JP2016205203A - Gas compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To efficiently separate an oil component in a compressed gas by a centrifugal separation type oil separator even if a flow speed of the compressed gas is low.SOLUTION: A swirl flow of a compressed refrigerant 13 which flows into an oil separation chamber 7f from a flow-in port 7g of an oil separator 7e is made to collide with a fin 7q of a cylinder member 7k which extends on a route of the swirl flow, and the cylinder member 7k is rotated by a rotation thrust force which is obtained by the fin 7q from the swirl flow. A lubricant 11 is separated from the swirl flow of the compressed refrigerant 13 which has collided with the fin 7q by a centrifugal force, and made to adhere on an internal peripheral wall 7h of the oil separator 7f. Furthermore, the lubricant 11 in the compressed refrigerant 13 which has adhered on a peripheral face 7n of the cylinder member 7k, an internal peripheral edge of a communication hole 7p and an internal peripheral face of the cylinder member 7k is scattered to the outside of the cylinder member 7k by the centrifugal force which is generated by the rotation of the cylinder member 7k, and made to adhere on the internal peripheral wall 7h of the oil separation chamber 7f. The lubricant 11 which has adhered on the internal peripheral wall 7h of the oil separation chamber 7f is made to drip to an oil sump 7d of a compression chamber 7a.SELECTED DRAWING: Figure 3

Description

  The present invention relates to a gas compressor that centrifuges oil from a gas compressed by a compression mechanism by an oil separator.

  For example, in a gas compressor used in a refrigeration cycle, when the sucked refrigerant is compressed by the compression mechanism and discharged into the discharge chamber, the compressed refrigerant is swirled spirally in the oil separator of the discharge chamber, and the refrigerant is generated by centrifugal force. The refrigeration oil inside is separated. The separated refrigeration oil is used as lubricating oil or the like in a rotary bearing of a rotating body (for example, a rotor) of a compression mechanism (for example, Patent Document 1).

JP 2007-323740 A

  In the centrifugal oil separator described above, when the refrigeration load is small and the discharge amount of the compressed refrigerant is small, the flow rate of the refrigerant is low, so that the separation performance of the refrigerating machine oil is lowered due to insufficient centrifugal force. In order to solve this problem, if the discharge hole connecting the compression mechanism and the discharge chamber is made small, when the refrigeration load is large, the pressure loss generated in the discharge hole is increased, and the compression efficiency of the refrigerant is lowered.

  The present invention has been made in view of the above circumstances, and an object of the present invention is to centrifuge oil from a gas compressed by a compression mechanism using an oil separator, even if the flow rate of the compressed gas is low. An object of the present invention is to provide a gas compressor capable of efficiently separating oil in compressed gas by a separator.

In order to achieve the above object, the gas compressor of the present invention comprises:
In the gas compressor for generating a spiral swirl flow in the compressed gas introduced from the compression mechanism and centrifuging the oil in the compressed gas,
An oil separation chamber in which a swirling flow of the compressed gas is generated;
A cylindrical member accommodated in the oil separation chamber so as to be rotatable around a central axis of the swirling flow;
A communication hole that communicates the outside of the cylindrical member exposed to the oil separation chamber and the inside of the cylindrical member that communicates with the discharge chamber from which the compressed gas separated from the oil is discharged;
A fin that protrudes from the circumferential surface of the cylindrical member toward the inner peripheral wall of the oil separation chamber, extends on the path of the swirling flow, and obtains the rotational driving force of the cylindrical member from the swirling flow;
It is characterized by providing.

  According to the present invention, when the compressed gas from the compression mechanism flows into the oil separation chamber to form a spiral swirl flow, the cylindrical member that collided with the fin rotates in the same direction as the compressed gas in the oil separation chamber. To do. Then, the oil component is centrifuged from the compressed gas that spirally swirls around the outside of the cylindrical member and adheres to the inner peripheral wall of the oil separation chamber, and the compressed gas from which the oil component has been separated passes from the outside of the cylindrical member to the inside through the communication hole. Flow into.

