JP2004068781A - Gas compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gas compressor which does not generate non-lubrication condition by preventing spillover and reverse flow of lubricating oil. <P>SOLUTION: A solenoid valve 22 opened by electricity carry is provided on an outlet port 21. A relief valve 23 connecting to an outlet chamber 19 projects on a side part of the outlet port 21 to release internal pressure by rise of internal pressure. One end of the splenoid valve is connected to a power source 75 and another end of the same is connected to an electromagnetic coil 34 via a switch 76 controlling operation of the gas compressor 50. When the switch 76 is turned off, a circuit is cut off and an electromagnetic clutch 72 is disengaged. Consequently, power transmission from an engine 70 to a rotating shaft 6 of the gas compressor 50 is cut off and operation thereof stops. The solenoid valve 22 is closed at a same time due to cut off of electricity carry, spillover of cooling medium from the outlet chamber 19 is prevented. <P>COPYRIGHT: (C)2004,JPO

Description

[0001]
TECHNICAL FIELD OF THE INVENTION
The present invention relates to a gas compressor, and more particularly, to a gas compressor that prevents outflow and backflow of lubricating oil and does not generate a non-lubricated state.
[0002]
[Prior art]
Gas compressors are used for indoor air conditioning and refrigeration. FIG. 9 shows an overall simplified configuration diagram of the air conditioning system. Heated air is sent from the cooling target space to the evaporator 60 by the fan 61. The refrigerant gas is vaporized by the heat and sent to the gas compressor 50 through the pipe 58. The air cooled by losing heat in the evaporator 60 is returned to the space to be cooled.
[0003]
The high-pressure refrigerant gas compressed by the gas compressor 50 passes through the discharge pipe 55 and is sent to the condenser 65. In the condenser 65, the refrigerant gas is liquefied by external blowing.
[0004]
The refrigerant gas that has passed through the condenser 65 passes through the pipe 56 and is rapidly reduced in pressure from a high pressure to a low pressure by an expansion valve 67. The reduced pressure refrigerant gas is supplied to the evaporator 60 through the pipe 57.
[0005]
Next, the internal mechanism of the gas compressor 50 will be described. The gas compressor 50 has a compressor main body 1 as shown in FIG. 10, and the compressor main body 1 includes a cylinder 4 inserted between a pair of side blocks 2 and 3, and a rotor 5 is provided in the cylinder 4. Are rotatably arranged.
[0006]
The rotor 5 is integrally provided with a rotating shaft 6 penetrating between the end faces, and the rotating shaft 6 is rotatably fitted in bearing holes 7, 8 provided in both side blocks 2, 3. . The rotation shaft tip side 6a protrudes from the bearing hole 7 and is formed so as to extend through the front head 9.
[0007]
A seal chamber 10 is provided on the outer periphery of the rotation shaft tip side 6a, and lubricating oil is supplied to the seal chamber 10 through a bearing gap G between the bearing hole 7 and the rotation shaft 6.
[0008]
FIG. 11 is a sectional view taken along the line AA in FIG. A vane groove 12 is formed in the outer peripheral surface of the rotor 5 in a radial direction, and a vane 13 is slidably mounted in the vane groove 12. When the rotor 5 rotates, the vane 13 is urged against the inner wall of the cylinder 4 by centrifugal force and hydraulic pressure at the bottom of the vane groove.
[0009]
The interior of the cylinder 4 is partitioned into a plurality of small chambers by a pair of side blocks 2, 3, a rotor 5, and vanes 13, 13,. These small chambers are referred to as compression chambers 14, 14...
[0010]
In such a compressor body 1, when the rotor 5 rotates and the volume of the compression chambers 14, 14,... Changes, the volume change causes the low-pressure refrigerant gas in the suction chamber 16 to be compressed through the suction passage 41. The air is sucked into the chamber 14 and compressed.
[0011]
In addition, around the rotation shaft 6 facing the rotor 5 of the side blocks 2 and 3, saliage grooves 35 and 36 respectively communicating with the bottoms of the vane grooves are provided. The lubricating oil is supplied to the sali grooves 35 and 36 from the oil reservoir 20 through the lubricating oil passages 37 and 38.
[0012]
The refrigerant gas in the suction chamber 16 is supplied from an external evaporator 60 connected to the suction port 15. A check valve 17 is provided between the suction port 15 and the suction chamber 16 to prevent the refrigerant from flowing backward.
