JP2007162561A - Refrigerant compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a refrigerant compressor making an oil separator compact while securing separating capacity of lubricating oil. <P>SOLUTION: The oil separator 50 is provided with an inlet port 54a for refrigerant gas to the inside of a separation space S, an outlet port 52c for refrigerant gas to the outside of the separation space S, and a swirl member 52 disposed between the inlet port 54a and the outlet port 52c. The inlet port 54a and the outlet port 52c are arranged so that an outlet direction Z1 of refrigerant gas from the outlet port 52c is in the same direction as an inlet direction Z2 of refrigerant gas into the inlet port 54a. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a refrigerant compressor provided with an oil separator that separates lubricating oil contained in refrigerant gas by swirling the refrigerant gas along a swirling portion in a separation space.

  In a refrigerant compressor that constitutes a refrigeration circuit and compresses refrigerant gas, lubricating oil is mixed into the refrigerant gas, and the lubricating oil is supplied to the compression mechanism so that the compression mechanism is lubricated. . In the refrigerant compressor, an oil separator is provided on the refrigerant gas discharge passage to prevent the lubricating oil from being taken out to the external refrigerant circuit together with the refrigerant gas (see, for example, Patent Document 1 and Patent Document 2). . This is because when the lubricating oil is taken out to the external refrigerant circuit, the lubricating oil adheres to, for example, the inner wall surface of the gas cooler or the evaporator, and the heat exchange efficiency decreases.

  As shown in FIG. 6, the oil separator described in Patent Document 1 includes an oil separation chamber 92 including a cylindrical inner cylinder 90 and a cylindrical outer cylinder 91 surrounding the inner cylinder 90. A separation space 93 is formed between the inner cylinder 90 and the outer cylinder 91. The lower end 90b of the inner cylinder 90 is a gas discharge port and communicates with an external refrigerant circuit (not shown). The discharge chamber 94 and the oil separation chamber 92 are communicated with each other by an inflow pipe 95. Further, an oil outlet 97 is formed on the upper side of the outer cylinder 91, and an oil storage chamber 96 communicating with the oil separation chamber 92 via the oil outlet 97 is formed around the oil separation chamber 92.

  In the refrigerant compressor provided with the oil separator having the above configuration, the refrigerant gas discharged into the discharge chamber 94 is introduced into the oil separation chamber 92 through the inflow pipe 95. The refrigerant gas introduced into the separation space 93 of the oil separation chamber 92 rises spirally around the inner cylinder 90. Lubricating oil is separated from the refrigerant gas by the centrifugal force generated by the spiral rotation, and the separated lubricating oil adheres to the inner peripheral surface of the outer cylinder 91. Thereafter, the lubricating oil adhering to the inner peripheral surface of the outer cylinder 91 is raised together with the refrigerant gas, and flows out from the oil outlet 97 of the outer cylinder 91 to the oil storage chamber 96. On the other hand, the refrigerant gas from which the lubricating oil is separated descends in the inner cylinder 90 and is supplied to the external refrigerant circuit from the gas discharge port which is the lower end 90b of the inner cylinder 90.

  As shown in FIG. 7, the oil separator described in Patent Document 2 is provided in a chamber 108 in the housing. The oil separator includes a bottomed cylindrical base body 101 having a separation chamber 100, and a flanged air guide tube 102 attached to the base body 101 so as to hang concentrically with the base body 101 from an upper opening edge of the separation chamber 100. Become. A through hole 101 a is formed in the side wall of the base 101, and the through hole 101 a communicates with a discharge passage 104 that connects the separation chamber 100 and the discharge chamber 103. The discharge passage 104 is formed through a fixture 106 that fixes the discharge valve to the housing. Further, a through hole 105 is formed in the bottom wall of the base 101.

In the refrigerant compressor including the oil separator having the above-described configuration, the refrigerant gas discharged into the discharge chamber 103 is introduced into the separation chamber 100 from the discharge passage 104 through the through hole 101a. The refrigerant gas introduced into the separation chamber 100 swirls around the flanged air guide tube 102. Then, the lubricating oil is separated from the refrigerant gas by the centrifugal force due to the turning, and the separated lubricating oil adheres to the inner peripheral surface of the side wall of the base 101. Thereafter, the lubricating oil passes through a through hole 105 provided in the bottom wall of the separation chamber 100 and stays at the bottom of the chamber 108. On the other hand, the refrigerant gas from which the lubricating oil has been separated passes through the flanged air guide tube 102 and is supplied to the external refrigerant circuit via another discharge passage.
Japanese Patent Laid-Open No. 2002-5021 JP 2001-165049 A

  Incidentally, in the oil separator described in Patent Document 1, the refrigerant gas introduced into the oil separation chamber 92 via the inflow pipe 95 is collided with the inner cylinder 90, and the flow of the refrigerant gas is introduced into the oil separation chamber 92. The refrigerant gas is caused to flow along the inner cylinder 90 by being changed in an orthogonal direction, and is swirled spirally in the separation space 93. For this reason, the refrigerant gas introduced into the separation space 93 has a lower flow velocity than before being introduced into the separation space 93. In order to separate as much lubricating oil as possible from the refrigerant gas whose flow rate has decreased, it is necessary to increase the swirling distance of the refrigerant gas, and as a result, the inner cylinder 90 and the outer cylinder 91 in the axial direction are required. The oil separator became larger as the length increased.

