JP2018178863A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To reduce loss in a transit route before gas is sucked into a cylinder chamber, in a gas compressor, to improve efficiency of the gas compressor.SOLUTION: A compressor 100 is configured such that outside an inner peripheral surface 41 of a cylinder 40, a penetrating passage 48 penetrating between end surfaces 40a, 40b is provided; in a front side block 20, a suction port 21 opened so as to straddle between the penetrating passage 48 and cylinder chambers 53, 54 is formed; between a partition wall 42 partitioning the cylinder chambers 53, 54 and the penetrating passage 48, and a rear side block 30, a cutout 43b (communication passage) communicating between the penetrating passage 48 and the cylinder chambers 53, 54 is formed; both end surfaces 42a, 42b of the partition wall 42 are inclined toward a direction of guiding refrigerant gas G to the cylinder chambers 53, 54.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a gas compressor.

  There is a vane rotary type as a gas compressor of an air conditioning system (hereinafter referred to as an air conditioning system) mounted on a vehicle or the like. In this vane-rotary type gas compressor, a rotor provided with a plurality of plate-like vanes is disposed inside a cylinder having an inner peripheral surface having an elliptical cross-sectional contour shape, and both cylinder and rotor end surfaces are And two end plates disposed over each other. Then, the cylinder chamber formed by the inner circumferential surface of the cylinder, the outer circumferential surface of the rotor, and the two end plates is divided by the vane into a plurality of compression chambers, and the volume of each compression chamber is changed by the rotation of the rotor. Thus, in the process of increasing the volume of the compression chamber, the gas is sucked into the compression chamber, and in the process of reducing the volume of the compression chamber, the gas trapped in the compression chamber is compressed and discharged.

  Here, in the cylinder, a through passage is formed on the outer side of the inner circumferential surface and between the end surfaces. Further, one of the two end plates corresponding to the suction side of the gas is formed with a suction port opened across the cylinder chamber and the through passage. Furthermore, the through passage and the cylinder chamber are communicated between the partition wall that separates the cylinder chamber and the through passage, and the other end plate of the two end plates (the end plate on the side other than the end plate on the suction side). A communication passage is formed.

  Thus, the gas passing through the suction port formed on the suction side end plate is directly sucked into the cylinder chamber (compression chamber), or the communication passage between the other end plate and the partition wall through the through passage. (See, for example, Patent Document 1).

Japanese Utility Model 1-038312

  By the way, it is desired to reduce the loss in the passage through which the gas having passed through the suction port is sucked into the cylinder chamber (compression chamber) to improve the efficiency of the gas compressor.

  The present invention has been made in view of the above circumstances, and improves the efficiency of the gas compressor by reducing the loss in the passage through which the gas having passed through the suction port passes until it is sucked into the cylinder chamber. To provide a gas compressor capable of

  According to the present invention, there is provided a cylinder having an inner peripheral surface, a rotor disposed inside the area surrounded by the inner peripheral surface, and provided on the rotor, rotating according to the rotation of the rotor. The tip projecting from the outer peripheral surface moves while being in contact with the inner peripheral surface of the cylinder, thereby spanning the plurality of vanes forming the suction stroke, the compression stroke and the discharge stroke, the end face of the cylinder and the end face of the rotor And two end plates disposed, the cylinder having a through passage penetrating between the two end faces of the cylinder on the outer side of the inner circumferential surface, one end plate of the end plates A suction port through which gas passes is formed across the cylinder chamber formed by the inner circumferential surface of the cylinder, the outer circumferential surface of the rotor and the two end plates and the through passage, Cylinder chamber and the above A communication passage is formed between the partition wall of the cylinder separating the passage and the other end plate of the two end plates, and the communication passage between the through passage and the cylinder chamber is formed. At least one end face of the gas compressor is a gas compressor which is inclined in a direction for guiding the gas to the cylinder chamber.

  According to the gas compressor of the present invention, it is possible to improve the efficiency of the gas compressor by further reducing the loss in the passage through which the gas having passed through the suction port is sucked into the cylinder chamber.

It is a longitudinal section showing a compressor which is one embodiment of a gas compressor concerning the present invention. It is sectional drawing which shows only a compression mechanism part among the cross sections which followed the II line in FIG. It is sectional drawing which shows the cross section which followed the II-II line in FIG. FIG. 5 is a cross-sectional view equivalent to FIG. 3 in which a recess is formed in the rear side block, which is an example of a communication passage flowing from the through passage to the compression chamber.

