JP5218905B2 - Variable capacity swash plate compressor - Google Patents

Description

  The present invention relates to a variable capacity swash plate compressor in which carbon dioxide is used as a refrigerant and a piston ring is provided on a piston that is moved by a swinging swash plate.

  In the variable capacity compressor disclosed in Patent Document 1, an extraction passage that always communicates the crank chamber and the suction chamber is provided in the drive shaft, and an inlet portion of the extraction passage that faces the crank chamber is provided in a radial direction of the drive shaft. It is characterized by setting. The mist-like oil that flows into the extraction passage together with the blow-by gas first collides with the inner peripheral surface of the inlet portion of the extraction passage by the rotational movement of the drive shaft, and is separated and attached to the centrifugal force due to the rotational movement of the drive shaft. Therefore, the amount of oil flowing out from the crank chamber to the suction chamber can be reduced with a simple configuration.

Patent Document 2 discloses a refrigerant compressor in which an oil separator including a centrifugal separator is provided on a refrigerant gas discharge passage. In Patent Document 2, the oil separator reservoir and the crank chamber communicate with each other via an air supply passage, and the oil in the oil reservoir is supplied together with the refrigerant gas supplied to the crank chamber for capacity control. It is disclosed that the air is returned to the crank chamber through the air supply passage, in other words, the air supply passage also serves as an oil return passage, and the amount of refrigerant gas supplied to the crank chamber is set on the air supply passage. It is disclosed that a control valve for adjusting is provided. As a result, the oil separated from the refrigerant is stored in the oil reservoir, and is further returned to the crank chamber via an air supply passage connecting the oil reservoir and the crank chamber, that is, an oil return path. It can be seen that the amount returned with the refrigerant returned to the chamber is adjusted.
JP 2003-343440 A JP 2005-120970 A

  As described above, Patent Document 1 discloses a compressor in which an oil separator (bleeding OS) is provided in the middle of a bleeding path. It is known that the extraction OS disclosed in Patent Document 1 can reduce the amount of oil circulation in the refrigeration cycle to some extent when R134a is used as a refrigerant.

However, in the case of a compressor using carbon dioxide (CO ₂ ) as a refrigerant, the differential pressure between the crank chamber and the suction chamber is several to ten times higher than that of R134a, and components in the crank chamber are concentrated in the center. Therefore, the flow velocity of the gas in the vicinity of the drive shaft is increased, and the oil is easily caught in the gas flow and discharged to the suction chamber. As a result, the amount of oil circulation in the refrigeration cycle is increased as compared with a compressor using R134a, and a decrease in refrigeration capacity cannot be sufficiently suppressed.

  In a compressor that employs a piston ring to reduce refrigerant leakage (blow-by) from the gap between the piston and the cylinder bore, the piston ring is effective in improving the compression efficiency. Since the oil contained in the refrigerant compressed in the step is prevented from entering the crank chamber, it is a great obstacle to return the oil that has once flowed out of the crank chamber to the crank chamber. For this reason, even if an oil separator is provided in the middle of the bleed path, a slight amount of oil flows out of the crank chamber, which may cause a problem that the amount of oil in the crank chamber is lost and the compressor is seized.

  On the other hand, Patent Document 2 discloses a configuration (discharge OS) in which an oil separator is provided on a refrigerant gas discharge passage. In this configuration, the oil centrifuged by the discharge OS is throttled by the control valve together with the amount of refrigerant supplied to the crank chamber and returned to the crank chamber, so that the control valve is closed under a high load or the like. The separated oil does not return to the crank chamber, and the oil in the crank chamber may be insufficient as in the compressor disclosed in Patent Document 1.

  If a configuration is adopted in which an oil return amount to the crank chamber is reduced by providing an orifice instead of this control valve, if all the separated oil in the reservoir is returned to the crank chamber, the high-pressure gas in the discharge chamber There is a problem that the performance is greatly deteriorated (especially when the load is high) by blowing through the orifice into the crank chamber. Therefore, if the orifice diameter is set to be small so that high-pressure gas does not blow through, the oil separated by the discharge OS is not sufficiently returned to the crank chamber and separated when the pressure difference between the discharge pressure and the crank chamber is small, such as at low loads. There is a disadvantage that the oil overflows from the reservoir and flows out of the compressor.