  Also in the oil separator described in Patent Document 2, the refrigerant gas introduced into the separation chamber 100 via the discharge passage 104 is caused to collide with the flanged air guide tube 102 and the flow of the refrigerant gas is introduced into the separation chamber 100. The refrigerant gas is caused to flow along the flanged air guide tube 102 by being changed in a direction orthogonal to the direction, and the periphery of the flanged air guide tube 102 is spirally swirled. For this reason, the refrigerant gas introduced into the separation chamber 100 has a lower flow velocity than before being introduced into the separation chamber 100. And in order to isolate | separate as much lubricating oil as possible from the refrigerant gas with which the flow velocity fell, it is necessary to increase the turning speed of the refrigerant gas around the flanged air guide tube 102. As a result, it is necessary to increase the flow velocity of the refrigerant gas before it collides with the flanged air guide tube 102. For that purpose, it is necessary to increase the passage distance of the discharge passage 104, and the oil separator is enlarged. .

  An object of the present invention is to provide a piston-type compressor capable of making the oil separator compact while ensuring the separation ability of the lubricating oil.

  In order to solve the above problems, the invention according to claim 1 compresses the refrigerant gas by the operation of the compression mechanism, and on the compressed refrigerant gas discharge passage, A circumferential wall that surrounds the swivel portion along the axial direction, and a separation space between the swirl portion and the circumferential wall, and the coolant gas is swirled along the swirl portion in the separation space, thereby In the refrigerant compressor in which an oil separator for separating the lubricating oil contained in the refrigerant gas is disposed, and further, an oil outlet for allowing the lubricating oil separated from the refrigerant gas to flow out of the oil separator is formed on the peripheral wall. The oil separator includes a refrigerant gas inlet to the separation space and a refrigerant gas outlet to the outside of the separation space, and the swivel portion is disposed between the inlet and the outlet. As well as Out direction of the refrigerant gas from the outlet port was arranged conductor inlet and outlet so as to have the same direction as the direction of introduction of the refrigerant gas to the inlet.

  According to this configuration, the refrigerant gas introduced into the separation space from the introduction port flows toward the outlet port while turning around the turning portion, and is led out of the separation space from the outlet port. At this time, the direction in which the refrigerant gas led out from the lead-out port is the same as the direction in which the refrigerant gas introduced from the lead-in port is the same, so the refrigerant gas introduced into the separation space When turning around, it flows toward the outlet without changing its flowing direction to a direction different from the introduction direction, and is led out from the outlet as it is. Therefore, the refrigerant gas swirls around the swivel portion at a flow velocity close to that when introduced into the separation space without reducing the flow velocity in the separation space, and the lubricating oil is efficiently centrifuged from the refrigerant gas. The Therefore, according to the oil separator, the refrigerant gas before being introduced into the oil separator in order to increase the turning distance of the refrigerant gas in order to increase the separation ability of the lubricating oil from the refrigerant gas or to increase the flow velocity of the refrigerant gas. It is not necessary to take a long passage length. As a result, the oil separator can be made compact while ensuring the ability to separate the lubricating oil from the refrigerant gas.

In addition, a direction in which the refrigerant gas is introduced into the inlet and a direction in which the refrigerant gas is led out from the outlet may be parallel.
According to this configuration, even if the direction in which the refrigerant gas is led out from the outlet port does not coincide with the direction in which the refrigerant gas is introduced into the inlet port and is slightly deviated in a state of being parallel to each other, On the other hand, the refrigerant gas is led out from the outlet without changing the flowing direction of the refrigerant gas in the direction intersecting (orthogonal direction). Therefore, the refrigerant gas is led out of the separation space from the outlet without reducing the flow velocity in the separation space. And since the separation capability of the lubricating oil is ensured even if the outlet direction is deviated parallel to the inlet direction, the degree of freedom in selecting the position of the outlet port can be increased, and the oil separator in the refrigerant compressor can be increased. The arrangement can flexibly correspond to the structure of the refrigerant compressor.

The introduction port and the outlet port may be located on the same straight line, and the introduction direction of the refrigerant gas to the introduction port may coincide with the outlet direction of the refrigerant gas from the outlet port.
According to this configuration, since the refrigerant gas introduced into the separation space from the inlet port flows toward the outlet port, it is difficult to change the direction in which the refrigerant gas flows when turning around the turning portion. Since the flow rate of the refrigerant gas in the separation space decreases as the crossing angle with respect to the introduction direction to the inlet increases, it is possible to suppress a decrease in the flow rate of the refrigerant gas.

Further, a direction in which a straight line connecting the introduction port and the outlet port extends may coincide with an axial direction of the turning unit extending from the introduction port side to the outlet port side of the turning unit.
According to this configuration, the refrigerant gas flows toward the outlet port while turning around the turning portion, and the flow of the refrigerant gas flowing from the inlet port toward the outlet port coincides with the axial direction of the turning portion. For this reason, it becomes possible to flow the refrigerant gas to the outlet port along the swivel portion. Therefore, the refrigerant gas can be swung around the swivel portion while suppressing a decrease in the flow rate of the refrigerant gas, and the lubricating oil separation capability can be increased.

