FIG. 3B) ) Until Even if the refrigerant gas G inside the compression chamber 43 is likely to be over-compressed exceeding the discharge pressure, the discharge hole 46b of the sub-discharge portion 46 and the discharge hole 45b of the main discharge portion 45 are discharged from the compression chamber 43. From at least one of them, an opening having a sufficient width S, that is, an opening area S1 that is greater than or equal to the entire opening area SA1 of the discharge hole 45b of the main discharge part 45 or an opening area S that is greater than or equal to the entire opening area SA2 of the discharge hole 46b of the sub-discharge part 46. The refrigerant gas G can be smoothly and smoothly discharged from the compression chamber 43 to the discharge chamber 45a of the main discharge portion 45 to the discharge chamber 46a of the sub discharge portion 46 through the openings (discharge holes 45b and 46b). it can.

  Note that, according to the compressor 100 of the first embodiment, the refrigerant gas G is sucked, compressed, and discharged for only one cycle during one rotation of the rotor 50, and therefore the refrigerant gas G is used during one rotation of the rotor 50. The refrigerant gas G can be compressed more slowly than the one that performs two cycles of suction, compression, and discharge, reducing the required power and compressing chambers 43, 43 adjacent to each other in the rotational direction. And the refrigerant gas G leaks from the minute gap between the vane 58 and the cyclone blocks 20 and 30 to the compression chamber 43 adjacent to the upstream side in the rotation direction, and the efficiency can be suppressed. .

  In addition, the proximity portion 48 of the inner peripheral surface 41 of the cylinder 40 is formed at a position away from the remote portion 49 along the rotational direction W of the rotor 50 on the downstream side by an angle of 270 degrees or more. However, the refrigerant gas G can be compressed more gently than the gas compressor having the contoured inner peripheral surface 41 formed at a position away from the remote portion 49 by an angle of about 180 [deg.], And the degree of efficiency reduction is reduced. Can be further reduced.

  In the compressor 100 of this embodiment, the entire opening area SA1 of the discharge hole 45b of the main discharge part 45 and the entire opening area SA2 of the discharge hole 46b of the sub-discharge part 46 are set to be equal. The gas compressor according to the invention is not limited to the one in which the opening areas of the two discharge parts (discharge holes) are the same, and any one of the discharge parts (discharge holes) is the other discharge part (discharge hole). ), And the total opening area S of the discharge portions (discharge holes) opening in the compression chamber is smaller in the overall opening area SA1 or SA2. The installation position of the second discharge part (sub-discharge part (discharge hole)) may be set so as to be larger than the opening area SA1 or SA2 of the discharge part (discharge hole).

  From the viewpoint of suppressing the influence of the refrigerant gas G accumulated in the dead volume of the sub discharge part (discharge hole) on the upstream compression chamber in the rotation direction W, the opening area of the sub discharge part (discharge hole) is mainly set. It is preferable to set it smaller than the opening area of the discharge part (discharge hole).

(Modification 1)
In addition, the compressor 100 of the present embodiment is provided with only one sub-discharge portion 46 upstream of the main discharge portion 45 in the rotational direction W of the rotor 50. The machine is not limited to this form, and a configuration in which another sub-discharge portion is further provided on the upstream side in the rotation direction W of the rotor 50 with respect to the sub-discharge portion 46 may be adopted.

