JP6510756B2 - Gas compressor - Google Patents

Description

  The present invention relates to a vane rotary gas compressor.

  As shown in Patent Document 1, various gas compressors have been conventionally proposed.

  The vane rotary type gas compressor shown in Patent Document 1 includes a compressor body, a motor unit which is housed in the compressor body and serves as a power source of the compressor unit, and a compressor unit.

  The compressor portion includes a cylinder member having a cylinder chamber, a rotor rotatably disposed in the cylinder chamber, and a plurality of vanes disposed so as to be able to retract from the outer peripheral surface of the rotor. The cylinder chamber is divided into two vanes to form a compression chamber.

  The cylinder member is provided with a suction port and a discharge port that are open to the cylinder chamber. The suction port communicates with a large volume suction chamber via a suction passage formed in the cylinder member. The suction chamber is supplied from the refrigerant suction port from the refrigeration cycle. The discharge port communicates with the discharge chamber having a large volume via a discharge passage formed in the cylinder member. The high pressure refrigerant in the discharge chamber is discharged from the discharge port to the refrigeration cycle.

  The compressor unit performs the suction process, the compression process, and the discharge process by the rotation of the rotor, and repeats this series of processes. In the suction process, the compression chamber is expanded by the rotation of the rotor, and the refrigerant is drawn into the compression chamber from the suction port. In the compression process, the compression chamber gradually shrinks and the refrigerant is compressed. In the discharge step, the compressed refrigerant is discharged from the discharge port. By the way, in the gas compressor of patent document 1, the on-off valve is provided in the discharge port, and it is preventing that the compressed refrigerant | coolant is discharged by less than a desired compression pressure.

JP, 2013-130185, A

  In Patent Document 1, when the gas compressor shifts from drive to stop, it is possible to prevent the high pressure refrigerant gas from flowing back to the compression chamber through the discharge chamber, the discharge passage, and the discharge port by the on-off valve.

  However, since the on-off valve is opened and closed each time the refrigerant gas is discharged from the compression chamber, there is a problem that abnormal noise is generated due to the opening and closing.

  Although it is conceivable to eliminate the on-off valve in order to prevent the generation of abnormal noise due to the on-off valve, the high-pressure refrigerant gas flows backward to the suction chamber via the compression chamber, so the compression unit rotates in reverse. There is a problem that a reverse rotation sound is generated by

  Moreover, in the conventional gas compressor, it is considered to prevent generation of abnormal noise due to opening and closing of the on-off valve by disposing the on-off valve and eliminating the on-off valve. Since the high-pressure refrigerant flows backward from the discharge chamber to the suction chamber through the compression chamber until the pressure in the gas compressor becomes uniform when the engine shifts from drive to stop, generation of reverse rotation noise due to reverse rotation of the compression unit It could not be prevented.

  Therefore, the present invention has been made to solve the above-described problems, and it is an object of the present invention to provide a gas compressor that can prevent the backflow of refrigerant after the compressor is stopped and can prevent the generation of abnormal noise. To aim.

In order to solve the above problems, the present invention includes a housing 2 and a compression unit 3 accommodated in the housing 2, and the housing 2 has a suction port 11 for suctioning refrigerant from a refrigeration cycle; It has a suction chamber 13 into which the refrigerant sucked from the suction port 11 flows, a discharge chamber 17, and a discharge port 19 for sending the refrigerant in the discharge chamber 17 to the refrigeration cycle, and the compression unit 3 has an inner periphery A compression block 10 having a cylinder chamber 25, a rotor 29 rotatably disposed in the cylinder chamber 25, a suction passage 36 for suctioning a refrigerant from the suction chamber 13 to the cylinder chamber 25, and the cylinder chamber 25. has a discharge chamber 34 which refrigerant discharged from the inner flows, and a discharge passage 38 for discharging the refrigerant in the discharge chamber 34 to the discharge chamber 17, the suction passage 3 Wherein the at least one check valve 45,45A in one passage of the discharge passage 38, 45B, 45C, and characterized in that a 45D and.

According to the present invention, by disposing the check valve in at least one of the suction passage and the discharge passage, it is possible to immediately prevent the backflow of the refrigerant after the gas compressor is stopped, so the compression section Reverse rotation can be prevented. That is, since the check valve closes at least one of the suction passage and the discharge passage immediately after the gas compressor stops, it is possible to prevent the reverse rotation of the compression section due to the backflow of the refrigerant.