In addition, the oil separator may include a forced swirling unit that swirls the refrigerant gas spirally around the swivel portion along the axial direction of the swivel portion.
According to this configuration, the refrigerant gas can be spirally swirled along the axial direction of the swivel portion by the forced swirl means. For this reason, the refrigerant gas introduced into the separation space from the introduction port is further spirally swirled by the forced swirling means without reducing the flow velocity, so that the lubricating oil is more efficiently centrifuged from the refrigerant gas. To be separated.

Moreover, the said forced turning means may be comprised by the spiral groove extended spirally from the one end side along the axial direction of this turning part to the other end side in the surrounding surface of the said turning part.
According to this configuration, the refrigerant gas can be spirally swirled along the axial direction of the swivel portion only by forming the spiral groove in the swivel portion. That is, the refrigerant gas can be spirally rotated with a simple configuration, and the lubricating oil can be more efficiently centrifuged from the refrigerant gas.

Further, the forced turning means may be configured by a spiral passage that spirally extends from one end side to the other end side along the axial direction of the turning portion in the separation space.
According to this configuration, the refrigerant gas introduced into the separation space can only flow through the spiral passage. For this reason, the refrigerant gas can be reliably swirled around the swirling portion by the spiral passage, and the lubricating oil can be efficiently centrifuged from the refrigerant gas by the spiral passage.

  Further, the forced turning means is constituted by a guide hole that communicates with the introduction port, extends from the introduction port toward the separation space, and extends in a direction obliquely intersecting the axial direction of the turning portion. May be.

  According to this configuration, the refrigerant gas introduced into the separation space from the introduction port is guided toward the separation space by the guide hole. For this reason, the refrigerant gas swirls along the swirl portion spirally by flowing along the peripheral surface of the swirl portion. Therefore, the refrigerant gas can be spirally swirled with a simple configuration.

  ADVANTAGE OF THE INVENTION According to this invention, an oil separator can be made compact, ensuring the separation capability of lubricating oil.

  Hereinafter, an embodiment in which the present invention is embodied in a refrigerant compressor used in a refrigeration circuit of a vehicle air conditioner will be described in detail based on the drawings. In the following description, for the “upper”, “lower”, “front”, and “rear” of the refrigerant compressor 10, the direction of the arrow Y1 shown in FIG. 1 is the vertical direction, and the direction of the arrow Y2 is the front-back direction.

  FIG. 1 is a longitudinal sectional view of the refrigerant compressor 10. As shown in FIG. 1, the housing of the refrigerant compressor 10 includes a cylinder block 11, a front housing 12 joined and fixed to the front end of the cylinder block 11, and a valve / port forming body 13 at the rear end of the cylinder block 11. And a rear housing 14 joined and fixed thereto.

  A crank chamber 15 is defined between the cylinder block 11 and the front housing 12 in the housing. A drive shaft 16 is rotatably supported by the cylinder block 11 and the front housing 12 so as to pass through the crank chamber 15. The drive shaft 16 is operatively connected to an engine E, which is a travel drive source of the vehicle, via a clutchless type (always transmission type) power transmission mechanism PT. Accordingly, when the engine E is in operation, the drive shaft 16 is always rotated by receiving power from the engine E.

  In the crank chamber 15, a lug plate 17 is fixed to the drive shaft 16 so as to rotate together with the drive shaft 16, and a swash plate as a disc-shaped cam plate is formed in the crank chamber 15. 18 is housed. The drive shaft 16 is inserted through the central portion of the swash plate 18, and the swash plate 18 is supported on the drive shaft 16 so as to be integrally rotatable and tiltable. A hinge mechanism 19 is interposed between the lug plate 17 and the swash plate 18. The swash plate 18 can be rotated synchronously with the lug plate 17 and the drive shaft 16 by the hinge connection with the lug plate 17 via the hinge mechanism 19 and the support of the drive shaft 16. Can be tilted with respect to the drive shaft 16 while being slid in the axial direction (the direction of the central axis L).

  In the cylinder block 11, a plurality of cylinder bores 22 are formed in the front-rear direction at equal angular intervals around the central axis L of the drive shaft 16. The single-headed piston 23 is accommodated in each cylinder bore 22 so as to be movable in the front-rear direction. The front / rear opening of the cylinder bore 22 is closed by the front surface of the valve / port forming body 13 and the rear end surface of the piston 23, and the compression chamber 24 whose volume changes in accordance with the movement of the piston 23 in the front / rear direction in the cylinder bore 22. Is partitioned.

  Each piston 23 is anchored to the outer periphery of the swash plate 18 via a pair of shoes 25. Accordingly, when the swash plate 18 is rotated by the rotation of the drive shaft 16, the swash plate 18 is swung back and forth in the direction of the central axis L of the drive shaft 16. As the swash plate 18 swings, the piston 23 is linearly reciprocated back and forth. In this embodiment, the crank chamber 15, the drive shaft 16, the swash plate 18, the piston 23, and the like constitute a compression mechanism.

  In the housing, a suction chamber 26 and a discharge chamber 27 are respectively defined between the valve / port forming body 13 and the rear housing 14. The valve / port forming body 13 is formed with a suction port 28 and a suction valve 29 so as to be positioned between the compression chamber 24 and the suction chamber 26, respectively, and the compression chamber 24 and the discharge chamber 27. A discharge port 30 and a discharge valve 31 are formed so as to be positioned between the two.