[0013]
The discharge chamber 19 is formed by the side block 3 and the case 52. The compressed high-pressure refrigerant gas is discharged to the discharge chamber 19 via the discharge port 27, the discharge valve 28, the oil separator 18, and the like.
[0014]
At this time, the oil separator 18 separates the oil from the high-pressure refrigerant gas, and the separated oil accumulates at the bottom of the discharge chamber 19 to form an oil reservoir 20 for lubricating oil. The high-pressure refrigerant gas from which the oil has been separated passes through the discharge pipe 55 from the discharge port 21 and is sent to the external condenser 65.
[0015]
FIG. 12 is a cross-sectional view of the discharge chamber 19 and a discharge pipe 55 connected thereto, taken along the line BB in FIG. 10. In general, the space of the pipe is often limited, and the discharge pipe 55 rises slightly vertically from the discharge port 21 so as to surround, for example, the gas compressor 50, then bends horizontally, and then hangs down. It is connected to a condenser 65.
[0016]
The shaft power of the external engine 70 causes the pulley 31 to rotate by the belt 74. The pulley 31 is provided with a bearing 32 between the pulley 31 and the front head 9 for smooth rotation. An electromagnetic coil 34 is also mounted for the electromagnetic clutch, and the armature 33 fixed to the right end of the rotating shaft 6a is attracted to or separated from the right end surface of the pulley 31 by excitation thereof, so that the connecting and disconnecting with the rotating shaft 6 is possible. It becomes. When the amateur 33 is attracted to the right end face of the pulley 31, the rotor 5 rotates as the pulley 31 rotates.
[0017]
[Problems to be solved by the invention]
By the way, in the current air conditioning system, the refrigerant gas containing the lubricating oil repeatedly flows out of the gas compressor 50 from the discharge chamber 19 through the discharge port 21 to the outside of the gas compressor 50 due to the change of the outside air temperature at the time of stoppage, and the oil content is reduced. There is a possibility of causing the conversion.
[0018]
The process during this time will be described below. As shown in FIG. 13A, at the end of the normal operation, an oil reservoir 20 exists in the lower part of the discharge chamber 19. The oil reservoir 20 is a lubricating oil, but also contains some liquefied refrigerant gas.
[0019]
Further, when the operation is stopped, a temperature difference may occur in each device such as the evaporator 60, the condenser 65, and the gas compressor 50 due to a difference in outside air temperature in contact with each other and a difference in heat capacity of each part. At this time, if it is assumed that the volume of each device does not change, the pressure decreases because the internal energy of the device having a lower temperature is reduced.
[0020]
Further, when the operation is stopped, a temperature difference may occur due to a difference in the outside air temperature at which each device such as the evaporator 60, the condenser 65, and the gas compressor 50 contacts, and a difference in heat capacity of each part.
[0021]
Specifically, at the time of stoppage when the outside air temperature is low, such as at night or in winter, the refrigerant gas is liquefied, and as shown in FIG. May be rising. If the temperatures of the condenser 65 and the discharge pipe 55 are lower than those of the gas compressor 50 under such conditions, the pressure in the condenser 65 and the discharge pipe 55 is lower.
[0022]
Accordingly, the pressure of the gas compressor 50 becomes relatively high, and a pressure difference occurs. Due to the pressure difference, the lubricating oil containing the liquefied refrigerant gas present in the discharge chamber 19 is pushed out to the discharge pipe 55 as shown in FIG. 13C and flows out of the gas compressor 50.
[0023]
On the other hand, when the outside air temperature rises in the daytime or summertime, the refrigerant gas liquefied in the discharge pipe 55 and the discharge chamber 19 is vaporized, and pressure is applied to the liquid surface of the oil reservoir 20. Further, the volume of the oil reservoir 20 itself is reduced by vaporizing the refrigerant gas liquefied in the lubricating oil. For both of these reasons, the level of the oil pool 20 drops. However, the liquid lubricating oil that has flowed out at a low temperature cannot go up the discharge pipe 55, remains at the bottom of the condenser 65 or the discharge pipe 55, and cannot return to the discharge chamber 19.
[0024]
By repeating this cycle for a long time, the amount of lubricating oil in the discharge chamber 19 decreases. As a result, the interior of the gas compressor 50 is finally brought into a non-lubricated state, and there is a possibility that various parts requiring lubricating oil, such as the cylinder 4, the rotor 5, and the rotating shaft 6, may cause burning.