  In this case, as shown in FIG. 5, the rotation of the rotor 50 in the rotation direction W causes the compression chamber 43 (for example, the compression chamber 43C) to enter the compression chamber 43C of the vane 58 on the downstream side in the rotation direction W. An extended line L1 of the facing surface 58b (hereinafter simply referred to as the rear surface 58b) is further provided with a discharge hole 47b (the entire opening area) of the sub discharge portion 47 (hereinafter referred to as the second sub discharge portion 47). The extension line L1 extends from the stage of passing through SA3 (the state shown in FIG. 5A) to the entire discharge hole 46b of the sub-discharge section 46 (hereinafter referred to as the first sub-discharge section 46). As shown in FIG. 6, the vane 58 on the downstream side in the rotation direction W of the compression chamber 43C (FIGS. 5A and 5B) is always used during the period up to the passing stage (the state shown in FIG. 5B). 6 (a) and 6 (b), two vanes 5 drawn by solid lines. , 58, the rear surface 58b of the right side vane 58 in the figure and the upstream side vane 58 in the rotational direction W (in each of FIGS. 5 (a), (b), 6 (a), (b)), it is indicated by a solid line. Of the two drawn vanes 58, 58, a second opening opened to the compression chamber 43C in a range between a surface 58a facing the compression chamber 43C (hereinafter simply referred to as the front surface 58a) of the left vane 58 in the drawing. The total S ′ (= S2 + S3) of a part or all of the opening area S3 of the discharge hole 47b of the sub-discharge part 47 and a part or all of the opening area S2 of the discharge hole 46b of the first sub-discharge part 46 is The discharge hole 47b of the second sub-discharge portion 47 is located at a position that is larger than the smaller overall opening area (SA2 or SA3) of the discharge holes 46b, 47b of both the sub-discharge portions 46, 47. It only has to be formed.

  According to the compressor 100 configured as described above, the extension line L1 of the rear surface 58b of the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 extends over the entire discharge hole 47b of the second sub-discharge portion 47. During the period from the passing stage (state of FIG. 5 (a)) to the stage (state of FIG. 5 (b)) where the extension line L1 passes through the entire ejection hole 46b of the first sub-ejection section 46). Even if the refrigerant gas G inside the compression chamber 43 is likely to be over-compressed exceeding the discharge pressure, the discharge hole 47b of the second sub-discharge portion 47 and the first sub-discharge are discharged from the compression chamber 43. From at least one of the discharge holes 46b of the portion 46, an opening having a sufficient width S ′, that is, the entire opening area SA2 of the discharge hole 46b of the first sub-discharge portion 46 or the discharge of the second sub-discharge portion 47 The total opening area SA3 or more opening area of the hole 47b Through the openings (discharge holes 46b, 47b), the refrigerant gas G from the compression chamber 43 smoothly into the discharge chamber 46a of the first sub-discharge section 46 to the discharge chamber 47a of the second sub-discharge section 47, and It can be discharged without interruption.

(Modification 2)
In the compressor 100 of the above embodiment, the extension line L1 of the rear surface 58b of the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 passes through the entire discharge hole 46b of the sub discharge portion 46 in the above-described period. During a specific period of time from the stage (state of FIG. 3 (a)) to the stage (state of FIG. 3 (b)) when the extension line L1 passes through the entire discharge hole 45b of the main discharge portion 45. 7, all of the discharge holes 46 b (opening area SA 2) of the sub-discharge part 46 and all of the discharge holes 45 b (opening area SA 1) of the main discharge part 45 are simultaneously provided in one compression chamber 43, as shown in FIG. The installation position of the ejection hole 46b of the sub-ejection unit 46 may be set so as to open to (S = SA1 + SA2).

  In this way, the discharge holes 46b of the sub-discharge portion 46 are installed so that all of the discharge holes 46b of the sub-discharge portion 46 and all of the discharge holes 45b of the main discharge portion 45 are simultaneously opened into one compression chamber 43. According to the compressor 100 whose position is set, a larger area S can be obtained during a period in which all of the discharge holes 46b of the sub-discharge part 46 and all of the discharge holes 45b of the main discharge part 45 are simultaneously opened in the compression chamber 43. Through the opening, the refrigerant gas G can be discharged more smoothly from the compression chamber 43.

  Note that each of the discharge holes 45b, 46b, 47b of the main discharge portion 45 and the sub discharge portions 46, 47 in the compressor 100 of the first embodiment and the first and second modifications described above is an opening in the inner peripheral surface 41 of the cylinder 40. However, the shape of the opening of each discharge portion (discharge hole) according to the present invention is not limited to this shape, and may be any shape including a rectangular shape. Can be adopted. However, from the viewpoint of ease of processing, the shape of the discharge part (discharge hole) is preferably circular.