  Hereinafter, embodiments of a gas compressor according to the present invention will be described with reference to the drawings. FIG. 1 is a longitudinal sectional view showing a compressor 100 which is an embodiment of a gas compressor according to the present invention, and FIG. 2 is a sectional view showing only a compression mechanism portion 60 among the sections along line II in FIG. FIG. 3 is a cross-sectional view showing a cross section taken along line II-II in FIG.

<Overview>
As shown in FIGS. 1, 2 and 3, compressor 100 is formed in cylinder 40, through passage 48 through which refrigerant gas G drawn into cylinder chambers 53 and 54 (see FIG. 2.3) passes and the cylinder chamber. The end faces 42a and 42b (see FIG. 3) of the partition wall 42, which is a partition that separates 53 and 54, are inclined.

<Compressor>
The compressor 100 is configured as a part of an air conditioning system (hereinafter simply referred to as an air conditioning system) mounted on a vehicle, and is cooled along with other components such as a condenser, an expansion valve, an evaporator, etc. It is provided on the circulation path of the medium. The compressor 100 compresses a refrigerant gas G (gas) as a gaseous cooling medium taken in from the evaporator of the air conditioning system, and supplies the compressed refrigerant gas G to the condenser of the air conditioning system.

  As shown in FIG. 1, the compressor 100 sucks low-pressure refrigerant gas G into the inside of a housing 10 consisting of a case 11 and a front head 12, compresses the sucked refrigerant gas G to high pressure, and then externally A compression mechanism unit 60 for discharging is provided. Inside the housing 10, a suction chamber 13 and a discharge chamber 14 are formed with the compression mechanism 60 interposed therebetween.

  The suction chamber 13 is in communication with a suction port 12 a formed in the front head 12, and low-pressure refrigerant gas G is introduced from the outside of the compressor 100 through the suction port 12 a. The discharge chamber 14 is in communication with the discharge port 11 a formed in the case 11, and the refrigerant gas G whose pressure is increased by the compression mechanism unit 60 is introduced. The refrigerant gas G led to the discharge chamber 14 flows to the outside of the compressor 100 through the discharge port 11 a.

  The compression mechanism portion 60 includes a rotating shaft 59, a rotor 50, vanes 58, a cylinder 40, and two side blocks 20 and 30. The cylinder 40 has an inner peripheral surface 41 having a contour shape (cross-sectional contour shape) in the cross section shown in FIG. The rotor 50 is formed in a cylindrical shape having an outer peripheral surface having a circular cross-sectional outline shape. The rotor 50 is disposed on the inside surrounded by the inner circumferential surface 41 of the cylinder 40. The rotor 50 rotates in the clockwise direction R in FIG. 1 around the central axis C integrally with the rotation shaft 59 fitted to the central portion thereof.

  The vanes 58 are provided on the rotor 50 so as to be able to project from the outer circumferential surface 51. A plurality of vanes 58 (for example, five at an angle of 72 degrees) are provided at equal angular intervals about the central axis C. Each vane 58 is disposed inside a vane groove formed in the rotor 50. Each vane 58 receives a load directed outward from the outer peripheral surface 51 of the rotor 50 by the centrifugal force generated by the rotation of the rotor 50 and the hydraulic pressure acting on the back pressure chamber 52 formed on the innermost side of the vane groove. , And are provided to be able to project from the outer circumferential surface 51 along the vane grooves.

  One side block 20 (front side block 20) is adjacent to the suction chamber 13 and covers one end surface 40a of the cylinder 40 and one end surface 50a of the rotor 50 so as to cover the respective end surfaces 40a, 50a. Is located in The other side block 30 (rear side block 30) is adjacent to the discharge chamber 14 and covers the respective end surfaces 40b and 50b across the other end surface 40b of the cylinder 40 and the other end surface 50b of the rotor 50. It is arranged as.

  Each side block 20.30 is provided with bearings 20a, 30a for rotatably supporting the rotating shaft 59 respectively projecting from the end faces 50a, 50b of the rotor 50. In the rear side block 30, on the side facing the discharge chamber 14, an oil separator 70 for separating the refrigeration oil L from the refrigerant gas G is provided.

  In FIG. 2, the rear side block 30 is disposed on the back side of the cylinder 40 and the rotor 50 and thus is visually recognized as an entity. On the other hand, the front side block 20 is not visible as an entity because it is disposed on the front side of the cylinder 40 and the rotor 50 in FIG. 2, but is denoted by a parenthesized code to indicate that it is present on the front side. ing.