[0025]
In addition, if the lubricating oil flows out of the gas compressor 50 more than necessary, good heat exchange between the evaporator 60 and the condenser 65 is hindered, leading to a decrease in efficiency.
[0026]
As a countermeasure, the capacity of the discharge chamber 19 may be increased in order to secure a sufficient space so that the gas does not overflow even if the gas is liquefied. However, it is difficult to reduce the size of the gas compressor 50. I will. In addition, there is a method of preventing the lubricating oil containing the liquefied refrigerant gas from flowing out by extending the discharge pipe 55 in front of the discharge port 21 in the vertical direction, but there is a problem with the installation space restriction.
[0027]
The present invention has been made in view of such conventional problems, and has as its object to provide a gas compressor that prevents outflow and backflow of lubricating oil and does not generate a non-lubricated state.
[0028]
[Means for Solving the Problems]
Therefore, the present invention provides a rotating shaft that rotates by external power, a clutch that transmits and disconnects power to the rotating shaft, and at least one compression chamber that compresses refrigerant gas by rotation of the rotating shaft. An oil separating section for separating lubricating oil from the refrigerant gas compressed in the compression chamber, a discharge chamber for storing the lubricating oil separated through the oil separating section, and a refrigerant discharged to the discharge chamber A discharge port for discharging gas to the outside, and a valve for preventing the lubricating oil from flowing out when the rotation shaft is stopped are provided at the discharge port.
[0029]
The valve opens only during operation and closes when operation is stopped. When the operation is stopped, a temperature difference may occur between the gas compressor and each external device communicating therewith due to a change in the external environment or the like. When this phenomenon causes a pressure difference between the gas compressor and each external device, lubricating oil containing refrigerant gas tends to flow out of the gas compressor. However, at this time, since the valve is closed, the outflow of lubricating oil can be prevented.
[0030]
Further, the present invention provides a rotating shaft that rotates by external power, transmission of power to the rotating shaft, a clutch that shuts off, and at least one compression chamber that compresses refrigerant gas by rotation of the rotating shaft. An oil separating section for separating lubricating oil from the refrigerant gas compressed in the compression chamber, a discharge chamber for storing the lubricating oil separated through the oil separating section, and a refrigerant discharged to the discharge chamber A discharge port for discharging gas to the outside, and a discharge pipe for guiding refrigerant gas from the discharge port to an external device, wherein the discharge pipe has a valve for preventing the lubricating oil from flowing out when the rotating shaft is stopped. It is characterized by having been arranged.
[0031]
The valve can also be arranged in the discharge line. In such a case, it is possible to obtain the same effect as the case where the discharge port is provided.
[0032]
Further, the present invention is characterized in that an electromagnetic valve is used as the valve, and the electromagnetic valve is interlocked with the clutch, and the clutch is opened when the clutch is connected and closed when the clutch is disconnected.
[0033]
From this, reliable and efficient control becomes possible.
[0034]
Furthermore, the present invention is characterized in that a fluid-operated valve is used as the valve, and the fluid-operated valve is opened and closed according to the pressure difference between the front and rear spaces partitioned by the fluid-operated valve.
[0035]
Fluid operated valves have a simple structure, are easy to install, and are inexpensive.
[0036]
Further, the present invention is characterized in that the fluid-operated valve is a valve provided with a valve body seated on a valve seat and an urging means for urging the valve body against the valve seat when the operation is stopped. And
[0037]
Furthermore, the present invention is characterized in that a reed valve is provided as the fluid-operated valve.
[0038]
If the reed valve is disposed in the longitudinal direction with respect to the pipe, operation by a slight pressure difference is also possible. For this reason, the valve can be simply configured, which leads to a reduction in material costs.
[0039]
Further, the present invention is characterized in that a relief valve for releasing pressure is provided in a space formed by the valve and the discharge chamber.
[0040]
The provision of the valve increases the airtightness in the discharge chamber when the valve is closed, but the provision of the relief valve prevents an accident when the pressure in the gas compressor rises abnormally.
[0041]
BEST MODE FOR CARRYING OUT THE INVENTION
Hereinafter, a first embodiment of the present invention will be described. FIG. 1 is an overall configuration diagram of a first embodiment of the present invention, and FIG. 2 is a cross-sectional view taken along line CC of FIG. The same elements as those in FIG. 10 are denoted by the same reference numerals and description thereof will be omitted.