  The oil content in the compressed gas swirling in the oil separation chamber adheres to the peripheral surface of the cylindrical member and the inner peripheral edge of the communication hole, or passes through the communication hole and adheres to the inner peripheral surface of the cylindrical member. The adhering oil component is a centrifugal force generated by rotating the cylindrical member by the rotational propulsion force obtained from the compressed gas colliding with the fins, and is scattered from the peripheral surface of the cylindrical member and the inner peripheral surface of the communication hole to the outside of the cylindrical member. Alternatively, it passes through the communication hole and scatters outside the cylindrical member. The scattered oil adheres to the inner peripheral wall of the oil separation chamber.

  Thus, the compressed gas flowing into the oil separation chamber from the compression mechanism becomes a spiral swirl flow outside the cylindrical member to generate centrifugal force, and also rotates the cylindrical member to apply centrifugal force to the cylindrical member. Is generated. For this reason, the amount of compressed gas flowing from the compression mechanism into the oil separation chamber is small, and the flow rate of the compressed gas is slow, so that the centrifugal force generated by the spiral swirling flow generated outside the cylindrical member sufficiently removes oil from the compressed gas. Even if it cannot be separated, it is possible to further separate the oil from the compressed gas by scattering the lubricating oil 11 adhering to the cylindrical member to the outside of the cylindrical member by centrifugal force due to the rotation of the cylindrical member.

  Therefore, when the oil component is centrifuged from the gas compressed by the compression mechanism by the oil separator, the oil component in the compressed gas can be efficiently separated by the centrifugal oil separator even if the flow rate of the compressed gas is low. .

  In addition, the oil component adhering to the inner peripheral wall of the oil separation chamber or the inner peripheral surface of the cylindrical member can be collected in the liquid reservoir by dropping due to its own weight.

It is a front sectional view showing a general gas compressor. It is explanatory drawing which shows schematic structure of the common oil separator used with the gas compressor of FIG. It is explanatory drawing which shows schematic structure of the oil separator which concerns on one Embodiment of this invention applied to the gas compressor of FIG. It is explanatory drawing which shows schematic structure of the oil separator which concerns on other embodiment of this invention applied to the gas compressor of FIG.

  Hereinafter, embodiments of the present invention will be described with reference to the drawings.

  FIG. 1 is a front sectional view showing a gas compressor having a general oil separator, and FIG. 2 is an explanatory view showing a state where refrigeration oil in a compressed refrigerant is centrifuged in the oil separator of FIG. A gas compressor 1 shown in FIG. 1 compresses a refrigerant (corresponding to gas in claims) by driving a rotary compression mechanism 3 with an electric motor 5.

  The gas compressor 1 includes a compression mechanism 3 and an electric motor 5, a housing 7 in which these are accommodated, and a controller 15 that controls the driving of the electric motor 5.

  The compression mechanism 3 includes a pair of side blocks 3a and 3b, a cylinder block 3c sandwiched between them, and a columnar rotor 3e accommodated in an elliptical cylinder chamber 3d formed inside the cylinder block 3c. doing.

  The rotor 3e is attached to the rotary shaft 5a of the electric motor 5 supported by the bearing portions 3f and 3g of the side blocks 3a and 3b, and is formed in a plurality of vane grooves (not shown) opened on the peripheral surface of the rotor 3e. Are supported by vanes (not shown) so as to be able to protrude from the peripheral surface of the rotor 3e.

  When the rotor 3e is rotated in the cylinder chamber 3d by the electric motor 5, the rotor 3e protrudes and retracts from the vane groove along the inner peripheral surface of each vane cylinder chamber 3d, and the two vanes adjacent to the rotor 3e and the cylinder chamber 3d. The volume of the space composed of and changes.