  As described above, the inside of the compression mechanism 60 is formed by the inner peripheral surface 41 of the cylinder 40, the outer peripheral surface 51 of the rotor 50, and the inner side surfaces of both side blocks 20, Chambers 53, 54 are formed. The two cylinder chambers 53 and 54 are formed rotationally symmetrical to each other with respect to the central axis C.

  Each cylinder chamber 53, 54 is divided into a plurality of spaces by vanes 58 projecting from the outer peripheral surface 51 of the rotor 50. That is, the rotor 50 rotates in the clockwise direction R while the tip end 58 a of the protruding vane 58 is pressed against and in contact with the inner circumferential surface 41 of the cylinder 40. Each space partitioned by the vanes 58 is a compression chamber 55 whose volume changes as the rotor 50 rotates in the clockwise direction R.

  The compression chamber 55 forms a suction stroke in which the volume increases to suck the low pressure refrigerant gas G in accordance with the rotation of the rotor 50, and the volume decreases to form a compression stroke in which the refrigerant gas G is compressed to a high pressure. The volume further decreases and approaches zero, forming a discharge stroke for discharging the refrigerant gas G to the outside.

  The inner peripheral surface 41 of the cylinder 40 has a substantially elliptical cross-sectional contour as shown in FIG. This roughly oval shape is the closest portion 41a where the inner circumferential surface 41 of the cylinder 40 and the outer circumferential surface 51 of the rotor 50 are closest, and the inner circumferential surface 41 of the cylinder 40 and the outer circumferential surface 51 of the rotor 50 are the most distant. And a remote unit 41b. Here, the closest portion 41 a is formed, for example, over a certain range of angles, and the inner peripheral surface 41 of the cylinder 40 and the outer peripheral surface 51 of the rotor 50 are substantially in contact with each other.

  As shown in FIG. 2, assuming that a straight line connecting an intermediate position of a certain angular range of the closest portion 41a and the central axis C is the x axis, the farthest portion 41b passes the central axis C and is orthogonal to the x axis It is biased toward the closest portion 41a on the upstream side in the rotational direction R rather than the portion where the y-axis intersects. That is, the farthest portion 41b is formed on the upstream side in the rotational direction R of the rotor 50 such that the compression stroke and the discharge stroke of the compression chamber 55 are longer than the suction stroke.

  Further, the cylinder 40 penetrates between the both end surfaces 40a and 40b of the cylinder 40, as shown in FIG. 3, at the downstream side of the rotation direction R of the closest portion 41a outside the inner circumferential surface 41. A through passage 48 is formed. By forming the through passage 48, a partition wall 42 is formed between the through passage 48 and the cylinder chambers 53, 54, which divides the through passage 48 and the cylinder chambers 53, 54.

  The partition wall 42 is notched at each end to be in contact with each end surface 40a, 40b of the cylinder 40, and these notched portions (cutouts 43a, 43b) correspond to the partition wall 42 and each side block 20. , 30 between the through passage 48 and the cylinder chambers 53, 54. The end faces 42 a and 42 b of the partition wall 42 formed by the notches 43 a and 43 b are inclined in the direction of guiding the refrigerant gas G to the cylinder chambers 53 and 54.

  Further, as shown in FIG. 3, the front side block 20 adjacent to the suction chamber 13 has a suction port which is opened across the cylinder chambers 53 and 54 and the through passage 48 and through which the refrigerant gas G in the suction chamber 13 passes. 21 is formed. Therefore, the low pressure refrigerant gas G in the suction chamber 13 is led to the cylinder chambers 53 and 54 through the respective suction ports 21 or passes through the through passages 48 from the respective suction ports 21 and the notch 43b which is a communicating passage. It is led to the cylinder chamber 53, 54 through it. That is, the refrigerant gas G having passed from the suction chamber 13 through the suction port 21 branches into the through passage 48 and the cylinder chambers 53 and 54 and flows.

  Since the refrigerant gas G needs to be supplied into the compression chamber 55 within a range where the suction stroke of the compression chamber 55 starts, the suction port 21 is adjacent to a certain angular range in which the closest portion 41a is formed. It is formed facing the compression chamber 55 (cylinder chamber 53, 54) in the above-mentioned state.