[0042]
In FIG. 2, an electromagnetic valve 22 that is opened by energization is disposed at the discharge port 21. A relief valve 23 that communicates with the discharge chamber 19 protrudes from the side of the discharge port 21 and is opened by an abnormal increase in internal pressure.
[0043]
FIG. 3 shows a wiring diagram around the solenoid valve 22. One end of the solenoid valve 22 is connected to the power supply 75, and the other end is connected to the electromagnetic coil 34 via a switch 76 that controls the operation of the gas compressor 50.
[0044]
In this configuration, when the switch 76 is turned on, the wiring is connected and the electromagnetic coil 34 is energized, so that the electromagnetic clutch 72 is in the connected state. Thereby, the power from the engine 70 is transmitted to the rotating shaft 6 of the gas compressor 50, and the operation starts. At this time, since the electromagnetic valve 22 is opened by energization, the refrigerant gas discharged from the discharge port 21 is sent to the condenser 65 through the discharge pipe 55.
[0045]
On the other hand, when the switch 76 is turned off, the wiring is disconnected, and the electromagnetic clutch 72 is disconnected. Therefore, power transmission from the engine 70 to the rotary shaft 6 of the gas compressor 50 is cut off, and the operation stops. At the same time, the solenoid valve 22 is closed due to the cutoff of the power supply, so that the refrigerant gas is prevented from flowing out of the discharge chamber 19.
[0046]
If the electromagnetic clutch 72 and the electromagnetic valve 22 are connected in parallel to the power supply, a failure or disconnection may cause an accident that only one of the electromagnetic clutch 72 and the electromagnetic valve 22 operates.
[0047]
For example, when only the energization of the solenoid valve 22 is stopped during operation, the solenoid valve 22 is closed, but the solenoid clutch 72 is energized, so the gas compressor 50 is in the operating state. However, the refrigerant gas cannot be discharged due to the closing of the electromagnetic valve 22, and an abnormal pressure is generated in the gas compressor 50.
[0048]
When only the energization of the electromagnetic clutch 72 is stopped, the electromagnetic valve 22 is open because it is energized and contains the liquefied refrigerant gas, even though the operation of the gas compressor 50 is stopped. The outflow of lubricating oil cannot be prevented.
[0049]
Assuming the above case, as a preventive measure, the wiring between the electromagnetic clutch 72 and the electromagnetic valve 22 is connected in series with the power supply as shown in FIG.
[0050]
Further, by providing the relief valve 23, even when the electromagnetic clutch 72 or the electromagnetic valve 22 fails, the refrigerant gas, which has been increased in pressure in accordance with the pressure in the discharge chamber 19, is discharged, thereby preventing an accident.
[0051]
Next, a second embodiment of the present invention will be described. FIG. 4 shows an overall configuration diagram of the second embodiment of the present invention. FIG. 5 is a sectional view taken along line DD in FIG. 4, and FIG. 6 is an enlarged sectional view of the valve 25 in FIG. The same elements as those in FIG. 10 are denoted by the same reference numerals and description thereof will be omitted.
[0052]
As shown in FIGS. 4 to 6, the discharge port 21 is provided with a valve 25. The discharge port 21 and the discharge chamber 19 communicate with each other through a fluid inlet 85 having a smaller diameter than the discharge port 21. A step is formed at the lower end of the discharge port 21 due to the diameter difference, and the valve 25 is fixed on the step.
[0053]
As shown in FIG. 6, the valve 25 has a hollow disk-shaped valve chamber bottom 83a, a valve chamber side 83b erected from the inner periphery of the valve chamber bottom 83a, and a valve at the upper end of the valve chamber side 83b. A valve chamber 83 having a chamber upper plate 83c, a spring 82 locked in the valve chamber upper plate 83c and housed in the valve chamber 83, and a valve head 81 disposed at the lower end of the spring 82. It is configured.
[0054]
At this time, the hollow of the valve chamber bottom portion 83a is larger than the fluid inlet 85, and a valve seat 86 is formed on the step of the discharge port 21. Further, between the valve chamber side portion 83b and the discharge port 21, there is a ventilation space generated by the difference in diameter.
[0055]
The valve head 81 includes a cylindrical peripheral wall 81a that covers the lower end of a spring 82, and a flat bottom 81b having a bottom outer edge formed on a flat plate. A conical projection is formed on the inner periphery of the flat bottom 81b. 81c is formed downward. When the valve 25 is closed, the flat bottom portion 81b of the valve head 81 is seated on the valve seat 86, and the conical projection 81c protrudes into the cylinder of the fluid inlet 85 and fits.