It is a whole sectional view of a gas compressor. It is the sectional view on the AA line of FIG. (A) It is a principal part expanded sectional view of a gas compressor of a 1st embodiment in which a valve body shows a closed state. (B) It is a principal part expanded sectional view of a gas compressor of a 1st embodiment in which a valve body shows an open state. (A) It is a principal part expanded sectional view of the gas compressor of the modification which a valve body shows a closed state. (B) It is a principal part expanded sectional view of the gas compressor of the modification which a valve body shows an open state. (A) It is a principal part expanded sectional view of a gas compressor of a 2nd embodiment in which a valve body shows a closed state. (B) The valve body enlarged view of 2nd Embodiment which shows a closed state. (A) It is a principal part expanded sectional view of the gas compressor of 2nd Embodiment which shows an open state. (B) The valve body enlarged view of 2nd Embodiment which shows an open state. (A) It is a principal part expanded sectional view of a gas compressor of a 3rd embodiment in which a valve body shows a closed state. (B) It is a principal part expanded sectional view of a gas compressor of a 3rd embodiment in which a valve body shows an open state. The principal part expanded sectional view of the gas compressor of a 4th embodiment in which a valve body shows a closed state.

  Hereinafter, embodiments and modifications of the present invention will be described in detail with reference to FIGS.

First Embodiment
As shown in FIGS. 1 to 3, the gas compressor 1 of the present invention includes a substantially cylindrical housing 2, a compression unit 3 disposed in the housing 2, and a motor unit 4 for transmitting a driving force to the compression unit 3. And an inverter unit 5 that controls the driving of the motor unit 4.

  The housing 2 is composed of a front head 7 and a bottomed cylindrical rear case 9 whose opening is closed by the front head 7.

  The inverter unit 5 is fixed to the front head 7, and a suction port 11 for drawing a refrigerant into the housing 2 from a not-shown refrigeration cycle is formed.

  A suction chamber 13 and a discharge chamber 17 are formed on the inner wall 15 of the rear case 9 so that the compression unit 3 is fixed and the inside of the housing 2 is partitioned. Further, on the bottom side of the rear case 9, a discharge port 19 communicating with the discharge chamber 17 and sending out the refrigerant to a not-shown refrigeration cycle is formed.

  The compression unit 3 is integrated with a compression block 10 having a cylinder chamber 25 on the inner periphery, a rotor 29 rotatably disposed in the cylinder chamber 25, an oil separator 27 fixed to the compression block 10, and the rotor 29. And a drive shaft 31 formed thereon.

  The compression block 10 includes a hollow cylinder block 21 and a pair of side blocks 23 disposed so as to sandwich both ends of the cylinder block 21.

  The cylinder block 21 communicates with a suction passage 36 described later and sucks the refrigerant into the cylinder chamber 25. The first discharge hole 33 discharges the refrigerant from the cylinder chamber 25 and the first discharge hole 33 discharges the refrigerant. A discharge chamber 34 into which the refrigerant flows and a second discharge hole 35 discharging the refrigerant from the discharge chamber 34 are formed.

  The first discharge holes 33 are provided at two positions in the circumferential direction of the cylinder block 21, and the refrigerant discharged from the respective first discharge holes 33 is discharged to the discharge chamber 34.

  The discharge chamber 34 has a larger cross-sectional area than the first discharge holes 33 and the second discharge holes 35, and has an effect as a damper.

  The second discharge hole 35 communicates with a discharge port 43 described later, and discharges the refrigerant flowing from the discharge chamber 34 to the side block discharge passage 44 via the discharge port 43.

  The side block 23 is composed of a front side block 23a disposed on the suction chamber 13 side and a rear side block 23b disposed on the discharge chamber 17 side, and the cylinder block 21 is held by a pair of side blocks 23 The cylinder chamber 25 is formed on the inner periphery of the cylinder block 21.

  The cylindrical rotor 29 rotatably accommodated in the cylinder chamber 25 is provided with vane grooves 30 at equal intervals in the circumferential direction, and the vane grooves 30 accommodate the vanes 28 in a freely retractable manner. The vanes 28 abut on the inner wall of the cylinder chamber 25 and the rotor 29 rotates to compress the refrigerant sucked into the cylinder chamber 25. Further, the rotor 29 is integrally formed with the drive shaft 31.

  One end side of the drive shaft 31 is rotatably supported by the side block 23, a motor unit 4 described later is fixed to the other end side, and the rotor 29 is rotated by rotation of the drive shaft 31.