  Then, while the space volume increases, low-pressure refrigerant is sucked through a suction port (not shown) formed in the side block 3a, and the sucked refrigerant is compressed as the space volume decreases. The compressed high-pressure refrigerant opens a discharge valve provided at a discharge port (not shown) of the cylinder block 3c, and is discharged from a discharge port (not shown) formed in the side block 3b.

  As shown in FIG. 1, the electric motor 5 includes a rotor 5b attached to the rotating shaft 5a and a stator 5c disposed outside the rotor 5b. The stator 5c has teeth (not shown) corresponding to a plurality of poles, and a coil 5d is wound around each tooth. The electric motor 5 rotates the rotor 5b by generating a rotating magnetic field in the stator 5c by applying a voltage in a predetermined pattern to each coil 5d.

  The housing 7 has a cylindrical shape with one end closed. The housing 7 accommodates the compression mechanism 3, and the accommodated compression mechanism 3 exposes the inside of the housing 7 to the closed discharge chamber 7 a on the closed side where the side block 3 b is exposed and the side block 3 a. It is partitioned off from the suction chamber 7b on the opening side. An electric motor 5 is accommodated in the suction chamber 7 b, and the suction chamber 7 b is sealed by a lid portion 9 attached to the opening 7 c of the housing 7.

  The suction chamber 7b described above is a space in which the low-temperature and low-pressure refrigerant compressed by the compression mechanism 3 is sucked from the outside of the gas compressor 1 (for example, the evaporator of the refrigeration cycle) via a suction port (not shown).

  Further, the discharge chamber 7a, which is hermetically partitioned from the suction chamber 7b by the compression mechanism 3, allows the high-temperature and high-pressure refrigerant compressed by the compression mechanism 3 to be discharged to the outside of the gas compressor 1 (for example, via a discharge port not shown). This is the space discharged to the condenser of the refrigeration cycle. A liquid reservoir 7d for storing lubricating oil 11 (also referred to as refrigerating machine oil, corresponding to oil in the claims) is formed at the lower portion of the discharge chamber 7a.

  The lubricating oil 11 in the liquid pool portion 7d is supplied to the bearing portions 3f and 3g of the side blocks 3a and 3b by the pressure of the refrigerant in the discharge chamber 7a, and is used for lubricating the rotating shaft 5a that the bearing portions 3f and 3g support. . The bearing portions 3f and 3g are formed by annular grooves formed on the inner peripheral surface of the through hole through which the rotation shaft 5a of the side blocks 3a and 3b passes.

  The lubricating oil 11 in the liquid reservoir 7d is supplied to the bearing portion 3f of the side block 3a through the passage 3h of the side block 3b, the passage 3i of the cylinder block 3c, and the passage 3j of the side block 3a. The lubricating oil 11 in the liquid reservoir 7d is supplied to the bearing portion 3g of the side block 3b through the passage 3k of the side block 3b.

  The lubricating oil 11 supplied to the bearing portions 3f and 3g of the side blocks 3a and 3b is collected in the liquid reservoir 7d of the discharge chamber 7a through a passage (not shown). A part of the lubricating oil 11 supplied to the bearing portion 3g of the side block 3b is mixed with the high-pressure refrigerant discharged into the discharge chamber 7a through the cylinder chamber 3d and the like.

  Therefore, the discharge chamber 7a is provided with an oil separator 7e that separates the lubricating oil 11 from the high-pressure refrigerant. The lubricating oil 11 separated from the refrigerant by the oil separator 7e is retained in the liquid reservoir 7d below the discharge chamber 7a.

  A general oil separator 7 e of the gas compressor 1 shown in FIG. 1 has a cylindrical and bottomed oil separation chamber 7 f as shown in FIG. 2, and the refrigerant 13 compressed in the compression mechanism 3. Flows into the oil separation chamber 7f through the inlet 7g. The inflow port 7g is formed in the inner peripheral wall 7h of the oil separation chamber 7f and opens toward a direction shifted from the center of the oil separation chamber 7f. A communication hole 7j is formed in the bottom 7i of the oil separation chamber 7f.