[0056]
The space on the discharge chamber 19 side and the space on the discharge pipe 55 side are isolated by the valve 25. A through hole 84 is provided near the fluid inlet 85 side of the valve chamber side portion 83b, and both spaces sandwiching the valve 25 communicate with the through hole 84.
[0057]
As shown in FIG. 6A, the valve head 81 is pressed against the valve seat 86 by the restoring force of the spring 82 and closes the gap between the valve 25 and the fluid inlet 85. When pressure is applied from the inlet 85 side, as shown in FIG. 6B, the spring 82 contracts due to the force, so that the valve head 81 moves upward. When the flat bottom portion 81b of the valve head 81 is located above the lower end of the through hole 84, the through hole 84 is opened, and the space on the discharge chamber 19 side and the space on the discharge pipe 55 side communicate with each other.
[0058]
The spring 82 has a greater restoring force than a pressure difference caused by a temperature difference between the gas compressor 50, the evaporator 60, and the condenser 65 at the time of stoppage. Those having a smaller restoring force than the discharge pressure are used.
[0059]
In such a configuration, when the gas compressor 50 is stopped, a differential pressure due to a temperature difference is generated in each part of the gas compressor 50, the evaporator 60, and the condenser 65, and the lubricating oil including the liquefied refrigerant gas in the discharge chamber 19 is discharged. Even if it tries to flow out to the discharge pipe 55, the spring 82 does not contract at the outflow pressure, and the valve head 81 cannot be pushed up. Therefore, it is possible to prevent the lubricating oil containing the refrigerant gas from flowing out.
[0060]
On the other hand, during operation of the gas compressor 50, the pressure of the refrigerant gas discharged from the gas compressor 50 pushes up the valve head 81 to open the through hole 84 in order to contract the spring 82, and the refrigerant gas passes through the discharge pipe 55. To the condenser 65. Therefore, the flow of the refrigerant gas discharged during operation is not hindered, and it is possible to prevent only the outflow of the lubricating oil containing the liquefied refrigerant gas at the time of stop.
[0061]
Next, a third embodiment of the present invention will be described. FIG. 7 shows an enlarged configuration diagram of the valve according to the third embodiment of the present invention. FIG. 8 is a sectional view taken along the line EE in FIG. The third embodiment of the present invention is a fluid-operated valve similar to the second embodiment. However, unlike the second embodiment using a spring, a thin plate-shaped reed valve 90 that bends according to pressure is used.
[0062]
In FIG. 7, a pipe 92 whose upper end is closed and whose lower end communicates with the discharge chamber 19 and a pipe 93 whose lower end is closed and whose upper end communicates with the discharge pipe 55 are adjacent to each other across a thick partition wall 95. ing. The pipe 92 and the pipe 93 communicate with each other through a vent 94 provided in the partition wall 95.
[0063]
The reed valve 90 is disposed on the pipe 93 side so as to close the ventilation port 94, and one end thereof is fixed by a valve support 91.
[0064]
In such a configuration, when pressure is applied from the space on the pipe 92 side, the reed valve 90 that has closed the outlet of the vent 94 bends toward the inside of the pipe 93 and opens the vent 94.
[0065]
In addition, the reed valve 90 can freely take a length in the pipe direction with respect to the pipe provided. For this reason, by making the reed valve longer, it is possible to open and close by a small pressure difference, and the manufacturing cost can be reduced.
[0066]
The refrigerant gas that has passed through the pipe 92 from the discharge chamber 19 flows to the ventilation port 94 on the side surface because the tip is closed. Although the tip of the vent 94 is closed by a reed valve 90, the reed valve 90 deflects toward the pipe 93 by the discharge pressure of the refrigerant gas due to the operation of the gas compressor 50, so the vent 94 is opened. Pass the refrigerant gas.
[0067]
At this time, if an excessive pressure is applied, the reed valve 90 is excessively bent. If this pressure exceeds the elastic force of the reed valve 90, it may lead to breakage. Therefore, the valve support 91 prevents the reed valve 90 from bending more than a certain amount and prevents the breakage.
[0068]
When the gas compressor 50 is stopped, the reed valve 90 is closed, and a differential pressure due to a temperature difference is generated in each part of the gas compressor 50, the evaporator 60, and the condenser 65, and the liquefied refrigerant in the discharge chamber 19 Even when the lubricating oil containing gas tries to flow out to the discharge pipe 55, the outflow pressure cannot cause the reed valve 90 to bend. Therefore, the ventilation port 94 remains closed, and it is possible to prevent the outflow of the lubricating oil containing the liquefied refrigerant gas.