  In view of the above points, the present invention is to provide a variable capacity swash plate compressor that can reduce the amount of oil circulation under a wide range of operating conditions and maintain an appropriate amount of oil in the crank chamber.

Accordingly, the present invention provides a crank chamber formed in the housing, a drive shaft that passes through the crank chamber and is rotatably supported by the housing, and a swash plate that swings in synchronization with the rotation of the drive shaft. And a piston reciprocating in a cylinder bore formed in a cylinder block secured to the periphery of the swash plate and fixed in the housing as the swash plate swings, and further constitutes a part of the housing A suction chamber and a discharge chamber are formed in the cylinder head, and a refrigerant is sucked from the suction chamber by a reciprocating motion of the piston and discharged into the discharge chamber. A piston ring is provided in the piston, and the stroke amount of the piston In the variable capacity swash plate compressor that is variable by changing the tilt angle of the swash plate, the bleed air passing through the drive shaft and communicating the crank chamber and the suction chamber A first oil separator mechanism provided in the passage, a second oil separator mechanism provided in a discharge path from the discharge chamber to the discharge port, and the discharge chamber and the crank chamber are always in communication with each other; An oil return path for returning the oil separated by the second oil separator mechanism to the crank chamber and a throttle means provided on the oil return path are provided .

  According to the first aspect of the present invention, the first oil separator mechanism (bleeding OS) provided on the bleed side and the second oil separator (discharge OS) provided on the discharge side are used in combination. By providing an oil return path that returns the separated oil to the crankcase, the amount of oil in the crankcase during operation can be properly maintained while maintaining high blow-by sealing performance by the piston ring. Reliability can be ensured. In particular, since the oil flowing out from the crank chamber to the suction chamber is reduced by the extraction OS, it is not necessary to set a high amount of oil to be separated and collected by the discharge OS. Therefore, the diameter of the orifice provided in the oil return path can be set small, and the high pressure fluid (gas / oil) flowing from the discharge chamber to the crank chamber can be suppressed to minimize the deterioration in performance.

  In addition, the first oil separator mechanism (bleeding OS) includes an introduction hole provided penetrating in a radial direction of the drive shaft, an axial center extending substantially from the center of the drive shaft, and the introduction hole and the drive. A first discharge hole communicating with the valve plate side end of the shaft, and a second discharge hole penetrating the cylinder block and communicating the suction chamber and the first discharge hole. Claim 2) is desirable.

  According to the second aspect of the present invention, since the introduction hole is provided so as to penetrate in the radial direction, the return flow rate of the oil in the introduction hole is about ½, so that the oil is not easily caught in the gas flow. Separability can be improved.

  Furthermore, it is desirable that the inner diameter of the introduction hole is 4 to 7 mm, and the outer diameter of the drive shaft portion (introduction part) where the introduction hole is formed is in the range of 20 mm to 26 mm.

  This is because if the inner diameter of the introduction hole is smaller than 4 mm, the oil may be discharged by a high-speed flow, and if it is larger than 7 mm, the rigidity of the drive shaft may be reduced. .

  In addition, the centrifugal force acting on the oil can be increased by setting the outer diameter of the introduction portion of the drive shaft to 20 mm or more, and separability can be secured even with carbon dioxide. However, if the diameter is larger than 26 mm, the oil stored in the crank chamber This is because there is a fear that the amount will decrease. In other words, the proper oil amount is usually 30 to 70 cc, but if the drive shaft diameter exceeds 26 mm, there is a greater possibility that 70 cc cannot be stored.

  It is desirable that the first discharge hole includes a diameter-expanding portion whose diameter gradually increases toward the second discharge hole. In addition, it is preferable that the cylinder block has a protrusion portion that protrudes into the enlarged diameter portion of the first discharge hole formed in the drive shaft, and the second discharge hole is formed in the protrusion portion. Accordingly, the second discharge hole is naturally formed to have a small diameter with respect to the enlarged diameter portion of the first discharge hole, and therefore, the stage from the first discharge hole to the second discharge hole. Thus, the second oil separation can be performed.