  The oil separation chamber 7f accommodates a hollow cylindrical member 7k that is open at both ends. The cylindrical member 7k is disposed concentrically with the inner peripheral wall 7h of the oil separation chamber 7f, and a flange portion 7l at the upper end is attached and fixed to the upper portion of the oil separation chamber 7f. The compressed refrigerant 13 (corresponding to the compressed gas in the claims) that flows into the oil separation chamber 7f through the inlet 7g of the oil separator 7e passes through the gap between the inner peripheral wall 7h of the oil separation chamber 7f and the cylindrical member 7k. It becomes a swirl flow swirling spirally from above to below.

  By this swirling flow, the component of the lubricating oil 11 in the compressed refrigerant 13 is centrifuged in the oil separation chamber 7f and attached to the inner peripheral wall 7h. The adhering lubricating oil 11 flows down to the lower end of the inner peripheral wall 7h due to its own weight, accumulates at the bottom 7i of the oil separation chamber 7f, and drops from the communication hole 7j to the oil reservoir 7d of the compression chamber 7a.

  The swirling flow of the compressed refrigerant 13 that has reached the bottom 7i of the oil separation chamber 7f then flows into the inside of the cylindrical member 7k from the communication hole 7m at the lower end of the cylindrical member 7k, and from the upper end of the cylindrical member 7k to the housing 7 It flows into the discharge chamber 7a.

  In the oil separator 7e having such a general configuration, the refrigeration load in the refrigeration cycle (not shown) to which the compressed refrigerant 13 is supplied from the gas compressor 1 is small, and the compressed refrigerant is transferred from the compression mechanism 3 to the oil separation chamber 7f. When the flow rate of 13 is small, the flow velocity of the swirling flow of the compressed refrigerant 13 in the oil separation chamber 7f is low, and the separation performance of the lubricating oil 11 is lowered due to insufficient centrifugal force.

  Therefore, in the present invention, in order to improve the separation performance of the lubricating oil 11 when the compressed refrigerant 13 is at a low flow rate, the configuration of the oil separator 7e is partially changed. Hereinafter, a schematic configuration of an oil separator in a gas compressor according to an embodiment of the present invention will be described with reference to FIG. In FIG. 3, the same members and portions as those in FIG.

  In the oil separator 7e of the present embodiment shown in FIG. 3, the cylindrical member 7k has a bottomed cylindrical shape with the bottom 7o closed, and the bottom 7o is formed in the oil separation chamber 7f at the bottom 7i of the oil separation chamber 7f. Are supported so as to be rotatable around a rotation center axis X (corresponding to a center axis in claims) of the swirling flow of the compressed refrigerant 13 in FIG.

  Accordingly, the flange portion 7l of the cylindrical member 7k is formed in a size having a slight gap with the inner peripheral wall 7h of the oil separation chamber 7f. The cylindrical member 7k is formed with a plurality of communication holes 7p in place of the communication holes 7m at the lower end shown in FIG.

  Furthermore, a fin 7q projects from the upper surface of the peripheral surface 7n of the cylindrical member 7k toward the inner peripheral wall 7h of the oil separation chamber 7f. The fin 7q extends on the path of the swirling flow of the compressed refrigerant 13 swirling outside the cylindrical member 7k.

  A disc-shaped backflow prevention piece 7r projects from the lowermost communication hole 7p on the peripheral surface 7n of the cylindrical member 7k toward the inner peripheral wall 7h of the oil separation chamber 7f. Between the outer peripheral edge of the backflow prevention piece 7r and the inner peripheral wall 7h of the oil separation chamber 7f, the lubricating oil 11 that has been centrifuged from the compressed refrigerant 13 in the oil separation chamber 7f and adhered to the inner peripheral wall 7h is separated by its own weight. A gap is provided that allows the bottom 7i of the chamber 7f to flow down.