  Carbon dioxide is used as the refrigerant gas for the refrigeration circuit. Refrigerant gas introduced into the suction chamber 26 from the external refrigerant circuit 41 (specifically, the outlet side of the evaporator 41a) of the refrigeration circuit moves from the top dead center position to the bottom dead center position side of each piston 23, and thereby the suction port. The air is sucked into the compression chamber 24 through the suction valve 28 and the suction valve 29. The refrigerant gas sucked into the compression chamber 24 is compressed to a predetermined pressure by the movement from the bottom dead center position of the piston 23 to the top dead center position side, and enters the discharge chamber 27 via the discharge port 30 and the discharge valve 31. Discharged.

  The rear housing 14 is formed with a connection passage 49 that connects the discharge chamber 27 and the external refrigerant circuit 41 (specifically, the inlet side of the gas cooler 41b). The refrigerant gas in the discharge chamber 27 is led to the external refrigerant circuit 41 via the connection passage 49. The refrigerant led out to the external refrigerant circuit 41 is cooled by the gas cooler 41b, depressurized by the expansion valve 41c, and then sent to the evaporator 41a for evaporation. In the present embodiment, the discharge chamber 27 and the connection passage 49 form a refrigerant gas discharge passage in the refrigerant compressor 10.

  As shown in FIG. 2, the rear housing 14 is formed with a housing hole 37 in the front-rear direction, which is a part of the connection passage 49 and forms a part of the discharge passage. A first pedestal 37a is formed inwardly on a substantially central peripheral surface in the front-rear direction of the housing hole 37, and has a smaller diameter than the first pedestal 37a on the rear side of the first pedestal 37a. A second pedestal 37b is formed. An oil separator 50 that separates lubricating oil contained in the refrigerant gas is disposed in the accommodation hole 37. The oil separator 50 communicates with the discharge chamber 27 and is connected to the inlet side of the gas cooler 41 b in the external refrigerant circuit 41 through the connection passage 49. Therefore, the refrigerant gas discharged from the discharge chamber 27 is supplied to the external refrigerant circuit 41 via the oil separator 50.

  As shown in FIG. 1, an extraction passage 32, an air supply passage 33, and a control valve 34 are provided in the housing of the refrigerant compressor 10. The extraction passage 32 connects the crank chamber 15 and the suction chamber 26. The air supply passage 33 connects the connection passage 49 (oil separator 50) serving as a discharge pressure region and the crank chamber 15 as a low pressure region lower than the connection passage 49. A control valve 34 is disposed in the supply passage 33.

  Then, by adjusting the opening degree of the control valve 34, the amount of high-pressure discharge gas introduced into the crank chamber 15 through the air supply passage 33 and the amount of gas discharged from the crank chamber 15 through the extraction passage 32. And the internal pressure of the crank chamber 15 is determined. The difference between the internal pressure of the crank chamber 15 and the internal pressure of the compression chamber 24 is changed in accordance with the change of the internal pressure of the crank chamber 15 and the inclination angle of the swash plate 18 is changed. As a result, the stroke of the piston 23, that is, the refrigerant compressor 10 discharge capacity is adjusted. That is, the refrigerant compressor 10 of the present embodiment is a variable capacity compressor that can vary the discharge capacity.

  For example, when the valve opening degree of the control valve 34 decreases, the internal pressure of the crank chamber 15 decreases. Therefore, the inclination angle of the swash plate 18 increases, the stroke of the piston 23 increases, and the discharge capacity of the refrigerant compressor 10 increases. On the contrary, when the valve opening degree of the control valve 34 increases, the internal pressure of the crank chamber 15 increases. Therefore, the inclination angle of the swash plate 18 is reduced, the stroke of the piston 23 is reduced, and the discharge capacity of the refrigerant compressor 10 is reduced.

Next, the oil separator 50 will be described.
As shown in FIG. 2, in the discharge passage, an oil separator 50 for separating lubricating oil from the refrigerant gas is disposed downstream of the discharge chamber 27 and upstream of the external refrigerant circuit 41. . The oil separator 50 includes a cylindrical case 51 that is press-fitted into the accommodation hole 37. In a state where the case 51 is press-fitted into the accommodation hole 37, the rear end of the case 51 abuts on the first pedestal 37a, and the rearward movement of the case 51 is restricted.

  A seal member 48 made of a rubber O-ring is mounted on the outer peripheral surface of the peripheral wall 51 a of the case 51 in order to suppress leakage of the refrigerant gas through the space between the accommodation hole 37 and the case 51. Further, an oil outlet 50b is formed in the lower portion of the peripheral wall 51a of the case 51 to allow the lubricating oil separated from the refrigerant gas to flow out of the case 51 (oil separator 50). The oil outlet 50b is connected to the control valve 34 through a passage 60 (see FIG. 1).

  Further, a turning member 52 as a turning portion is accommodated in the case 51, and a peripheral wall 51 a in the case 51 is disposed so as to surround the turning member 52 along the axial direction M. An annular separation space S is formed between the inner peripheral surface of the peripheral wall 51 a and the peripheral surface of the turning member 52. The swivel member 52 extends along the direction in which the refrigerant gas flows in the discharge passage (accommodating hole 37). The swivel member 52 is accommodated such that its axial direction M extends in the front-rear direction in the case 51, and the front end (one end) side of the swivel member 52 is disposed on the discharge chamber 27 side, which is the front end side of the case 51. The rear end (other end) side of the turning member 52 is disposed on the external refrigerant circuit 41 side which is the rear end side of the case 51. A spiral groove 52 a is formed on the circumferential surface of the turning member 52 so as to extend spirally from the front end (one end) side to the rear end (other end) side along the axial direction M of the turning member 52. The spiral groove 52 a constitutes a forced swirling means that swirls the refrigerant gas around the swivel member 52 along the axial direction M of the swivel member 52.