(Embodiment 2)
1 and 2 also show an electric vane rotary compressor 100 '(hereinafter simply referred to as a compressor 100') which is an embodiment of the second gas compressor according to the present invention. The premise of 100 ′ is the same as that of the compressor 100 of the first embodiment.

  That is, the compressor 100 ′ of the second embodiment has the same configuration as the compressor 100 of the first embodiment except for the difference in the installation position of the sub-ejection unit 46.

  Therefore, the description of the compressor 100 ′ of the second embodiment will be omitted from the description of the compressor 100 of the first embodiment, and the description of the configuration other than the above-described differences and the operations and effects of the configuration will be omitted. It shall be carried out only for the actions and effects of the structure related to the difference and the structure related to the difference.

  As shown in FIG. 8, the compressor 100 ′ of the second embodiment has an extension line L <b> 1 of the rear surface 58 b of the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 as the rotor 50 rotates in the rotation direction W. When the center 45m of the discharge hole 45b of the discharge part 45 passes through the center 45m on the inner peripheral surface 41, the center 46m of the discharge hole 46b of the sub-discharge part 46 on the inner peripheral surface 41 rotates in the compression chamber 43. A discharge hole 46b of the sub-discharge portion 46 is formed at a position where it is arranged downstream of the extension line L2 of the front surface 58a of the vane 58 upstream of W in the rotational direction W.

  In addition, although the shape on the inner peripheral surface 41 of each discharge hole 45b, 46b of each discharge part 45, 46 in compressor 100 'of this Embodiment 2 is circular, in the 2nd gas compressor based on this invention, it is. The shape of the opening of the discharge portion (discharge hole) is not limited to a circle, and any shape including a rectangle and a triangle can be adopted.

  In this case, the “center” of the discharge part (discharge hole) to be compared with the extension of the front and rear surfaces of the vane is the opening of the discharge part (discharge hole) on the inner peripheral surface of the cylinder. The “center of gravity” of the shape (various shapes including a rectangle and a triangle) is applied.

  According to the compressor 100 ′ of the second embodiment configured as described above, the center of the opening that is approximately ½ of the opening area of the discharge hole 46 b of the sub-discharge part 46 and the opening of the discharge hole 45 b of the main discharge part 45. The center of the opening, which is approximately ½ of the area, is between the inner surfaces of the two vanes 58 and 58 that partition one compression chamber 43 (the front surface 58a of the upstream vane 58 and the downstream vane 58). Since the discharge hole 46b of the sub-discharge portion 46 is installed in such a positional relationship as to be included in the range between the rear surface 58b and the rear surface 58b, the rear surface 58b of the vane 58 on the downstream side in the rotation direction W of the compression chamber 43 is extended. From the stage where the line L1 passes through the entire discharge hole 46b of the sub-discharge part 46 (state of FIG. 3A), the extended line L1 passes through the entire discharge hole 45b of the main discharge part 45 (FIG. 3). During the period until (b) state), the pressure Even if the refrigerant gas G inside the chamber 43 is likely to be over-compressed exceeding the discharge pressure, at least one of the discharge hole 46 b of the sub-discharge portion 46 and the discharge hole 45 b of the main discharge portion 45 is discharged from the compression chamber 43. From the compression chamber 43, the refrigerant gas G can be smoothly and smoothly discharged from the compression chamber 43 to the discharge chamber 45a of the main discharge portion 45 to the discharge chamber 46a of the sub discharge portion 46 through the sufficiently wide opening. .

  In each of the compressors 100 and 100 ′ of the first and second embodiments and the first and second modifications described above, the description has been made assuming that five vanes 58 are provided. However, each gas compressor according to the present invention is limited to this embodiment. However, the number of vanes can be selected as appropriate, such as 2, 3, 4, or 6, and the above-described embodiment and compressor can be used by a gas compressor to which the selected number of vanes are applied. The same operation and effect as 100 and 100 'can be obtained.

