JP2013227869A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a gas compressor in which the pulsation is reduced without the use of a diaphragm.SOLUTION: A gas compressor includes a volume expansion mechanism that expands the volume of an ejection chamber 14 in response to such timing that coolant gas G which is ejected from a rear side block 30 of a compressor body 60 to the ejection chamber 14 passes through the ejection chamber 14. The volume expansion mechanism is constituted of a recessed space 55 for volume expansion formed in a prescribed angular range θ (θ<120°) around the axial center C of an end surface 54 of a side facing the rear side block 30 of a rotor 50; and two vent holes 38a, 38b that communicate the recessed space 55 and the ejection chamber 14 which are formed on a position or in a range of the rear side block 30, with each other, in response to such timing that coolant gas G ejected from the compressor body 60 passes through the ejection chamber 14.

Description

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

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

  In this gas compressor, a compressor main body that is driven to rotate and compresses the gas is accommodated in the housing, and high-pressure gas is intermittently discharged from the compressor main body and the gas passes through the housing. A discharge chamber is formed by a housing and a compressor body, and high-pressure gas is discharged from the discharge chamber to the outside of the housing.

  However, this gas compressor has a problem that pulsation occurs inside the discharge chamber as a result of intermittent discharge of high-pressure gas from the compressor body, and this pulsation becomes abnormal.

  Therefore, a technique has been proposed in which a throttle is provided in a discharge passage that leads from the compressor body to the discharge chamber to reduce pulsation and reduce the generation of abnormal noise (Patent Document 1).

Japanese Patent Laid-Open No. 7-12072

  However, the technique disclosed in the above-mentioned prior art document increases the flow resistance of the discharge gas due to the restriction, and there is a concern that the performance as a gas compressor is deteriorated.

  This invention is made | formed in view of the said situation, Comprising: It aims at providing the gas compressor which can reduce a pulsation without using an aperture_diaphragm | restriction.

  In the gas compressor according to the present invention, the volume expansion mechanism expands the volume of the discharge chamber corresponding to the timing at which the gas discharged from the compressor body passes through the discharge chamber, thereby causing pulsation without using a restriction. It is to reduce.

  That is, the gas compressor according to the present invention includes a compressor main body that intermittently discharges a high-pressure gas, and the compressor main body accommodated therein, and the high-pressure gas discharged from the compressor main body therein. A volume expansion mechanism that expands the volume of the discharge chamber in response to the timing at which the gas discharged from the compressor body passes through the discharge chamber. It is characterized by having.

  According to the gas compressor of the present invention, pulsation can be reduced without using a throttle.

It is a perspective view showing the appearance of the vane rotary compressor which is one embodiment of the gas compressor concerning the present invention. It is a disassembled perspective view of the vane rotary compressor shown in FIG. It is a longitudinal cross-sectional view which shows the inside of the vane rotary compressor shown in FIG. It is a figure which shows the cross section along the AA in FIG. It is a perspective view which shows the state which exposed the end surface of the rotor except the rear side block among the compressor main bodies. It is a perspective view which shows the state which attached the rear side block to the compressor main body shown in FIG. It is a figure (the 1) which shows a section which meets a BB line in Drawing 6, (a) is a state before a crevice space reaches the 2nd vent, and (b) is a crevice space is the 2nd. A state in which only the vent hole is communicated and (c) represents a state in which the recessed space communicates with the second vent hole and the first vent hole. FIGS. 7A and 7B are views (No. 2) showing a cross section taken along line BB in FIG. 6, in which FIG. 6A shows a state in which the recessed space communicates only with the first ventilation hole, and FIG. Each represents a state of passing through the pores.

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

  A vane rotary compressor 100 (hereinafter simply referred to as a compressor 100), which is an embodiment of a gas compressor according to the present invention, is an air having an evaporator, a gas compressor, a condenser, and an expansion valve installed in an automobile or the like. Used as a gas compressor in harmony systems. This air conditioning system constitutes a refrigeration cycle by circulating a refrigerant gas G (gas).

  The compressor 100 accommodates a compressor body 60 (see FIG. 2) that compresses the refrigerant gas G (gas) at a high temperature and a high pressure inside the housing 10 shown in FIG.