  The spiral groove 52a gradually decreases in the radial depth from the front end side to the rear end side of the turning member 52, and converges toward the axis of the turning member 52 on the rear end side. ing. Further, a flange portion 52b is formed at the rear end of the turning member 52, and a plurality (four in this embodiment) of outlet ports 52c (only three outlet ports 52c are shown in FIG. 2) are provided on the flange portion 52b. It is formed at intervals. The refrigerant gas introduced into the separation space S is led out of the separation space S from the outlet 52c. The refrigerant gas derivation direction Z1 from the derivation port 52c is the direction indicated by the arrow Z1 in FIG. 2, and the refrigerant gas derivation direction Z1 is from the front end (one end) side to the rear end (other end) side of the turning member 52. It is the same direction as the axial direction M.

  In the oil separator 50, a cylindrical lid member 54 is fitted on the front end of the case 51 through a stopper 53 and a variable throttle 55 as a throttle. The lid member 54 is formed with an inlet 54 a for introducing refrigerant gas into the case 51 (separation space S), and the inlet 54 a communicates with the discharge chamber 27 and the case 51. The four outlets 52c are formed so as to be displaced outwardly in the radial direction of the turning member 52 with respect to the inlet 54a. Each introduction port 54 a is disposed around the axis of the turning member 52. The refrigerant gas discharged into the discharge chamber 27 is introduced into the separation space S from the introduction port 54a. The introduction direction Z2 of the refrigerant gas from the introduction port 54a into the separation space S is the direction indicated by the arrow Z2 in FIG. 2, and the introduction direction Z2 of the refrigerant gas is from the front end (one end) side to the rear end ( The direction is the same as the axial direction M toward the other end. The stopper 53 has a cylindrical shape, and a communication port 53b that connects the introduction port 54a and the inside of the case 51 is formed at the center thereof. The refrigerant gas that has passed through the introduction port 54 a passes through the communication port 53 b and is introduced into the separation space S in the case 51.

  Further, the outer periphery of the variable throttle 55 is sandwiched between the outer periphery of the stopper 53 and the outer periphery of the lid member 54. The variable throttle 55 includes a plurality (two in the present embodiment) of throttle valves 55a having a lead shape. In the center of the front side of the stopper 53, a relief portion 53a that allows elastic deformation of the throttle valve 55a is recessed. As shown by a two-dot chain line in FIG. 2, the variable throttle 55 receives the refrigerant gas flow and both throttle valves 55a are elastically deformed to allow the refrigerant gas flow. Note that the variable throttle 55 increases the cross-sectional area of the refrigerant gas by increasing the amount of elastic deformation of each throttle valve 55a as the flow rate of the refrigerant gas increases, and each throttle valve by decreasing the flow rate of the refrigerant gas. Reducing the amount of elastic deformation of 55a reduces the passage cross-sectional area of the refrigerant gas. For this reason, when the flow rate of the refrigerant gas increases, the differential pressure between the upstream side and the downstream side of the variable throttle 55 becomes difficult to be applied, and when the flow rate of the refrigerant gas decreases, the differential pressure between the upstream side and the downstream side of the variable throttle 55 It becomes easy to stick.

  In the accommodation hole 37, a valve seat forming member 56 having a cylindrical shape is accommodated behind the case 51 (external refrigerant circuit 41 side), and a cylindrical shape is sandwiched around the outer periphery of the valve seat forming member 56. A member 57 is externally fitted. The outer peripheral portion of the check valve 58 is sandwiched between the outer peripheral portion of the valve seat forming member 56 and the outer peripheral portion of the clamping member 57. A valve hole 56 a is formed in the center of the valve seat forming member 56, and a peripheral portion of the valve hole 56 a in the valve seat forming member 56 is a valve seat 56 b on which the check valve 58 is seated. An escape portion 57 a that allows elastic deformation of the check valve 58 is formed on the front surface of the clamping member 57 that faces the valve seat forming member 56. 2, the check valve 58 is elastically deformed by receiving the refrigerant gas flow and allows the refrigerant gas to flow out of the separation space S, while entering the separation space S. The flow of the refrigerant gas is cut off. A gas outlet 57 b for refrigerant gas to the outside of the oil separator 50 is formed at the center of the clamping member 57, and the gas outlet 57 b communicates with the inside of the case 51, the valve hole 56 a, and the connection passage 49.

  The oil separator 50 is assembled with the case 51, the turning member 52, the stopper 53, the lid member 54, the variable throttle 55, the valve seat forming member 56, the clamping member 57, and the check valve 58. And accommodated in the accommodation hole 37. Specifically, the holding member 57, the check valve 58, the valve seat forming member 56, the case 51, the turning member 52, the stopper 53, the variable throttle 55, and the lid member 54 are arranged in the same order in the external refrigerant circuit of the accommodation hole 37. The oil separator 50 is configured by being housed in the 41 side.