[0069]
【The invention's effect】
As described above, according to the present invention, since the discharge port or the discharge pipe is provided with the valve, it is possible to prevent the lubricating oil present in the discharge chamber from flowing out of the gas compressor together with the refrigerant gas. Thus, the lubrication oil in the gas compressor can be prevented from being diluted.
[0070]
Accordingly, since the non-lubricated state does not occur during the operation of the gas compressor, the burning of each part is prevented, and the safe and stable operation of the gas compressor is realized. In addition, adhesion of lubricating oil to an external heat exchanger such as an evaporator or a condenser can be prevented, which leads to an improvement in the performance of the air conditioning system.
[Brief description of the drawings]
FIG. 1 is a configuration diagram of a first embodiment of the present invention. FIG. 2 is a cross-sectional view taken along a line CC in FIG. 1. FIG. 3 is a wiring diagram in the first embodiment of the present invention. FIG. 5 is a cross-sectional view taken along the line DD in FIG. 4; FIG. 6 is an enlarged cross-sectional view of the valve in FIG. 4; FIG. 7 is an enlarged cross-sectional view of a reed valve. FIG. 9 is a cross-sectional view taken along the line EE in FIG. 7; FIG. 9 is a schematic diagram illustrating the overall configuration of the air conditioning system; FIG. 10 is a cross-sectional view taken along the line AA in FIG. 12 is a cross-sectional view taken along the line BB in FIG. 10 [FIG. 13] A diagram for explaining a failure occurrence mechanism at the time of stoppage [Description of reference numerals]
DESCRIPTION OF SYMBOLS 1 Compressor main body 4 Cylinder 5 Rotor 6 Rotating shaft 14 Compression chamber 16 Suction chamber 17 Check valve 18 Oil separator 19 Discharge chamber 21 Discharge port 22 Solenoid valve 23 Relief valve 25 Valve 34 Electromagnetic coil 52 Case 55 Discharge pipe 65 Condenser 70 engine 72 electromagnetic clutch 75 power supply 76 switch 81 valve head 82 spring 83 valve chamber 86 valve seat 90 reed valve 92, 93 pipe

Claims (7)

A rotating shaft that is rotated by external power,
A clutch for transmitting and disconnecting power to the rotating shaft;
By the rotation of the rotating shaft, at least one compression chamber for compressing the refrigerant gas,
An oil separation unit that separates lubricating oil from the refrigerant gas compressed in the compression chamber,
A discharge chamber in which lubricating oil separated through the oil separating unit is stored,
A discharge port for discharging the refrigerant gas discharged to the discharge chamber to the outside,
A gas compressor, wherein a valve for preventing the lubricating oil from flowing out when the rotating shaft is stopped is provided at the discharge port. A rotating shaft that is rotated by external power,
A clutch for transmitting and disconnecting power to the rotating shaft;
By the rotation of the rotating shaft, at least one compression chamber for compressing the refrigerant gas,
An oil separation unit that separates lubricating oil from the refrigerant gas compressed in the compression chamber,
A discharge chamber in which lubricating oil separated through the oil separating unit is stored,
A discharge port for discharging the refrigerant gas discharged to the discharge chamber to the outside,
Equipped with a discharge pipe for guiding the refrigerant gas from the discharge port to an external device,
A gas compressor, wherein a valve for preventing the outflow of the lubricating oil when the rotation shaft is stopped is provided in the discharge pipe. The gas according to claim 1 or 2, wherein the valve is an electromagnetic valve, and the electromagnetic valve is interlocked with the clutch, and the clutch is opened when the clutch is connected and closed when the clutch is disconnected. Compressor. 3. The gas compressor according to claim 1, wherein the valve is a fluid-operated valve, and is opened and closed according to a pressure difference between front and rear spaces partitioned by the fluid-operated valve. 5. The valve according to claim 4, wherein the fluid-operated valve is a valve provided with a valve head seated on a valve seat and an urging means for urging the valve head against the valve seat when the operation is stopped. Gas compressor. The gas compressor according to claim 4, wherein the fluid operated valve includes a reed valve. The gas compressor according to any one of claims 1 to 6, wherein a relief valve for releasing pressure is disposed in a space created by the valve and the discharge chamber.

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