  In the oil separator 7e of the present embodiment configured as described above, the compressed refrigerant 13 that has flowed into the oil separation chamber 7f through the inlet 7g of the oil separator 7e is combined with the inner peripheral wall 7h of the oil separation chamber 7f and the cylinder. When the spiral swirl flow is directed downward from above the gap with the member 7k, the swirl flow collides with the fins 7q of the cylindrical member 7k extending on the swirl flow path.

  Since the fin 7q collided with the swirling flow of the compressed refrigerant 13 obtains a rotational driving force from the swirling flow, the cylindrical member 7k rotates in the same direction as the compressed refrigerant 13 by this rotating driving force.

  Then, the swirling flow of the compressed refrigerant 13 after colliding with the fins 7q separates the lubricating oil 11 in the compressed refrigerant 13 by the centrifugal force generated by its own swirling while going downward of the oil separation chamber 7f. The lubricated oil 11 is adhered to the inner peripheral wall 7h of the oil separation chamber 7f.

  In addition, when the compressed refrigerant 13 directed downward in the oil separation chamber 7f reaches the backflow prevention piece 7r, the compressed refrigerant 13 flows from the outside to the inside of the cylindrical member 7k through the communication hole 7p on the peripheral surface 7n of the cylindrical member 7k. The compressed refrigerant 13 that has flowed into the inside of the cylindrical member 7k flows into the discharge chamber 7a of the housing 7 from the upper end of the cylindrical member 7k.

  Note that when the compressed refrigerant 13 is swirled and flows through the oil separation chamber 7f from the upper side to the lower side, the lubricating oil 11 in the compressed refrigerant 13 is placed on the peripheral surface 7n of the cylindrical member 7k and the inner peripheral edge of the communication hole 7p. Adhere to. The adhering lubricating oil 11 is scattered to the outside of the cylindrical member 7k from the peripheral surface 7n and the inner peripheral edge of the communication hole 7p by the centrifugal force generated in the rotating cylindrical member 7k.

  Part of the lubricating oil 11 passes through the communication hole 7p, flows into the cylindrical member 7k, and adheres to the inner peripheral surface of the cylindrical member 7k. The lubricating oil 11 also passes through the communication hole 7p by the centrifugal force generated by the rotation of the cylindrical member 7k and is scattered outside the cylindrical member 7k. The scattered lubricating oil 11 adheres to the inner peripheral wall 7h of the oil separation chamber 7f.

  Here, the total flow path cross-sectional area of the plurality of communication holes 7p formed on the peripheral surface 7n of the cylindrical member 7k is set so that the maximum flow rate of the compressed refrigerant 13 discharged from the compression mechanism 3 to the discharge chamber 7a can pass through. ing. Further, the communication hole 7p formed at the lowermost portion of the cylindrical member 7k is disposed immediately above the closed bottom portion 7o. Therefore, the lubricating oil 11 centrifuged from the compressed refrigerant 13 inside the cylindrical member 7k is discharged outside the cylindrical member 7k through the communication hole 7p without staying inside the cylindrical member 7k.

  If there is no problem in operation, the communication hole 7p formed at the lowermost position of the cylindrical member 7k may be disposed at an upper position spaced from the closed bottom portion 7o.

  Thus, the lubricating oil 11 separated from the compressed refrigerant 13 by the centrifugal force generated in the compressed refrigerant 13 outside the cylindrical member 7k, the inner peripheral edge of the peripheral surface 7n of the cylindrical member 7k and the communication hole 7p, or the cylinder Any lubricating oil 11 that adheres to the inner peripheral surface of the member 7k and scatters outside the cylindrical member 7k due to the centrifugal force generated by the rotation of the cylindrical member 7k adheres to the inner peripheral wall 7h of the oil separation chamber 7f.