  The refrigerant gas G branched from the suction port 21 to the through passage 48 flows through the through passage 48 toward the rear side block 30, and flows into the cylinder chambers 53 and 54 through the notch 43b. Part of the refrigerant gas G directly flowing from the suction port 21 to the cylinder chambers 53 and 54 flows into the cylinder chambers 53 and 54 through the notches 43a.

  Here, the direction of inclination of the end faces 42 a and 42 b of the partition wall 42 will be described. The inclination directions of the end faces 42a and 42b are all suitable for guiding the refrigerant gas G to the cylinder chambers 53 and 54, but the through passages 48 and the cylinder chambers 53 and 54 are suitable for the inclination direction. The direction of the inclination differs between the end face 42a on the side of the starting point of the bifurcation and the end face 42b that does not branch and only leads to the cylinder chambers 53 and 54.

  Specifically, the end face 42 a is a starting point from which the flowing refrigerant gas G branches into the through passage 48 and the cylinder chambers 53 and 54, but the refrigerant gas G flows into the cylinder chambers 53 and 54 through the through passage 48. Direct flow into the cylinder chambers 53, 54 is less loss in flow operation. Therefore, the end face 42 a is inclined in a direction that facilitates the flow of the branched refrigerant gas G to the cylinder chambers 53 and 54 compared to the through passage 48. Specifically, the end face 42 a is inclined in a direction suitable for guiding the refrigerant gas G to the cylinder chambers 53, 54 toward the cylinder chambers 53, 54.

  On the other hand, the end face 42b only flows the refrigerant gas G having flowed through the through passage 48 from the suction port 21 into the cylinder chamber 53, 54 in one way without branching or the like, so the flow to the cylinder chamber 53, 54 It is inclined in the direction to reduce the loss in operation. Specifically, the end face 42 b is directed to the through passage 48 so as to spread the cross sectional area of the through passage 48 as it approaches the rear side block 30 to facilitate the flow of the refrigerant gas G toward the cylinder chambers 53 and 54, The refrigerant gas G is inclined in a direction suitable to lead to the cylinder chambers 53 and 54.

  According to the compressor 100 configured as described above, with the rotation of the rotor 50, in the compression chamber 55, the vane 58 on the front side (downstream side) in the rotational direction R dividing the compression chamber 55 is the closest portion From the time it passes 41a, the volume increases and it becomes the suction stroke. At this time, the inside of the compression chamber 55 becomes negative pressure, and the refrigerant gas G in the suction chamber 13 is directly connected to the compression chamber 55 through the suction port 21 or the through passage 48 and the notch 43 b through the suction port 21. Through the air into the compression chamber 55.

  When the vane 58 on the front side in the rotational direction R of the compression chamber 55 passes through the farthest part 41 b and the volume of the compression chamber 55 becomes maximum, the vane 58 on the rear side (upstream side) in the rotational direction R The refrigerant gas G inside the compression chamber 55 is confined by passing the port 21. Then, as the rotation of the rotor 50 progresses, the volume of the compression chamber 55 decreases, and the refrigerant gas G inside is compressed to a high pressure, and finally, the vane 58 on the rear side in the rotational direction R of the compression chamber 55 However, the refrigerant gas G is discharged from the inside of the compression chamber 55 to the discharge chamber 14 via the oil separator 70 before passing through the closest portion 41a on the opposite side.

  Then, in the suction stroke of the compression chamber 55, the compressor 100 makes the refrigerant gas G flowing into the compression chamber 55 through the suction port 21 by the inclination of the end surface 42a of the partition wall 42 (the inclination toward the cylinder chamber 53, 54). , And the flow into the compression chamber 55 more easily than the through passage 48. Therefore, the loss in the path of the refrigerant gas G flowing to the compression chamber 55 can be reduced compared to the case where the end face 42a is not inclined or the end face 42a faces the through passage 48, and the efficiency of the compressor 100 can be reduced. Can be improved.

  Further, the compressor 100 is a refrigerant that has passed through the through passage 48 and the notch 43 b via the suction port 21 due to the inclination (the inclination toward the through passage 48) of the end surface 42 b of the partition wall 42 in the suction stroke of the compression chamber 55. The gas G is made easy to flow into the compression chamber 55 from the through passage 48. Therefore, the loss in the flow path of the refrigerant gas G can be reduced and the efficiency of the compressor 100 can be improved, as compared with the case where the end face 42b is not inclined or faces the compression chamber 55. .

  As described above, according to the compressor 100, the efficiency of the compressor 100 can be improved by reducing the loss in the passage through which the refrigerant gas G having passed through the suction port 21 passes until the cylinder chambers 53 and 54 are sucked. be able to.