  The housing 10 includes a substantially cylindrical main body case 11 with one end closed, and a front cover 12 that closes an opening at the other end of the main body case 11. 12 is fastened and fixed by four bolts 18 inserted along a direction in which a rotating shaft 51 described later extends from the front cover 12 side.

  Then, in a state where the main body case 11 and the front cover 12 are fastened by the bolts 18, a space for completely accommodating the compressor main body 60 is formed inside the main body case 11 and the front cover 12. Yes.

  In a state where the compressor main body 60 is accommodated in a space formed inside the housing 10, the compressor main body 60 is sandwiched between the main body case 11 and the front cover 12 along the direction in which the rotary shaft 51 extends. It is fixed to the housing 10.

  At this time, in order to prevent the compressor body 60 from rotating around the rotation shaft 51 with respect to the housing 10, two rotation prevention pins 17 and 17 are inserted into the body case 11 and the compressor body 60, Two detent pins 17 and 17 are inserted into the front cover 12 and the compressor body 60.

  As described above, since the compressor body 60 is sandwiched between the main body case 11 and the front cover 12 along the direction in which the rotation shaft 51 extends, a slight gap is formed between the main body case 11 and the front cover 12. However, in order to prevent the refrigerant gas G and the like from leaking from the gap, an O-ring 19 that hermetically seals the inside and outside of the housing 10 is disposed in the gap.

  As shown in FIGS. 2 and 3, the front cover 12 has an intake 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 outside of the housing 10. Is formed.

  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 compressor main body 60 accommodated in the housing 10 includes a rotary shaft 51 that is rotatable around an axis C, a substantially cylindrical rotor 50 that rotates integrally with the rotary shaft 51, and the rotor 50. A cylinder 40 having a contoured inner peripheral surface 41 surrounding the outer peripheral surface 52 from the outside, and three plate-like members 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. A vane 58 and two side blocks (the front side block 20 and the rear side block 30) that close both end surfaces of the rotor 50 and the cylinder 40 are provided.

  Here, the rotating shaft 51 is rotatably supported around the axis C by a bearing 12b formed on the front cover 12 and bearings 27 and 37 respectively formed on the side blocks 20 and 30 of the compressor body 60. In addition, a portion of the rotating shaft 51 that protrudes from the front cover 12 to the outside is provided with a pulley, a gear, and the like, and the pulley, the gear, and the like are rotated by receiving transmission of power from the engine of the vehicle.

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

  Of the two spaces partitioned inside the housing 10, the space on the left side of FIG. 3 sandwiching the compressor body 60 is a suction chamber 13 in a low-pressure atmosphere into which low-pressure refrigerant gas G is introduced from the evaporator through the suction port 12 a. The space on the right side of FIG. 3 across the compressor body 60 is a high-pressure atmosphere discharge chamber 14 in which high-pressure refrigerant gas G is discharged to the condenser through the discharge port 11a.

  Therefore, the front side block 20 faces the suction chamber 13 and the rear side block 30 faces the discharge chamber 14.

  As shown in FIG. 4, the compressor main body 60 has a substantially C-shaped single unit 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 inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 52 of the rotor 50 are close to each other in one range (angle 360 [degrees]) around the axis C of the rotating shaft 51. The contour shape of the inner peripheral surface 41 of the cylinder 40 is set, whereby 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. 4), an angle of 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 52 of the rotor 50 and the inner peripheral surface 41 of the cylinder 40 gradually increases from the remote portion 49 to the proximity portion 48 along the rotation 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 the three vanes 58 are installed around the rotation shaft 51 at equal angular intervals of 120 [degrees], three 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, four compressions are performed during many periods during the rotation of the rotor 50. There is a period in which the three 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 by the vane 58 gradually decreases along the rotation direction W from the remote portion 49 to the proximity portion 48.

  A suction chamber formed in the front side block 20 in a portion of the cylinder chamber 42 on the most upstream side in the rotation direction W of the rotor 50 (a portion on the downstream side of the proximity portion 48 along the rotation direction W). A suction hole 23 leading to 13 faces.

  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 sucks the refrigerant gas G into the compression chamber 43 through the suction hole 23, compresses the refrigerant gas G inside the compression chamber 43, and from the inside of the compression chamber 43 during one rotation of the rotor 50. The refrigerant gas G is discharged to the discharge parts 45 and 46 only for one cycle.