  The oil separator 50 separates lubricating oil from refrigerant gas by centrifugation. In the oil separator 50, the introduction port 54 a is disposed at a position corresponding to the front end (one end) along the axial direction M of the swivel member 52, and corresponds to the rear end (other end) along the axial direction M. The outlet port 52c is disposed at a position where it is located. The axial direction M of the swivel member 52 is the same as the introduction direction Z2 of the refrigerant gas from the introduction port 54a into the separation space S and the discharge direction Z1 of the refrigerant gas from the discharge port 52c to the outside of the separation space S. The turning member 52 is sandwiched between the introduction port 54a and the outlet port 52c. The refrigerant gas lead-out direction Z1 is parallel to the refrigerant gas introduction direction Z2, and is also parallel to the axial direction M of the turning member 52.

  The passage 60 connected to the oil outlet 50b of the oil separator 50 is located on the air supply passage 33, and the oil separator 50 and the crank chamber 15 are communicated with each other via the air supply passage 33 (passage 60). Yes. The lubricating oil separated by the oil separator 50 is returned to the crank chamber 15 through the passage 60, that is, the air supply passage 33, together with the refrigerant gas supplied to the crank chamber 15 for capacity control. The control valve 34 is displaced in accordance with the difference between the upstream pressure (pressure in the discharge chamber 27) and the downstream pressure (pressure in the case 51) of the variable throttle 55. This differential pressure reflects the refrigerant flow rate in the refrigeration circuit.

  The refrigerant gas introduced from the discharge chamber 27 into the case 51 through the introduction port 54a is introduced into the separation space S after the flow rate is reduced by the variable restriction 55. In the case 51, the turning member 52 extends along the introduction direction Z2 of the refrigerant gas from the introduction port 54a into the separation space S. That is, since the axial direction M of the turning member 52 extends parallel to the introduction direction Z2 of the refrigerant gas from the introduction port 54a, the direction in which the refrigerant gas flows in a direction orthogonal to the introduction direction Z2 is changed. Without flowing in the separation space S along the axial direction M of the swivel member 52. The refrigerant gas flows along the swivel member 52, and is forcibly swirled by the spiral groove 52 a formed on the peripheral surface of the swivel member 52. Since the spiral groove 52 a is formed over the entire axial direction M of the turning member 52, the refrigerant gas turns spirally over the entire axial direction M of the turning member 52.

  The lubricating oil is separated from the refrigerant gas spirally turning in the separation space S along the spiral groove 52a of the turning member 52 by the centrifugal separation action, and the separated lubricating oil is the inner peripheral surface of the peripheral wall 51a of the case 51. Adhere to. Thereafter, the lubricating oil adhering to the peripheral wall 51a flows down by its own weight, flows out of the case 51 (oil separator 50) from the oil outlet 50b together with the refrigerant gas, and is shared with the control valve 34 and the crank chamber 15 through the passage 60. The

  On the other hand, the refrigerant gas from which the lubricating oil is separated flows toward the outlet port 52c, but the refrigerant gas outlet direction Z1 from the outlet port 52c is the same as the refrigerant gas inlet direction Z2 to the inlet port 54a. An introduction port 54a and a discharge port 52c are arranged at the top. Therefore, when the refrigerant gas flows toward the outlet port 52c, the refrigerant gas flows without changing the flow direction in a direction different from the direction of introduction into the inlet port 54a, and is directly led out of the separation space S from the outlet port 52c. . Thereafter, the refrigerant gas derived from the outlet 52 c is supplied to the external refrigerant circuit 41 through the connection passage 49.

According to the above embodiment, the following effects can be obtained.
(1) The oil separator 50 has a refrigerant gas inlet 54a at a position corresponding to the front end (one end) along the axial direction M of the revolving member 52, and the rear end (other end) along the axial direction M. And a refrigerant gas outlet 52c at a position corresponding to. Then, the inlet 54a and the outlet are arranged so that the introduction direction Z2 of the refrigerant gas from the inlet 54a into the separation space S and the outlet direction Z1 of the refrigerant gas from the outlet 52c to the outside of the separation space S are the same direction. 52c is arranged. For this reason, the refrigerant gas introduced into the separation space S from the introduction port 54a flows to the outlet port 52c while turning along the axial direction M of the turning member 52, and from the outlet port 52c without changing the flowing direction. Derived outside the separation space S. Therefore, the refrigerant gas can be prevented from flowing in a direction orthogonal to the introduction direction as in the background art, and a decrease in the flow rate of the refrigerant gas can be suppressed. As a result, in order to compensate for a decrease in the lubricating oil separation capability due to a decrease in the flow rate of the refrigerant gas, it is necessary to lengthen the turning member 52 in order to ensure a long turning distance of the refrigerant gas or to secure a long introduction distance of the refrigerant gas. The oil separator 50 can be made compact.