  Further, the compressor 100 is formed with the notch 43a that allows the through passage 48 and the compression chamber 55 to communicate with each other at one end of the partition wall 42, as compared with the case where the notch 43a is not formed. The path of the refrigerant gas G flowing into the compression chamber 55 from the suction port 21 can be widened. As a result, it is possible to further reduce the loss in the path through which the refrigerant gas G passes until it is sucked into the cylinder chambers 53 and 54, and to further improve the efficiency of the compressor 100.

  Further, the compressor 100 is formed with a notch 43 b at the other end of the partition wall 42 that allows the through passage 48 and the compression chamber 55 to communicate with each other, compared with the case where the notch 43 b is not formed. The path of the refrigerant gas G flowing into the compression chamber 55 from the through passage 48 can be broadened. As a result, it is possible to further reduce the loss in the path through which the refrigerant gas G passes until it is sucked into the cylinder chambers 53 and 54, and to further improve the efficiency of the compressor 100.

  Further, in the compressor 100 of the present embodiment, the cross-sectional contour shape of the inner peripheral surface 41 of the cylinder 40 is the closest part 41 a closest to the outer peripheral surface 51 of the rotor 50 and the farthest part 41 b farthest from the outer peripheral surface 51. The most remote portion 41b is biased upstream in the rotational direction R of the rotor 50 with respect to the direction (y-axis direction) orthogonal to the closest portion 41a so that the compression stroke and the discharge stroke are longer than the suction stroke. It is formed.

  Thus, by making the compression stroke relatively long, over-compression in the compression chamber 55 can be prevented or suppressed. Here, by forming the notches 43a and 43b in the partition wall 42, the area (pressure receiving area) where the vanes 58 in the compression chamber 55 contact the inner peripheral surface (inner peripheral surface 41 of the cylinder 40) of the partition wall 42 Is reduced by the amount of the notches 43a and 43b, and the pressure (surface pressure) per unit area at which the inner circumferential surface 41 and the tip 58a of the vane 58 contact each other increases.

  However, since the position of the farthest part of the compressor 100 is biased to the suction stroke side, the cross-sectional contour shape of the inner peripheral surface 41 on the suction stroke side is inclined with respect to the arrangement direction (projecting direction) of the vanes 58. The angle gets smaller (the crossing angle gets smaller). Therefore, the normal force (the component of the load at which the vane 58 contacts the inner circumferential surface 41 and orthogonal to the inner circumferential surface 41) received by the inner circumferential surface 41 from the vanes 58 is reduced. As a result, the frictional force between the vanes 58 and the inner circumferential surface 41, which is proportional to the vertical reaction force, is reduced, and an increase in power due to the sliding of the vanes 58 can be prevented or suppressed.

<Modification 1>
In the compressor 100 according to the above-described embodiment, the two end faces 42a and 42b of the partition wall 42 are both inclined, but in the gas compressor according to the present invention, only one end face of this partition wall is inclined. Even in this case, the loss in the gas flow path can be reduced to improve the efficiency of the gas compressor.

  That is, only the end face 42a of the end near the suction port 21 of the partition wall 42 may be inclined toward the compression chamber 55, and in this case as well, the refrigerant gas G passing through the suction port 21 is a cylinder It is possible to improve the efficiency of the compressor 100 by reducing the loss in the path that passes through the chambers 53 and 54 before suction. Further, only the end face 42b of the partition wall 42 on the side far from the suction port 21 may be inclined toward the through passage 48, and also in this case, the refrigerant gas G passing through the through passage 48 from the suction port 21 is It is possible to improve the efficiency of the compressor 100 by further reducing the loss in the path which passes by the time it is sucked into the cylinder chambers 53, 54.

<Modification 2>
In the compressor 100 described above, the notches 43a and 43b are formed at both ends of the partition wall 42. However, the notches 43a and 43b may not necessarily be formed at both ends. That is, the notch 43 a may be formed only at the end of the partition wall 42 close to the suction port 21 and the notch 43 b may not be formed at the end remote from the suction port 21. As described above, even if the notch 43a is formed only at the end close to the suction port 21, the refrigerant gas G passing through the suction port 21 passes by the time it is sucked into the cylinder chambers 53 and 54. The losses in the path can be reduced to improve the efficiency of the compressor 100.