  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 discharge chamber 14 through the formed discharge path 38 and is a main discharge portion.

  The downstream discharge unit 45, which is the main discharge unit, discharges the refrigerant gas G compressed in the compression chamber 43 when the pressure in the compression chamber 43 reaches the discharge pressure while the compression chamber 43 passes. Part.

  On the other hand, 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, is located in the rear side block 30. It merges with the discharge path 38 through the formed discharge path 39 and communicates with the discharge chamber 14 and is a secondary discharge section.

  The upstream discharge section 46, which is a secondary discharge section, over-compresses (discharges) in the compression chamber 43 when the compression chamber 43 reaches the discharge pressure at the previous stage desired by the downstream discharge section 45. The pressure in the compression chamber 43 reaches the discharge pressure during the period in which the compression chamber 43 faces the discharge portion 46. When the refrigerant gas G inside the compression chamber 43 is discharged and the pressure inside the compression chamber 43 does not reach the discharge pressure, the refrigerant gas G inside the compression chamber 43 is not discharged.

  The discharge chamber 14 is formed with two flat ribs 16a and 16b extending in parallel with the rotation shaft 51. The discharge chamber 14 is divided into three regions 14a, 14b and 14c by the two ribs 16a and 16b. It has been.

  Of these three regions 14 a, 14 b and 14 c, the first region 14 a disposed on the uppermost side in FIG. 3 is a region where the high-pressure refrigerant gas G is directly discharged through the discharge path 38.

  The second region 14b disposed in the middle of the three regions 14a, 14b, and 14c is a region that directly communicates with the discharge port 11a, and is a region into which the refrigerant gas G that is discharged into the first region 14a flows. .

  Of the three regions 14a, 14b, and 14c, the third region 14c disposed on the lowermost side is a region in which the refrigerating machine oil R separated from the refrigerant gas G is stored.

  While the refrigerant gas G discharged to the first region 14a travels toward the discharge port 11a, the refrigerant gas G contacts the ribs 16a and 16b, the outer surface of the rear side block 30, the inner surface of the main body case 11, and the like. By contact, the refrigerating machine oil R mixed and discharged with the refrigerant gas G is separated from the refrigerant gas G, and the refrigerating machine oil R is stored in the third region 14c serving as an oil storage part mainly by its own weight.

  On the other hand, the refrigerant gas G from which the refrigerating machine oil R is separated is sent from the second region 14b to the condenser through the discharge port 11a.

  The refrigerating machine oil R stored in the third region 14c of the discharge chamber 14 has an oil passage 34a formed in the rear side block 30 and a back pressure supply recess formed in the rear side block 30 due to the high pressure atmosphere in the discharge chamber 14. The oil passages 34 a and 34 b formed in the rear side block 30, the oil passage 44 formed in the cylinder 40, the oil passage 24 formed in the front side block 20, and the front side block 20. Are 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, respectively, and become the back pressure that 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 part and a cooling function are also exerted in a contact part between the parts and a contact part 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 refrigerant gas in the compression chamber 43 In order to be mixed with G, the refrigerating machine oil R is separated from the refrigerant gas G inside the discharge chamber 14.

  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.

  Here, the compressor 100 of the present embodiment expands the volume of the discharge chamber 14 in accordance with the timing at which the refrigerant gas G discharged from the rear side block 30 of the compressor body 60 to the discharge chamber 14 passes through the discharge chamber 14. A volume expansion mechanism is provided.

  Specifically, as shown in FIGS. 5 and 6, the volume expanding mechanism is configured to have a predetermined angular range θ (θ <120 [degrees] around the axis C of the end surface 54 of the rotor 50 facing the rear side block 30. ] Formed in the position or range of the rear side block 30 corresponding to the timing when the refrigerant gas G discharged from the compressor body 60 passes through the discharge chamber 14. The two vent holes 38a and 38b are formed through the recess space 55 and the discharge chamber 14.

  One of the two vent holes 38a and 38b is located at an angular position downstream of the rotational direction W around the axis C of the rotor 50 in the angular range θ of the end surface 54 of the rotor 50 in which the recessed space 55 is formed. The first vent hole 38a is formed correspondingly, and the other is a first vent hole 38a formed corresponding to the angular position on the upstream side in the rotational direction W around the axis C of the rotor 50. Is a second vent hole 38b formed separately.