  (2) The four outlets 52c are arranged around the axis of the inlet 54a, and the refrigerant gas introduction direction Z2 to the inlet 54a and the refrigerant gas outlet directions Z1 from the outlets 52c Are parallel. Then, the refrigerant gas introduced into the separation space S from the inlet 54a flows to each outlet 52c while turning along the axial direction M of the turning member 52, and is led out from the outlet 52c. Here, the derivation direction Z1 of the refrigerant gas from the derivation port 52c does not coincide with the introduction direction Z2 of the refrigerant gas to the introduction port 54a, but from the derivation port 52c without changing the direction in which the refrigerant gas flows in the separation space S. Derived. Therefore, the refrigerant gas does not decrease the flow velocity in the separation space S, and the lubricating oil is efficiently separated. That is, if the refrigerant gas outlet direction Z1 and the inlet direction Z2 are the same direction, the lubricating oil can be efficiently separated. Therefore, the position of the outlet 52c may be arbitrarily changed, and the position of the outlet 52c may be changed. This makes it possible to flexibly correspond to the structure of the refrigerant compressor 10 in the arrangement of the oil separator 50 in the refrigerant compressor 10.

  (3) In the oil separator 50, the oil outlet 50b is formed in the peripheral wall 51a of the case 51 to which the lubricating oil centrifuged from the refrigerant gas will adhere. The lubricating oil adhering to the peripheral wall 51a flows down toward the oil outlet 50b by its own weight and flows out of the oil separator 50 from the oil outlet 50b. Therefore, for example, as in the case where the oil outlet 50b is formed not in the peripheral wall 51a but in the flange portion 52b in which the outlet port 52c is formed, the lubricating oil adhering to the peripheral wall 51a rides on the flow of the refrigerant gas and the flange portion There is no need to move along 52b. As a result, the lubricating oil can be quickly flowed out of the oil separator 50, and as a result, the compression mechanism and the like can be quickly lubricated.

  (4) The lubricating oil centrifuged by the oil separator 50 flows out of the oil separator 50 from the oil outlet 50 b without accumulating in the oil separator 50. Therefore, it is possible to suppress the lubricating oil centrifuged by the oil separator 50 from being taken out to the external refrigerant circuit 41 together with the refrigerant gas.

(5) Moreover, since it is not necessary to provide the structure for storing lubricating oil in the oil separator 50, the oil separator 50 can be made further compact.
(6) A spiral groove 52 a for spirally swirling the refrigerant gas along the peripheral surface of the swing member 52 is formed on the peripheral surface of the swing member 52. For this reason, the refrigerant gas introduced into the separation space S is forcibly swirled along the flowing direction. Therefore, in the oil separator 50, in addition to suppressing the decrease in the flow rate of the refrigerant gas, the ability to separate the lubricating oil from the refrigerant gas can be enhanced by forcibly turning the refrigerant gas in a spiral shape.

  (7) The oil separator 50 includes a case 51, a turning member 52, a stopper 53, a lid member 54, a variable throttle 55, a valve seat forming member 56, a clamping member 57, and a check valve 58. It is assembled and assembled. Each member is arranged in parallel along the direction in which the refrigerant gas is introduced into the oil separator 50. Therefore, for example, unlike the background art in which the inner cylinder extends in a direction orthogonal to the direction in which the refrigerant gas flows, the entire oil separator 50 can be made compact. Moreover, since the oil separator 50 is comprised only by assembling each member in the accommodation hole 37 in a predetermined order, the oil separator 50 can be easily provided in the refrigerant compressor 10.

  (8) In the oil separator 50, the turning member 52 and the outlet 52c are arranged in parallel along the refrigerant gas introduction direction Z2 into the separation space S, and the variable throttle 55 and the check valve 58 are also arranged in parallel. Yes. Therefore, for example, as compared with the case where the variable throttle 55 and the check valve 58 cannot be assembled integrally with the oil separator 50 as in the configuration in which the refrigerant gas flows in a direction orthogonal to the refrigerant gas introduction direction Z2. The oil separator 50 can be made compact.

(Second Embodiment)
Next, a second embodiment in which the present invention is embodied in a refrigerant compressor used in a refrigeration circuit of a vehicle air conditioner will be described in detail with reference to the drawings. Note that in the second embodiment described below, the same components as those in the first embodiment described above are denoted by the same reference numerals, and redundant description thereof is omitted or simplified.

  As shown in FIGS. 3 and 4, a bottom 65 is integrally formed on the rear side of the case 51 constituting the oil separator 50. A protrusion 66 extending in a columnar shape toward the front side of the case 51 protrudes from the bottom portion 65, and the protrusion 66 constitutes a turning portion around which the refrigerant gas turns. Further, a separation space S is defined between the protrusion 66 and the peripheral wall 51a. As shown in FIGS. 4A and 4B, a recess 66 a is formed at the front end of the protrusion 66. In addition, a guide portion 66b that communicates with the concave portion 66a and is inclined obliquely from the front side to the rear side of the projection 66 is formed at the front portion of the projection 66. In the case 51, a spiral passage 67 is formed between the projection 66 and the peripheral wall 51a, and communicates with the recess 66a and the guide portion 66b and extends spirally along the circumferential direction of the projection 66. . The spiral passage 67 constitutes forced swirling means for forcibly swirling the refrigerant gas along the swirl member 52 in a spiral shape. In addition, on the rear end side of the protrusion 66, an outlet 68 for leading the refrigerant gas out of the separation space S is formed in the bottom 65.

  In the second embodiment, the protrusion 66 has an axial direction M in which the refrigerant gas is introduced from the introduction port 54a into the separation space S in the introduction direction Z2 and from the outlet 68 to the outside of the separation space S. The turning member 52 is disposed so as to extend in the same direction as the lead-out direction Z1, and the turning member 52 is sandwiched between the introduction port 54a and the lead-out port 68. Further, the refrigerant gas derivation direction Z1 and the refrigerant gas introduction direction Z2 coincide with each other, and the derivation direction Z1 and the introduction direction Z2 also coincide with the axial direction M of the protrusion 66.