  The front side block 23 a is formed between the suction hole 37 for suctioning the refrigerant from the suction chamber 13 to the cylinder chamber 25, the front side bearing 39 for rotatably supporting the drive shaft 31, and the suction hole 37 and the cylinder chamber 25. And a side block suction passage 40.

  Further, a passage from the suction hole 37 to the cylinder chamber 25 is formed as a suction passage 36 through which the refrigerant is sucked.

  The rear side block 23b is provided continuously with the rear side bearing 41 rotatably supporting the drive shaft 31, the discharge port 43 discharging the refrigerant flowing from the discharge chamber 34, and the discharge port 43, and the check valve 45 is provided. A side block discharge passage 44 is provided, and a step 46 formed between the discharge port 43 and the side block discharge passage 44 and in contact with the check valve 45 is provided.

  The check valve 45 is in contact with the step 46 to open and close the discharge port 43, a spring 51 urging the discharge port 43 in the direction of the discharge port 43, and a spring receiver 49 supporting the spring 51 at one end. And have. The biasing force of the spring portion 51 can be appropriately changed to a desired biasing force by replacing the spring portion 51.

  The valve main body 47 is formed to have a substantially U-shaped cross section, and the spring receiving portion 49 is formed by the end of the valve main body 47 being erected.

  The oil separator 27 fixed to the rear side block 23b separates the refrigerant flowing in via the side block discharge passage 44 into a gas and an oil for maintaining the lubrication in the housing 2, and a separation portion 53 A communication passage 55 communicating with the side block discharge passage 44 and a spring support portion 56 supporting the other end of the spring portion 51 of the check valve 45 are provided.

  Further, a discharge passage 38 through which the refrigerant is discharged is formed by the side block discharge passage 44 and the communication passage 55.

  The motor unit 4 includes a stator 57 fixed to the inner wall 15 of the rear case 9, and a motor rotor 59 rotatably disposed on the inner periphery of the stator 57 and rotated by magnetic force. As the motor rotor 59 is rotated by the magnetic force, the drive shaft 31 is rotated, and the rotor 29 is rotated to compress the refrigerant in the cylinder chamber 25.

  Next, the operation of the gas compressor 1 will be described.

  FIG. 3A shows the time when the gas compressor 1 is stopped, and FIG. 3B shows the time when the gas compressor 1 is driven.

  When the gas compressor 1 shown in FIG. 3A is stopped, the valve main body 47 is in contact with the step 46 by the biasing force of the spring 51 and closes the discharge port 43.

  When the gas compressor 1 is activated from the state shown in FIG. 3A, the refrigerant is compressed in the cylinder chamber 25 and passes from the first discharge hole 33 to the discharge chamber 34, the second discharge hole 35, and the discharge passage 38. Then, the refrigerant is discharged to the discharge chamber 17. By discharging the refrigerant from the second discharge hole 35, the valve main body 47 is pressed by the pressure obtained by compressing the refrigerant, and the valve main body 47 is separated from the step 46 by the spring portion 51 contracting. Open. That is, the check valve 45 as shown in FIG. 3B is in the open state.

  When the valve body 47 opens the discharge port 43, the compressed refrigerant passes through the side block discharge passage 44 and flows into the separation portion 53 through the communication passage 55 of the oil separator 27. The refrigerant flowing into the separation unit 53 is separated into the refrigerant and the oil, and is discharged to the discharge chamber 17, and the refrigerant is discharged from the discharge chamber 17 to the refrigeration cycle through the discharge port 19.

  When the gas compressor 1 is stopped from the state where the check valve 45 shown in FIG. 3B is opened, the valve main body 47 abuts on the step 46 by the biasing force of the spring 51 and closes the discharge port 43. . That is, the check valve 45 as shown in FIG. 3A is closed.

  According to the present embodiment, when the gas compressor 1 is driven, the check valve 45 can be opened and the refrigerant compressed in the cylinder chamber 25 can be discharged to the discharge chamber 17, and when the gas compressor 1 is stopped The stop valve 45 can immediately close the discharge port 43. That is, since the check valve 45 immediately closes the discharge port 43 immediately after the gas compressor 1 is stopped, the high pressure refrigerant discharged to the discharge chamber 17 flows back through the cylinder chamber 25 to the suction chamber 13 which is at a low pressure. Can be prevented. Further, since the backflow of the refrigerant can be prevented, the reverse rotation of the rotor 29 due to the backflow of the refrigerant can be prevented, and the generation of abnormal noise such as chattering can be prevented.