  Further, the second oil separator mechanism (discharge OS) includes a first discharge passage that extends in a direction in which the refrigerant is pushed out from a discharge chamber in which the refrigerant is pushed out by the piston, the first discharge passage, and the discharge port. A second discharge passage that communicates with the second discharge passage, a small diameter portion that is provided in the second discharge passage and that extends along the second discharge passage to a position facing the first discharge passage, and the small diameter portion A separation portion formed of a diameter-expanding portion that expands so as to abut on the second discharge passage toward the discharge port side, and at the opposite end portion of the discharge port of the second discharge passage, It is desirable that the oil return path is open. A filter is preferably disposed below the second discharge passage, and a first dust collection pocket is preferably formed at the lower end. Further, a foreign matter capturing means such as a non-woven fabric may be provided in the dust collection pocket.

  Thereby, the discharge gas discharged from the first discharge passage swirls around the outer periphery of the small-diameter portion of the separation portion arranged in the second discharge passage, moves in a spiral shape, and moves below the second discharge passage. Since the inside of the small-diameter portion of the separating portion is raised to reach the discharge port from the enlarged-diameter portion, oil separation can be reliably performed.

  The oil return path communicates with the first return path extending from the second discharge path and the first return path, and is disposed between the cylinder head and the cylinder head and the cylinder block. The valve plate, the discharge valve, the cylinder gasket, and the second return path that penetrates the cylinder block and opens to the crank chamber are desirable. It is desirable to provide a second dust collection pocket in a portion from the first oil return path to the second oil return path.

  As a result, the oil separated by the discharge OS and accumulated below the second discharge passage is returned to the crank chamber through the first return path and the second return path.

Furthermore, it is desirable to provide an aperture means on the second return path. The throttle means is preferably provided either in the cylinder head of the second return path or in the valve plate, and particularly in the valve plate. Further, the equivalent diameter of the said throttle means is in the range of 0.15-0.35 mm (claim 5) is desirable.

  Thus, by providing the throttle means either in the cylinder head or on the valve plate on the second return path, the airtightness of the high-pressure oil return path is greatly improved. (COP) is improved. Moreover, the oil return property at the time of low load can be improved by setting the equivalent diameter of the throttle means to 0.15 mm or more, and the gas return at the time of high load can be improved by setting it to 0.35 mm or less. Therefore, it is possible to suppress a decrease in COP.

Furthermore, a heat insulating material is provided on at least one wall surface of the discharge chamber through which the high-pressure gas passes, the wall surfaces of the first discharge passage and the second discharge passage, and the wall surface of the suction chamber through which the low-pressure gas passes. (Claim 6 ) is desirable. As a material for the heat insulating material, a resin-based material such as PTFE, PPS, PBT, PI, or PAI can be selected. Further, in consideration of heat resistance, reinforcing fibers such as glass fibers may be appropriately added.

Accordingly, the high-pressure gas and the low-pressure gas can be shut off in temperature, so that the cooling effect by the oil of the high-pressure gas can be prevented and the intake gas can be prevented from overheating. Furthermore, a high discharge temperature at the time of low OCR can be prevented.

  As described above, according to the present invention, in a capacity swash plate type compressor that is used in a refrigeration cycle using carbon dioxide as a refrigerant and employs a piston ring, the extraction OS and the discharge OS are used in combination. By providing an oil return path that returns the oil separated in the crank chamber to the crank chamber, the oil volume in the crank chamber is maintained properly and the oil circulation rate (OCR) is reduced while maintaining high blow-by sealing performance by the piston ring. It is possible to reduce from a load to a high load. Further, by providing a heat insulating material that suppresses heat conduction between the high and low pressure gases, a high discharge temperature can be prevented.

  Embodiments of the present invention will be described below with reference to the drawings.

  As shown in FIG. 1, a variable capacity swash plate compressor 1 constituting a part of a refrigeration cycle using carbon dioxide as a refrigerant includes a front head 2, a cylinder housing 3, and a housing 5 including a cylinder head 4, and the front head. 2, a cylinder block 6 fixed in the cylinder housing 3, a crank chamber 7 defined by the cylinder housing 3, a drive shaft 8 rotatably held by the front head 2 and the cylinder block 6, and this drive A swash plate 9 that is swingably held on a shaft 8; a rod 10 that is fixed to the drive shaft 8 and transmits a rotational force to the swash plate 9; a cylinder bore 11 formed in the cylinder block 6; A piston 12 that is held on the periphery of the swash plate 9 and reciprocates in the cylinder bore 11 by the swinging motion of the swash plate 9; Comprising a piston ring 13 provided in tons 12. A valve plate 14 and a cylinder head gasket 36 are disposed between the cylinder block 6 and the cylinder head 4, and a discharge valve 15 is mounted on the cylinder head side.