  The compressor 100 configured not to form the notch 43 b at the end far from the suction port 21 as described above has a passage through which the refrigerant gas G passing through the through passage 48 flows from the through passage 48 to the compression chamber 55 Need to be. Therefore, in the case where the notch 43b is not formed in the partition wall 42 as described above, the rear side block 30 may be provided with a communication passage flowing from the through passage 48 to the compression chamber 55.

  FIG. 4 is a cross-sectional view equivalent to FIG. 3 in which a recess 31, which is an example of a communication passage flowing from the through passage 48 to the compression chamber 55, is formed in the rear side block 30. As shown in FIG. 4, the compression mechanism portion 60 may have a recess 31 recessed across the through passage 48 and the compression chamber 55 with the partition wall 42 of the rear side block 30 interposed therebetween. The concave portion 31 of the rear side block 30 formed in this manner serves as a communication passage that allows the through passage 48 and the compression chamber 55 to communicate with each other. Therefore, even if the notch 43 b is not formed, the refrigerant gas G that has passed through the through passage 48 can flow through the concave portion 31 of the rear side block 30 into the compression chamber 55.

  Of course, even in the configuration shown in FIG. 4 in which the recess 31 is formed in the rear side block 30, the end face 42b of the partition wall 42 may be inclined toward the through passage 48, and the refrigerant passing through the through passage 48 The efficiency of the compressor 100 can be improved by reducing the loss in the passage through which the gas G is drawn into the cylinder chambers 53 and 54.

  Further, the notch 43 b may be formed only at the end of the partition wall 42 on the side far from the suction port 21, and the notch 43 a may not be formed at the end near the suction port 21. Thus, even if the notch 43b is formed only at the end far from the suction port 21, the refrigerant gas G having passed through the through passage 48 passing through the suction port 21 is sucked into the cylinder chamber 53, 54. The efficiency of the compressor 100 can be improved by reducing the losses in the path through which it passes.

  The end face 42a of the end on the side where the notch 43a is not formed may be inclined toward the compression chamber 55 as shown in FIG. 4, and the refrigerant gas G passing through the suction port 21 is a cylinder chamber It is possible to improve the efficiency of the compressor 100 by reducing the loss in the path that passes through to 53, 54 by suction.

  In the gas compressor according to the present invention, both ends of the partition wall 42 may not form the notches 43a and 43b, and as described above, at least one end surface 42a or 42b of the partition wall 42 is inclined. It should be done.

Reference Signs List 20 front side block 21 suction port 30 rear side block 40 cylinder 41 inner circumferential surface 42 partition wall 42a, 42b end surface 43a, 43b notch 48 through passage 53, 54 cylinder chamber 55 compression chamber 100 compressor (gas compressor)
G refrigerant gas

Claims (4)

A cylinder having an inner circumferential surface,
A rotor which is disposed inside and surrounded by the inner circumferential surface and which rotates about a central axis;
A plurality of suction strokes and a compression stroke and a discharge stroke formed by moving the tip provided from the outer peripheral surface of the rotor in contact with the inner peripheral surface of the cylinder according to the rotation of the rotor. With the vane,
An end face of the cylinder and two end plates disposed across the end face of the rotor;
The cylinder has a through passage penetrating between the two end surfaces of the cylinder outside the inner circumferential surface,
A gas is opened in one end plate of the end plates across the cylinder chamber formed by the inner circumferential surface of the cylinder, the outer circumferential surface of the rotor and the two end plates and the through passage. A suction port is formed to pass through,
Between the partition wall of the cylinder that divides the cylinder chamber and the through passage, and the other end plate of the two end plates, a communication passage that allows the through passage and the cylinder chamber to communicate with each other is formed.
The gas compressor in which at least one end face of the both end faces of the partition wall is inclined in a direction for guiding the gas to the cylinder chamber. At least one of both ends of the partition wall is formed with a notch that allows the through passage and the cylinder chamber to communicate with each other.
The gas compressor according to claim 1, wherein an end face of the partition wall formed by the notches is inclined in a direction for guiding the gas to the cylinder chamber. The inner circumferential surface of the cylinder has a cross-sectional contour shape,
It has the closest portion closest to the outer circumferential surface and the farthest portion farthest from the outer circumferential surface, and the farthest portion has the compression stroke and the discharge stroke longer than the suction stroke. The gas compressor according to claim 2, wherein the gas compressor is formed to be biased upstream in the rotational direction of the rotor.   The gas compressor according to any one of claims 1 to 3, wherein a recessed portion recessed across the through passage and the cylinder chamber is formed across the partition wall of the other end plate. .