20 Front side block 30 Rear side block 40 Cylinder 42 Cylinder chamber 43, 43A, 43B, 43C Compression chamber 45 Main discharge part (discharge part)
46, 47 Sub-discharge part (discharge part)
48 Proximal portion 49 Remote portion 50 Rotor 51 Rotating shaft 58 Vane 58a Front surface 58b Rear surface 60 Compressor body 70 Cyclone blocks 100, 100 'Electric vane rotary compressor (gas compressor)
G Refrigerant gas (gas)
L1, L2 Extension line R Refrigerating machine oil S Size, area S1, S2, S3, SA1, SA2, SA3 Open area W Rotation direction

Claims (4)

In the gas compressor that houses the compressor body inside the housing,
The compressor main body has a substantially columnar rotor that rotates integrally with a rotation shaft, an inner peripheral surface having a contour shape that surrounds the rotor from the outside of the outer peripheral surface of the rotor, and a predetermined discharge portion is provided. A provided cylinder, a plurality of plate-like vanes provided so as to protrude from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder, and two side blocks that block both ends of the rotor and the cylinder. Prepared,
The vane forms a plurality of compression chambers by partitioning a space formed between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor,
The contour shape of the inner peripheral surface of the cylinder is set so that each of the formed compression chambers performs gas suction, compression, and discharge from the discharge unit only for one cycle during the period of one rotation of the rotor.
One or more sub-discharge sections that discharge gas inside the compression chamber when the pressure of the gas inside the compression chamber reaches the discharge pressure are formed upstream of the discharge section in the rotation direction of the rotor. ,
When the rotor rotates, the extension line of the surface of the vane on the downstream side in the rotation direction of the compression chamber that faces the compression chamber passes through the entire sub-discharge unit. The period up to the passing stage is always in the range between the surface of the vane on the downstream side in the rotational direction facing the compression chamber and the surface of the vane on the upstream side in the rotational direction facing the compression chamber. The total of the opening area of a part or all of the ejection part and the opening area of part or all of the ejection part is larger than the entire opening area of the smaller one of the ejection part and the sub-ejection part. The gas compressor is characterized in that the sub-discharge part is formed at such a position.   In a specific period of the period, between a surface of the vane on the downstream side in the rotation direction in the one compression chamber facing the compression chamber and a surface of the vane on the upstream side in the rotation direction in the compression chamber. 2. The gas compressor according to claim 1, wherein the sub-discharge portion is formed at a position where all of the sub-discharge portion and all of the discharge portions are simultaneously opened. In the gas compressor that houses the compressor body inside the housing,
The compressor main body has a substantially columnar rotor that rotates integrally with a rotation shaft, an inner peripheral surface having a contour shape that surrounds the rotor from the outside of the outer peripheral surface of the rotor, and a predetermined discharge portion is provided. A provided cylinder, a plurality of plate-like vanes provided so as to protrude from the outer peripheral surface of the rotor toward the inner peripheral surface of the cylinder, and two side blocks that block both ends of the rotor and the cylinder. Prepared,
The vane forms a plurality of compression chambers by partitioning a space formed between an inner peripheral surface of the cylinder and an outer peripheral surface of the rotor,
The contour shape of the inner peripheral surface of the cylinder is set so that each of the formed compression chambers performs gas suction, compression, and discharge from the discharge unit only for one cycle during the period of one rotation of the rotor.
One or more sub-discharge sections that discharge gas inside the compression chamber when the pressure of the gas inside the compression chamber reaches the discharge pressure are formed upstream of the discharge section in the rotation direction of the rotor. ,
When the extension line of the surface of the vane on the downstream side in the rotation direction of the compression chamber facing the compression chamber passes through the center of the discharge portion opening due to the rotation of the rotor, the center of the opening of the sub discharge portion is The sub-discharge portion is formed at a position where the vane on the upstream side in the rotation direction in the compression chamber is arranged on the downstream side in the rotation direction with respect to the extension line of the surface facing the compression chamber. Gas compressor.   The proximity portion where the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor are closest is located downstream from the remote portion where the inner peripheral surface of the cylinder and the outer peripheral surface of the rotor are farthest from each other in the rotational direction of the rotor. The gas compressor according to any one of claims 1 to 3, wherein the gas compressor is formed at a position with an angle of 270 [degrees] or more.