  A suction chamber 16 and a discharge chamber 17 are formed in the cylinder head 4. The suction chamber 16 communicates with a suction port (not shown), and the discharge chamber 17 communicates with a discharge port 18. In addition, a pressure control valve (not shown) is provided in an air supply passage (not shown) connecting the discharge chamber 17 and the crank chamber 7.

  With the above configuration, the piston 12 reciprocates along the cylinder bore 11 by the swash plate 9 that rotates and swings as the drive shaft 8 rotates, and the refrigerant sucked from the suction chamber 16 is discharged through the discharge chamber 17. Delivered from outlet 18. Further, by adjusting the opening degree of the control valve in accordance with the operating load, the high pressure gas in the discharge chamber 17 is introduced into the crank chamber 7 to adjust the pressure in the crank chamber 7, and the inclination angle of the swash plate 9 is adjusted. Is appropriately changed.

  In the variable capacity swash plate compressor 1 having the above-described configuration, the drive shaft 8 is formed with an introduction hole 19 that penetrates the drive shaft 8 in the radial direction, and the shaft of the drive shaft 8 extends from the approximate center of the introduction hole 19. A first discharge hole 20 formed along the direction is formed. The first discharge hole 20 has an enlarged diameter portion 21 that increases in diameter toward the cylinder block side of the drive shaft 8, and a protruding portion 22 that protrudes from the cylinder block 6 is located in the enlarged diameter portion 21. A second discharge hole 23 that opens to the first discharge hole 20 and communicates the first discharge hole 20 and the suction chamber 16 is formed in the approximate center of the protrusion 22. As a result, the introduction hole 19, the first discharge hole 20, and the second discharge hole 23 form an extraction passage, and further, a first oil separator mechanism (extraction OS). As shown in FIG. 2, the introduction hole 19 may be provided on the front head 2 side with respect to the rod 10. In this case, since the first discharge hole 20 and the rod 10 interfere with each other, the communicating portion 37 may be provided on the rod 10.

  The diameter of the introduction hole 19 is set within a range of 4 mm to 7 mm. By setting it to 4 mm or more, the problem that the refrigerant gas has a high flow rate and oil is discharged without being separated is solved, and by setting it to 7 mm or less, the rigidity of the drive shaft 8 is prevented from being lowered. Further, the portion (introduction portion) 8A of the drive shaft 8 where the introduction hole 19 is formed has an outer diameter set in a range of 20 mm or more and 26 mm or less. By setting the outer diameter to 20 mm or more, the centrifugal force acting on the refrigerant gas oil can be increased and the oil separation from the refrigerant gas can be improved. By setting the outer diameter to 26 mm or less, the amount of oil stored in the crank chamber 7 Can be secured. Usually, the appropriate amount of oil stored in the crank chamber 7 is 30 to 70 cc. However, if it exceeds 26 mm, there is a high possibility that the oil will not be stored up to 70 cc.

  Thereby, in the first oil separator mechanism (extracted air OS), the oil is separated from the refrigerant gas flowing in from the introduction hole 19 by the centrifugal force generated by the rotation of the drive shaft 8 (first extracted OS), and further, the first oil separator mechanism (extracted air OS). Oil separation (second extraction OS) is performed again at the stage of flowing into the second discharge hole 23 from the discharge hole 20. Further, since the introduction hole 19 penetrates in the radial direction, the flow rate of the refrigerant gas is reduced, and the oil separation property in the first extraction OS can be improved.

  Further, the cylinder head 4 is formed with a first discharge passage 24 extending in a direction in which the refrigerant is pushed out from a discharge chamber 17 through which the refrigerant is pushed out by the piston 12, and perpendicular to the first discharge passage 24. Thus, a second discharge passage 25 communicating with the discharge port 18 is formed. Further, the second discharge passage 25 has a small diameter portion 26 extending along the second discharge passage 25 at a position facing the first discharge passage 24, and from the small diameter portion 26 to the discharge port 18 side. A separation portion 28 composed of a diameter-expanded portion 27 that increases in diameter so as to come into contact with the second discharge passage 25 is mounted and fixed. Accordingly, the first discharge passage 24, the second discharge passage 25, and the separation portion 28 constitute a second oil separator mechanism (discharge OS).