[Modification]
The modification of the said 1st Embodiment is demonstrated using FIG. Description of the same configuration as that of the first embodiment is omitted.

  The compressor 3 of the gas compressor 1 shown in FIG. 4 is different from the first embodiment in the configuration of the rear side block 23b, the oil separator 27, and the check valve 45A.

  The rear side block 23b of this modification supports one end of the spring portion 51a of the check valve 45A by means of a step 46 formed between the discharge port 43 and the side block discharge passage 44.

  The spring portion 51a has a biasing force in a direction away from the discharge port 43, and the other end of the spring portion 51a is supported by the spring receiving portion 49a of the valve main body 47a.

  Further, the valve main body 47a of the present modified example is formed to have a substantially T-shaped cross section, and a spring receiving portion 49a is formed by protruding near the center of the valve main body 47a.

  The oil separator 27 has a high pressure supply hole 61 communicating the discharge chamber 17 with the side block discharge passage 44 in addition to the oil separator 27 of the first embodiment.

  The high pressure supply hole 61 causes the high pressure refrigerant in the discharge chamber 17 to flow into the side block discharge passage 44, thereby pressing the valve body 47a in the direction in which the spring portion 51a is contracted.

  Next, the operation of the check valve 45A of this modification will be described.

  FIG. 4A shows the time when the gas compressor 1 is stopped, and FIG. 4B shows the time when the gas compressor 1 is driven.

  In the state shown in FIG. 4A, the high pressure supply hole 61 provided in the oil separator 27 causes the high pressure refrigerant from the discharge chamber 17 to flow into the side block discharge passage 44 so that the spring portion 51a is contracted. The valve main body 47a is pressed. The end of the valve main body 47 a pressed by the high-pressure refrigerant contacts the step 46 to close the discharge port 43.

  Further, as shown in FIG. 4B, when the gas compressor 1 is driven, the compressed refrigerant is discharged from the discharge port 43, whereby the high-pressure refrigerant separates the valve main body 47a from the step 46. And the discharge port 43 is opened. At this time, the valve main body 47 a closes the high pressure supply hole 61 to prevent the high pressure refrigerant from flowing into the side block discharge passage 44 from the discharge chamber 17.

  When the gas compressor 1 is stopped from the driving state of the gas compressor 1 shown in FIG. 4B, the high-pressure refrigerant from the discharge chamber 17 presses the valve main body 47a in the direction in which the spring portion 51a contracts, and the valve main body 47a It abuts on the portion 46 and is in the state shown in FIG.

  With the above configuration, the same effect as that of the first embodiment can be obtained.

Second Embodiment
The second embodiment will be described with reference to FIGS. The description of the same configuration as that of the first embodiment and the modification will be omitted.

  The configuration of the rear side block 23b, the oil separator 27, and the check valve 45B in the compression unit 3 of the gas compressor 1 shown in FIGS.

  In the present embodiment, the discharge port 43 of the rear side block 23b and the side block discharge passage 44 are configured to be combined, and the check valve 45B is disposed in the communication passage 55 of the oil separator 27.

  As shown in FIGS. 5B and 6B, in the check valve 45B, the valve seats 52b and 54b are fixed to the communication passage 55, respectively.

  The valve seat 52b is formed to be substantially O-shaped in cross section, and a refrigerant passage 60b is provided on the inner periphery. Further, the valve seat 54b is also formed in a substantially O-shape in cross section, and the refrigerant passage 62b is provided on the inner periphery, and a spring support portion 56b is provided protruding toward the valve seat 52b.

  One end side of the spring portion 51b is supported by the spring support portion 56b, and the other end side of the spring portion 51b is supported by the spring receiving portion 49b of the valve main body 47b.

  Next, the operation of the check valve 45B of the present embodiment will be described.

  5 (a) and 5 (b) show the stop time of the gas compressor 1, and FIGS. 6 (a) and 6 (b) show the drive time of the gas compressor 1. FIG.

  In the state shown in FIGS. 5A and 5B, the valve main body 47b is in contact with the valve seat 52b by the biasing force of the spring portion 51b to close the refrigerant passage 60b.

  Further, in the state shown in FIGS. 6A and 6B, the compressed refrigerant is discharged from the discharge port 43, whereby the high pressure refrigerant presses the valve main body 47b in the direction of separating the valve body 52b from the valve seat 52b. The refrigerant passage 60b of the valve seat 52b is opened.