  That is, in the stage before the high-pressure refrigerant gas G is discharged from the discharge portion 45 to the discharge chamber 14 through the discharge passage 38, as shown in FIG. 7A, the recessed space 55 formed in the end face 54 of the rotor 50. Is closed by the rear side block 30 and does not communicate with the discharge chamber 14.

  Therefore, the volume of the discharge chamber 14, which is a space from which the high-pressure refrigerant gas G is discharged from the compressor main body 60, is the volume of only the discharge chamber 14 shown in FIG.

  Thereafter, when the rotation of the rotor 50 proceeds to a position where the high-pressure refrigerant gas G starts to be discharged from the discharge portion 45 to the discharge chamber 14 through the discharge path 38, as shown in FIG. A downstream portion 55a of the formed recessed space 55 communicates with the second ventilation hole 38b of the rear side block 30, and the recessed space 55 and the discharge chamber 14 communicate with each other through the second ventilation hole 38b.

  Therefore, the high-pressure refrigerant gas G discharged from the compressor body 60 into the discharge chamber 14 also flows into the recessed space 55 communicating with the discharge chamber 14, and the volume of the discharge chamber 14 is substantially enlarged by the volume of the recessed space 55. It will be done.

  When the rotation of the rotor 50 further proceeds, as shown in FIG. 7C, the recessed space 55 formed in the end face 54 of the rotor 50 is not only the second ventilation hole 38b of the rear side block 30, but also the first passage. The recess space 55 and the discharge chamber 14 communicate with each other through the first air hole 38a and the second air hole 38b, and the volume of the discharge chamber 14 is substantially equal to the volume of the recess space 55. The enlarged state continues.

  When the rotation of the rotor 50 further proceeds and the flow rate of the refrigerant gas G discharged from the compression chamber 43 to the discharge chamber 14 decreases, the recessed space 55 formed in the end face 54 of the rotor 50 as shown in FIG. Is not communicated with the second ventilation hole 38b of the rear side block 30, and is communicated only with the first ventilation hole 38a.

  Even at this stage, the volume of the discharge chamber 14 is substantially enlarged by the volume of the recessed space 55.

  When the rotation of the rotor 50 further proceeds and the flow rate of the refrigerant gas G discharged from the compression chamber 43 to the discharge chamber 14 becomes extremely small, a recess formed in the end face 54 of the rotor 50 as shown in FIG. The space 55 is blocked by the rear side block 30 and does not communicate with the discharge chamber 14. Therefore, the volume of the discharge chamber 14 is only the volume of the discharge chamber 14.

  According to the compressor 100 of the present embodiment configured as described above, when the high-pressure refrigerant gas G discharged from the compressor body 60 passes through the discharge chamber 14, the discharge is performed during one rotation of the rotary shaft 51. Occurs three times intermittently.

  In the conventional gas compressor, pulsation occurs according to the discharge timing of the refrigerant gas G, but the compressor 100 according to the present embodiment has a discharge chamber according to the passage timing of the refrigerant gas G by the above-described volume expansion mechanism. Since the volume of 14 is substantially enlarged, pulsation can be suppressed without using a throttle mechanism.

  Further, the compressor 100 of the present embodiment has vent holes 38a and 38b formed at the position or range of the rear side block 30 corresponding to the timing when the refrigerant gas G discharged from the compressor body 60 passes through the discharge chamber 14. The volume expansion mechanism communicating with the volume expansion recess space 55 formed on the end surface 54 of the rotor 50 ensures that the refrigerant gas G discharged from the compressor body 60 passes through the discharge chamber 14 with certainty. The volume of the discharge chamber 14 can be easily increased by the volume of the recessed space 55.

  Furthermore, in the compressor 100 of the present embodiment, as the rotor 50 rotates, first, the second vent hole 38b communicates with the recessed space 55 of the rotor 50 (FIG. 7B), and the volume of the discharge chamber 14 is substantially reduced. Then, the first vent hole 38a also communicates with the recessed space 55 of the rotor 50 (FIG. 7C). By the subsequent rotation of the rotor 50, the second ventilation hole 38b does not communicate with the recessed space 55, and only the first ventilation hole 38a communicates with the recessed space 55 (FIG. 8A).