Further, a filter 29 is disposed below the second discharge passage 25, and a first dust collecting pocket 30 is formed at the lower end. The oil separated by the second oil separator mechanism is returned into the crank chamber 7 through an oil return path 31 described below.

  In the second oil separator mechanism configured as described above, the refrigerant gas discharged from the first discharge passage 24 swirls around the outer periphery of the small-diameter portion 26 of the separation portion 28 and descends in a spiral shape, and further the small-diameter portion 26. Then, the liquid is discharged from the discharge port 18. In this path, the refrigerant gas swirls around the outer periphery of the small-diameter portion 26 at high speed, and the oil contained in the refrigerant gas is reliably separated by changing the flow direction from descending to ascending.

  As described above, according to the present invention, the oil circulation rate (OCR) is sufficiently lowered by using the extraction OS and the discharge OS together, and the separated oil is supplied under any conditions via the oil return path. Can also be returned to the crank chamber.

  The oil return path 31 is a first return that extends in the cylinder head 4 along the longitudinal direction of the second discharge passage 25 from below the filter 29 provided in the second discharge passage 25. Through the path 32 and the first return path 32, the cylinder head 4, the valve plate portion (including the cylinder head gasket 36, the discharge valve 15 and the valve plate 14), the intake valve 40 and the cylinder block 6 are penetrated. And a second return path 33 that opens into the crank chamber 7. Further, a throttle mechanism 35 is provided in a portion from the cylinder head 4 to the valve plate 14 in the second return path 33. If the throttle mechanism 35 is provided in the cylinder block 6, a high pressure (discharge pressure) acts on the valve plate portion upstream of the throttle function, and the valve plate 14 is airtight due to surface contact. And the suction valve 40 leak high pressure gas. According to the configuration of the present invention, since the throttle mechanism 35 is provided on the upstream side of the suction valve 40, the pressure of the metal contact portion becomes low, and the airtightness can be maintained. In particular, the provision of the throttle mechanism 35 on the valve plate 14 facilitates the formation of the throttle mechanism 35, and it is particularly desirable to perform the laser processing. A second dust collection pocket 34 is formed between the first return path 32 and the second return path 33.

  The equivalent diameter of the diaphragm mechanism 35 is set within a range of 0.15 mm to 0.35 mm. As shown in FIG. 4, by setting the equivalent diameter to 0.15 mm or more, the problem that the oil does not return sufficiently at low load and flows out of the compressor is eliminated, and by setting the equivalent diameter to 0.35 mm or less. This solves the problem that the coefficient of performance (COP) decreases due to gas blowing into the crank chamber at high load.

  When the configuration according to the present invention (bleeding OS + piston ring + discharge OS + oil return throttling mechanism: 0.27 mm) is employed, the OCR becomes 0.5 (%) or less from the low load condition to the high load condition. A high oil separation effect was obtained as compared with 4.5 to 5.7% in the case of OS alone. The improvement rate of COP reached 25% at medium and low load conditions.

  By the way, the oil circulating in the refrigeration cycle has the problem of reducing the refrigeration capacity by inhibiting heat exchange in the refrigeration cycle, while taking heat from the refrigerant gas compressed by the cylinder bore and becoming high pressure and high temperature, It also has a favorable effect of suppressing the temperature rise of the discharge gas. Therefore, as a result of reducing the oil circulating in the refrigeration cycle by the oil separator, the temperature of the discharge gas rises, the heat of the discharge gas is conducted to the intake gas, the density of the intake gas is reduced, and the volume efficiency is lowered. There is a fear.

However, in the capacity swash plate compressor 1 according to the present invention, the heat insulating material 38 is further arranged on the peripheral walls of the discharge chamber 17, the first discharge passage 24, and the second discharge passage 25 on the high pressure side to further reduce the pressure. A heat insulating material 38 is also disposed on the peripheral wall of the suction chamber 16 on the side.