  In the spring portion 51b of the present embodiment, the valve main body 47b opening the refrigerant passage 60b has an urging force that does not close the refrigerant passage 62b of the valve seat 54b.

  When the gas compressor 1 is stopped from the state where the check valve 45B shown in FIGS. 6 (a) and 6 (b) is open, the valve main body 47b abuts against the valve seat 52b by the biasing force of the spring portion 51b. Block 60b. That is, the check valve 45B as shown in FIGS. 5 (a) and 5 (b) is in a closed state.

  According to the present embodiment, when the gas compressor 1 is driven, the check valve 45B is pressed by the discharged high-pressure refrigerant to open the discharge passage 38, and the refrigerant compressed in the cylinder chamber 25 is discharged via the discharge passage 38. It is possible to discharge to the discharge chamber 17. Further, immediately after the gas compressor 1 is stopped, the high pressure refrigerant discharged to the discharge chamber 17 is at a low pressure via the cylinder chamber 25 because the check valve 45B immediately closes the refrigerant passage 60b by the biasing force of the spring 51b. Backflow to the suction chamber 13 can be prevented. Therefore, reverse rotation of the compression unit due to backflow of the refrigerant can be prevented, and generation of abnormal noise can be prevented.

Third Embodiment
The third embodiment will be described with reference to FIG. The description of the same configuration as the first and second embodiments and the modification will be omitted.

  The configuration of the front side block 23a and the check valve 45C of the compression unit 3 of the gas compressor 1 shown in FIG. 7 is different from those of the first and second embodiments and the modification.

  The front side block 23a of the present embodiment includes a suction hole 37 for sucking the refrigerant from the suction chamber 13 into the cylinder chamber 25, and a side block suction passage 40 provided continuously with the suction hole 37 and in which a check valve 45C is disposed. A step 46c is formed between the suction hole 37 and the side block suction passage 40 and is in contact with the check valve 45C.

  One end of the check valve 45C is supported by the spring receiving portion 49c, and the other end is supported by the valve seat 52c.

  Next, the operation of the check valve 45C of the present embodiment will be described.

  FIG. 7A shows the time when the gas compressor 1 is stopped, and FIG. 7B shows the time when the gas compressor 1 is driven.

  In the state shown in FIG. 7A, the valve main body 47c is in contact with the step 46c by the biasing force of the spring 51c to close the suction hole 37.

  Further, in the state shown in FIG. 7B, in order to suck the refrigerant into the cylinder chamber 25, the pressure of the refrigerant to be sucked presses the valve main body 47c in the direction of separating from the step 46c, and the suction hole 37 is opened.

  When the gas compressor 1 is stopped from the state where the check valve 45C shown in FIG. 7B is opened, the valve main body 47c abuts on the step 46c by the biasing force of the spring 51c to close the suction hole 37. . That is, the check valve 45C as shown in FIG. 7A is closed.

  According to the present embodiment, when the gas compressor 1 is driven, the check valve 45C is pressed by the pressure for sucking the refrigerant into the cylinder chamber 25 to open the suction passage 36, and the refrigerant compressed in the cylinder chamber 25 is discharged. It can be discharged into the chamber 17. Further, when the gas compressor 1 is stopped, the high pressure refrigerant discharged to the discharge chamber 17 passes through the cylinder chamber 25 to a low pressure, because the check valve 45C immediately closes the suction hole 37 by the biasing force of the spring portion 51c. It is possible to prevent backflow to the suction chamber 13 that is. Therefore, reverse rotation of the compression unit due to backflow of the refrigerant can be prevented, and generation of abnormal noise can be prevented.

Fourth Embodiment
The fourth embodiment will be described with reference to FIG. In addition, about the structure similar to the said 1st-3rd embodiment and a modification, description is abbreviate | omitted.

  The compression part 3 of the gas compressor 1 shown in FIG. 8 is provided with a check valve 45D in the suction hole 37 of the front side block 23a.

  The check valve 45D of the present embodiment includes a valve accommodating portion 46d having an opening 48d, a valve main body 47d, a spring receiving portion 49d, and a spring portion 51d.

  The valve accommodating portion 46d communicating with the side block suction passage 40 includes an opening 48d for sucking the refrigerant from the suction chamber 13 and a spring support portion 56d for supporting the other end of the spring portion 51d.

  Next, the operation of the check valve 45D of the present embodiment will be described.