  As a result, inside the recessed space 55, as shown in FIG. 7C, the refrigerant gas G flowing into the recessed space 55 causes a flow from the upstream portion 55b to the downstream portion 55a, Therefore, the refrigerant gas G inside the recessed space 55 can quickly move into the discharge chamber 14.

  The second ventilation hole 38b is preferably formed in a portion facing the first region 14a of the discharge chamber 14, and the first ventilation hole 38a is preferably formed in a portion facing the second region 14b of the discharge chamber 14. .

  The first region 14a and the second region 14b are divided by the rib 16b, but the refrigerant gas G discharged from the compression chamber 43 to the first region 14a is separated from the tip of the rib 16b and the outer surface of the rear side block 30. Flows into the second region 14b through a narrow passage between the two.

  For this reason, the refrigerant gas G flowing from the first region 14a to the second region 14b has resistance in a narrow passage between the tip of the rib 16b and the outer surface of the rear side block 30, and the second ventilation hole 38b By being formed in the portion facing the first region 14a, the refrigerant gas G discharged to the first region 14a is easily guided to the recessed space 55 through the second ventilation hole 38b.

  Similarly, since the first ventilation hole 38a is formed at a portion facing the second region 14b, the refrigerant gas G introduced into the recessed space 55 is less likely to be discharged to the second region 14b with less resistance. .

  Therefore, the introduction of the refrigerant gas G into the recessed space 55 and the discharge of the refrigerant gas G from the recessed space 55 can be performed smoothly.

  The compressor 100 of the present embodiment has two vent holes 38a and 38b as vent holes leading to the recessed space 55, but the gas compressor according to the present invention is not limited to this form. There may be one air hole or three or more air holes.

  The volume expansion mechanism that expands the volume of the discharge chamber 14 is not limited to the above-described form, and the volume of the discharge chamber corresponds to the timing at which the gas discharged from the compressor body passes through the discharge chamber. Any structure or mechanism may be used as long as the structure is enlarged.

  The compressor 100 of the embodiment described above has three vanes 58, but the gas compressor according to the present invention is not limited to this form, and the number of vanes is 2, 4, and 5. 6 and the like can be appropriately selected, and the same operation and effect as the above-described embodiment and the compressor 100 can be obtained also by the gas compressor to which the selected number of vanes are applied.

  In addition, the gas compressor according to the present invention may be a so-called two-stage type in which one cycle of suction, compression, and discharge is performed twice during one rotation of the rotation shaft. The compressor 100 may be a so-called one-stage compressor that performs one cycle of stroke only once during one rotation of the rotary shaft.

14 Discharge chamber 14a 1st area | region 14b 2nd area | region 14c 3rd area | region 16a, 16b Rib 30 Rear side block 38 Discharge path 38a 1st ventilation hole 38b 2nd ventilation hole 50 Rotor 51 Rotating shaft 54 End surface 55 Recessed space 55a Downstream portion 55b Upstream portion 60 Compressor body 100 Vane rotary compressor (gas compressor)
θ Angle range G Refrigerant gas W Rotation direction

Claims (3)

A compressor main body for intermittently discharging high-pressure gas, and a housing in which the compressor main body is housed and a discharge chamber through which high-pressure gas discharged from the compressor main body passes is formed. And
A gas compressor comprising a volume expansion mechanism that expands a volume of the discharge chamber in response to a timing at which the gas discharged from the compressor body passes through the discharge chamber. The compressor body includes a columnar rotor that rotates about an axis, and a side block that closes an end surface of the rotor and faces the discharge chamber,
The volume enlarging mechanism includes a volume expanding recess space formed in a predetermined angular range around the axis of the end surface of the rotor and a timing at which gas discharged from the compressor body passes through the discharge chamber. 2. The gas compressor according to claim 1, further comprising a corresponding vent hole formed at a position or a range of the side block and passing through the recessed space and the discharge chamber.   The vent hole is a first vent hole formed corresponding to an angular position on the downstream side in the rotational direction around the axis of the rotor in the angular range of the rotor in which the recessed space is formed; 3. The gas compression according to claim 2, wherein the second ventilation hole formed corresponding to the angular position on the upstream side in the rotational direction around the axis of the rotor is formed separately. Machine.