  As a result, heat conduction between the high-pressure and high-temperature refrigerant gas that passes through the high-pressure side and the low-pressure and low-temperature refrigerant gas that passes through the low-pressure side can be cut off, so that the intake gas can be prevented from overheating. Further, as shown in FIG. 3, a high discharge temperature at the time of low OCR can be prevented. As the material of the heat insulating material 38, a resin-based material such as PTFE, PPS, PBT, PI, or PAI can be selected. Further, in consideration of heat resistance, reinforcing fibers such as glass fibers may be added as appropriate. In FIG. 3, the characteristic line indicated by the alternate long and short dash line indicates the relationship between the rotational speed of the compressor and the discharge temperature Td without the heat insulating material, and the characteristic line indicated by the dotted line indicates that the heat insulating material is provided only on the discharge side. (PBT) shows the relationship between the rotational speed of the compressor and the discharge temperature Td, and the characteristic lines shown by the solid lines indicate the rotational speed of the compressor when heat insulating material is placed on the high-pressure side and the low-pressure side. And the discharge temperature Td. Thus, even if a heat insulating material is provided only on the high-pressure side or the low-pressure side so as to block the heat conduction between the high-pressure side and the low-pressure side, a corresponding effect can be obtained.

It is sectional drawing which showed the outline of the capacity | capacitance swash plate type compressor which concerns on the Example of this invention. It is the partially expanded sectional view which showed another form of the shaft part. It is a characteristic diagram which showed the relationship between the rotational speed of the capacity | capacitance swash plate type compressor which concerns on this invention, and discharge temperature. FIG. 5 is a characteristic diagram showing the relationship between the equivalent diameter of the aperture mechanism and COP.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Variable capacity swash plate type compressor 2 Front head 3 Cylinder housing 4 Cylinder head 5 Housing 6 Cylinder block 7 Crank chamber 8 Drive shaft 9 Swash plate 10 Rod 11 Cylinder bore 12 Piston 13 Piston ring 14 Valve plate 15 Discharge valve 16 Suction chamber 17 Discharge Chamber 18 Discharge port 19 Introduction hole 20 First discharge hole 21 Expanded portion 22 Entry portion 23 Second discharge hole 24 First discharge passage 25 Second discharge passage 26 Small diameter portion 27 Expanded portion 28 Separating portion 29 Filter 30 First Dust Collection Pocket 31 Oil Return Path 32 First Oil Return Path 33 Second Oil Return Path 34 Second Dust Collection Pocket 35 Throttle Mechanism 36 Cylinder Head Gasket 37 Communication Portion 38 Heat Insulation Material 40 Suction Valve

Claims (6)

A crank chamber formed in the housing, a drive shaft that passes through the crank chamber and is rotatably supported by the housing, a swash plate that swings in synchronization with the rotation of the drive shaft, and a peripheral edge of the swash plate And a piston that reciprocates in a cylinder bore formed in a cylinder block fixed in the housing as the swash plate swings. And a discharge chamber are formed, the refrigerant is sucked from the suction chamber by the reciprocating motion of the piston and discharged into the discharge chamber, and the piston is provided with a piston ring, and the stroke amount of the piston is inclined by the swash plate. In a variable capacity swash plate compressor that can be changed by changing the angle,
A first oil separator mechanism provided in an extraction passage passing through the drive shaft and communicating the crank chamber and the suction chamber;
A second oil separator mechanism provided in a discharge path from the discharge chamber to the discharge port;
An oil return path that constantly communicates the discharge chamber and the crank chamber and returns the oil separated by the second oil separator mechanism to the crank chamber ;
A variable capacity swash plate compressor, comprising a throttle means provided on the oil return path .   The first oil separator mechanism includes an introduction hole provided so as to penetrate in a radial direction of the drive shaft, and a substantially center of the drive shaft extending in the axial direction to extend the introduction hole and a cylinder head side end of the drive shaft. 2. A first exhaust hole that communicates with a portion, and a second exhaust hole that passes through the cylinder block and communicates the suction chamber and the first exhaust hole. The variable capacity swash plate compressor described.   3. The variable capacity swash plate compressor according to claim 2, wherein an inner diameter of the introduction hole is 4 to 7 mm, and an outer diameter of a portion of the drive shaft where the introduction hole is formed is in a range of 20 mm to 26 mm.   4. The variable capacity swash plate compressor according to claim 2, wherein the first discharge hole includes an enlarged-diameter portion whose diameter gradually increases toward the second discharge hole. 5. 5. The variable capacity swash plate compressor according to claim 1, wherein an equivalent diameter of the throttle means is in a range of 0.15 to 0.35 mm. A heat insulating material is disposed on at least one wall surface of the discharge chamber through which the high-pressure gas passes, the wall surfaces of the first discharge passage and the second discharge passage, and the wall surface of the suction chamber through which the low-pressure gas passes. The variable capacity swash plate compressor according to any one of claims 1 to 5 .

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