  The lubricating oil 11 adhering to the inner peripheral wall 7h flows down to the lower end of the inner peripheral wall 7h due to its own weight through the clearance between the backflow preventing piece 7r and the inner peripheral wall 7h, accumulates at the bottom 7i of the oil separation chamber 7f, and is compressed from the communication hole 7j. It is dripped at the oil reservoir 7d of the chamber 7a.

  At this time, since the liquid level of the lubricating oil 11 accumulated in the bottom 7i of the oil separation chamber 7f is covered with the backflow prevention piece 7r, it becomes a swirling flow outside the cylindrical member 7k and becomes a compressed refrigerant directed toward the bottom 7i of the oil separation chamber 7f. 13 is prevented from flowing into the inside of the cylindrical member 7k from the outside through the communication hole 7p together with the compressed refrigerant 13 by being wound up above the backflow preventing piece 7r.

  As described above, in the oil separator 7e of the gas compressor 1 of the present embodiment, the compressed refrigerant 13 flowing into the oil separation chamber 7f from the compression mechanism 3 becomes a spiral swirl flow outside the cylindrical member 7k, and the centrifugal force. In addition, the cylindrical member 7k is rotated to generate a centrifugal force on the cylindrical member 7k. For this reason, the amount of the compressed refrigerant 13 flowing from the compression mechanism 3 into the oil separation chamber 7f is small, and the flow rate of the compressed refrigerant 13 is slow, so that the compressed refrigerant is compressed by the centrifugal force generated by the spiral swirling flow generated outside the cylindrical member 7k. Even if the lubricating oil 11 cannot be sufficiently separated from the cylinder 13, the lubricating oil 11 attached to the cylindrical member 7 k is scattered outside the cylindrical member 7 k by the centrifugal force generated by the rotation of the cylindrical member 7 k, and the lubricating oil 11 is compressed from the compressed refrigerant 13. Can be further separated.

  Therefore, when the lubricating oil 11 is centrifuged by the oil separator 7e from the refrigerant 13 compressed by the compression mechanism 3, the centrifugal oil separator 7e lubricates the compressed refrigerant 13 even if the flow rate of the compressed refrigerant 13 is low. The oil 11 can be separated efficiently.

  The backflow prevention piece 7r protruding from the peripheral surface 7n of the cylindrical member 7k toward the inner peripheral wall 7h of the oil separation chamber 7f may be omitted. Moreover, the position where the fin 7q protrudes from the peripheral surface 7n of the cylindrical member 7k may be above or below the communication hole 7p, or may protrude from the peripheral surface 7n at the same height as the communication hole 7p.

  Further, in place of the communication hole 7p on the peripheral surface 7n of the cylindrical member 7k, as shown in FIG. 4, a plurality of communication holes 7p for communicating the outside and the inside of the cylindrical member 7k are formed at the bottom 7o of the cylindrical member 7k. Also good. In this case, instead of bearing the bottom portion 7o of the cylindrical member 7k so as to be rotatable around the rotation center axis X at the bottom portion 7i of the oil separation chamber 7f, a step is formed on the upper portion of the oil separation chamber 7f. It is good also as a structure which bearings the flange part 7l so that rotation around the rotation center axis | shaft X is possible.

  Moreover, although the opening diameter of the communication hole 7p formed in the peripheral surface 7n and the bottom 7o of the cylindrical member 7k may be increased to be singular, as shown in FIGS. 3 and 4, a plurality of small-diameter communication holes 7p are formed. This is advantageous because it is easy to maintain the rigidity of the portion of the cylindrical member 7k that forms the communication hole 7p.

  Furthermore, in the above embodiment, the case where the present invention is applied to the gas compressor 1 having the vane rotary type compression mechanism 3 that rotates the rotor 3e in the cylinder chamber 3d has been described as an example. However, the present invention has a rotary compression mechanism that sucks and compresses gas by rotating a rotating body, such as a scroll compressor that rotates a movable scroll with respect to a fixed scroll to compress gas. Widely applicable to gas compressors.