  FIG. 8 shows the time when the gas compressor 1 is stopped.

  In the state shown in FIG. 8, the valve main body 47 d abuts against the opening 48 d of the valve housing portion 46 d by the urging force of the spring portion 51 d, thereby closing the valve housing 47 d and blocking the refrigerant from flowing into the side block suction passage 40. Further, when the gas compressor 1 is driven, in order to suck the refrigerant into the cylinder chamber 25, the pressure of the refrigerant to be sucked presses the valve main body 47d in the direction of separating the valve body 47d from the opening 48d, and the refrigerant is sucked into the side block suction passage 40 Do.

  When the gas compressor 1 is stopped from the state where the check valve 45D is opened, the valve main body 47d abuts on the opening 48d by the biasing force of the spring 51d, and closes the opening 48d. That is, the check valve 45D as shown in FIG. 8 is in a closed state.

  According to the present embodiment, when the gas compressor 1 is driven, the check valve 45D is pressed by the pressure for sucking the refrigerant into the cylinder chamber 25 to open the suction passage 36, and the refrigerant compressed in the cylinder chamber 25 is discharged. It can be discharged into the chamber 17. In addition, when the gas compressor 1 is stopped, the high pressure refrigerant discharged to the discharge chamber 17 passes through the cylinder chamber 25 at a low pressure because the check valve 45D immediately closes the opening 48d by the biasing force of the spring 51d. Backflow to a certain suction chamber 13 can be prevented. Therefore, reverse rotation of the compression unit due to backflow of the refrigerant can be prevented, and generation of abnormal noise can be prevented.

  Of course, the first to fourth embodiments and the modifications described above can be combined appropriately.

DESCRIPTION OF SYMBOLS 1 gas compressor 2 housing 3 compression part 13 suction chamber 17 discharge chamber 21 cylinder block 23 side block 25 cylinder chamber 29 rotor 36 suction passage 38 discharge passage 45, 45A, 45B, 45C, 45D check valve

Claims (2)

A housing (2) and a compression section (3) accommodated in the housing (2);
The housing (2) has a suction port (11) for suctioning the refrigerant from the refrigeration cycle;
There is a suction chamber (13) into which the refrigerant sucked from the suction port (11) flows, a discharge chamber (17), and a discharge port (19) for sending the refrigerant in the discharge chamber (17) to the refrigeration cycle And
The compression unit (3) includes a compression block (10) having a cylinder chamber (25) on the inner periphery, a rotor (29) rotatably disposed in the cylinder chamber (25), and the suction chamber (13). A suction passage (36) for sucking the refrigerant into the cylinder chamber (25), a discharge chamber (34) into which the refrigerant discharged from the cylinder chamber (25) flows, and the inside of the discharge chamber (34). A discharge passage (38) for discharging the refrigerant into the discharge chamber (17);
A check valve (45, 45A, 45B, 45C, 45D) is disposed in at least one of the suction passage (36) and the discharge passage (38),
The compression unit (3) comprises an oil separator (27) fixed to the compression block (10),
The discharge passage (38) is provided across the compression block (10) and the oil separator (27).
The gas compressor (1), wherein the check valve (45, 45A) is disposed at a position of the discharge passage (38) of the compression block (10). A housing (2) and a compression section (3) accommodated in the housing (2);
The housing (2) has a suction port (11) for suctioning the refrigerant from the refrigeration cycle;
There is a suction chamber (13) into which the refrigerant sucked from the suction port (11) flows, a discharge chamber (17), and a discharge port (19) for sending the refrigerant in the discharge chamber (17) to the refrigeration cycle And
The compression unit (3) includes a compression block (10) having a cylinder chamber (25) on the inner periphery, a rotor (29) rotatably disposed in the cylinder chamber (25), and the suction chamber (13). A suction passage (36) for sucking the refrigerant into the cylinder chamber (25), a discharge chamber (34) into which the refrigerant discharged from the cylinder chamber (25) flows, and the inside of the discharge chamber (34). A discharge passage (38) for discharging the refrigerant into the discharge chamber (17);
A check valve (45, 45A, 45B, 45C, 45D) is disposed in at least one of the suction passage (36) and the discharge passage (38),
The compression unit (3) comprises an oil separator (27) fixed to the compression block (10),
The discharge passage (38) is provided across the compression block (10) and the oil separator (27).
The gas compressor (1), wherein the check valve (45B) is disposed at a position of the discharge passage (38) of the oil separator (27).

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