  Further, in the above embodiment, the electric gas compressor 1 in which the compression mechanism 3 is rotationally driven by the electric motor 5 has been described as an example. However, the present invention can be widely applied to, for example, a gas compressor other than an electric compressor that is mounted on a vehicle and rotationally drives a compression mechanism with the power of an engine.

  INDUSTRIAL APPLICATION This invention can be utilized in the gas compressor which centrifuges an oil component with the oil separator from the gas compressed with the compression mechanism.

DESCRIPTION OF SYMBOLS 1 Gas compressor 3 Compression mechanism 3a, 3b Side block 3c Cylinder block 3d Cylinder chamber 3e, 5b Rotor 5 Electric motor 5a Rotating shaft 5c Stator 5d Coil 7 Housing 7a Discharge chamber 7b Suction chamber 7c Housing opening 7d Oil separation part 7e 7f Oil separation chamber 7g Inlet 7h Oil separation chamber peripheral wall 7i Oil separation chamber bottom 7j Oil separation chamber communication hole 7k Cylindrical member 7l Flange 7p Cylindrical member communication hole 7n Cylindrical member peripheral surface 7o Cylindrical member bottom 7q Fin 7r Backflow prevention piece 9 Lid 11 Lubricating oil (oil content)
13 Compressed refrigerant (compressed gas)
15 Controller X Center axis of rotation (center axis)

Claims (5)

In the gas compressor (1) for generating a spiral swirl flow in the compressed gas (13) introduced from the compression mechanism (3) and centrifuging the oil (11) in the compressed gas (13),
An oil separation chamber (7f) in which a swirling flow of the compressed gas (13) is generated;
A cylindrical member (7k) accommodated in the oil separation chamber (7f) so as to be rotatable around a central axis (X) of the swirling flow;
The cylindrical member (7k) communicating with the outside of the cylindrical member (7k) exposed to the oil separation chamber (7f) and the discharge chamber (7a) into which the compressed gas (13) separated from the oil (11) is discharged. ) Communication hole (7p) communicating with the inside,
Projecting from the peripheral surface (7n) of the cylindrical member (7k) toward the inner peripheral wall (7h) of the oil separation chamber (7f), the cylindrical member extends from the swirling flow to the cylindrical member. A fin (7q) for obtaining a rotational driving force of (7k);
A gas compressor (1) comprising:   The cylindrical member (7k) is formed in a bottomed cylindrical shape with a closed bottom (7o), the communication hole (7p) is formed on the peripheral surface (7n), and the fin (7q) Is disposed above the communication hole (7p) of the peripheral surface (7n), and is directed from the peripheral surface (7n) below the communication hole (7p) toward the inner peripheral wall (7h). The gas compressor (1) according to claim 1, wherein a backflow prevention piece (7r) having an outer shape slightly smaller than the inner peripheral wall (7h) is projected.   The cylindrical member (7k) is formed in a bottomed cylindrical shape with a closed bottom (7o), and the bottom (7o) can be rotated around the central axis (X) by the oil separation chamber (7f). 3. The gas compressor (1) according to claim 1 or 2, characterized in that the gas compressor (1) is supported by the bearing.   The cylindrical member (7k) is formed in a bottomed cylindrical shape with a closed bottom (7o), and the communication hole (7p) is formed on the peripheral surface (7n) immediately above the bottom (7o). The gas compressor (1) according to claim 1, 2 or 3, wherein the gas compressor (1) is provided.   A plurality of the communication holes (7p) are provided, and the total flow path cross-sectional area of the plurality of communication holes (7p) is set so that the compressed gas (13) having the maximum flow rate can pass therethrough. The gas compressor (1) according to claim 1, 2, 3 or 4.

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