  In the second embodiment, the refrigerant gas introduced into the separation space S from the introduction port 54a is guided to flow toward the rear side of the separation space S from the recess 66a by the guide portion 66b, and enters the spiral passage 67. Derived. Then, the refrigerant gas flows along the spiral passage 67 to forcibly swirl around the protrusion 66, and the lubricating oil is separated from the refrigerant gas swirling the spiral passage 67 by a centrifugal separation action. The

Therefore, according to the second embodiment, the following effects can be obtained in addition to the same effects as (1) to (8) of the first embodiment.
(9) In the second embodiment, the spiral passage 67 is formed in the case 51, and the refrigerant gas can be more reliably swirled in the spiral shape by the spiral passage 67. Therefore, the ability to separate the lubricating oil from the refrigerant gas can be increased.

(Third embodiment)
Next, a third embodiment in which the present invention is embodied in a refrigerant compressor used in a refrigeration circuit of a vehicle air conditioner will be described in detail with reference to the drawings. Note that in the third embodiment described below, the same components as those in the first embodiment described above are denoted by the same reference numerals, and redundant description thereof is omitted or simplified.

  As shown in FIG. 5, a bottom forming member 70 is assembled integrally with the case 51 on the rear side of the case 51 constituting the oil separator 50. The bottom forming member 70 includes a bottom plate 71 having a disc shape and a cylindrical tube portion 72 projecting from the bottom plate 71. In the state where the bottom forming member 70 is assembled to the case 51, the cylindrical portion 72 protrudes toward the front side of the case 51, and the cylindrical portion 72 constitutes a swivel portion around which the refrigerant gas turns. ing. A gas passage 72 a is formed inside the cylindrical portion 72. A pair of through holes 72b are formed in the cylinder portion 72 so as to face each other, and each through hole 72b communicates with the gas passage 72a. Further, a refrigerant gas outlet 72c is formed at the rear end of the cylindrical portion 72 and at the rear end of the gas passage 72a, and the inlet 54a and the outlet 72c are located on the same straight line. A separation space S is formed between the cylindrical portion 72 and the peripheral wall 51a.

  A lid 73 is integrally formed on the front side of the case 51, and a guide hole 74 that penetrates the lid 73 in the thickness direction (front-rear direction) is formed in the lid 73. The guide hole 74 is formed to extend obliquely from the center of the lid portion 73 toward the edge, and the extending direction is inclined with respect to the axial direction M of the cylindrical portion 72. Further, the guide hole 74 opens toward the separation space S that is outside the cylindrical portion 72. The guide hole 74 constitutes a forced turning means for forcibly turning the refrigerant gas in a spiral shape along the cylindrical portion 72.

  In the third embodiment, the cylindrical portion 72 has an axial direction M in which the refrigerant gas is introduced from the introduction port 54a into the separation space S and the refrigerant gas is introduced from the outlet 72c to the outside of the separation space S. The lead-out direction Z1 is arranged to extend in the same direction. Also, the refrigerant gas lead-out direction Z1 and the refrigerant gas introduction direction Z2 are the same direction, and the direction in which the straight line connecting the introduction port 54a and the discharge port 72c extends and the axial direction M of the cylindrical portion 72 coincide. ing.

  The refrigerant gas introduced into the separation space S from the introduction port 54 a is guided by the guide holes 74 so as to flow toward the rear side of the separation space S. Then, the refrigerant gas flows along the cylindrical portion 72, and is forced to spiral around the cylindrical portion 72. Then, from the refrigerant gas swirling in the separation space S, the lubricating oil is separated by a centrifugal separation action, and the refrigerant gas from which the lubricating oil has been separated flows from the through hole 72b located in the middle of the swirling to the gas passage 72a, The gas passage 72a is led out of the separation space S through the outlet 72c.

Therefore, according to the third embodiment, the following effects can be obtained in addition to the same effects as (1) to (8) of the first embodiment.
(10) In the third embodiment, the refrigerant gas can be spirally swirled by forming the guide hole 74 obliquely. Therefore, the refrigerant gas can be spirally swirled with a simple configuration.

Each embodiment may be changed as follows.
In the above embodiment, the refrigerant compressor 10 is embodied as a swash plate type variable displacement type, but may be a wobble type variable displacement type provided with a swing plate as a cam plate.

In the above embodiment, the refrigerant compressor 10 is embodied as a variable capacity type, but may be a fixed capacity type.
In the above embodiment, the refrigerant compressor 10 is a piston type, but may be a scroll type or a vane type.

In the above embodiment, carbon dioxide is used as the refrigerant gas, but chlorofluorocarbon (for example, R134a) may be used as the refrigerant.
In the above embodiment, the refrigerant compressor 10 is a single-head piston type, but it may be a double-head piston type.

  In the first embodiment, the variable throttle 55 and the check valve 58 in the oil separator 50 may be omitted, and the oil separator 50 may be configured by the lid member 54, the turning member 52, and the case 51.

In the above embodiment, the variable stop 55 is embodied as the stop, but it may be a fixed stop.
In the above embodiment, the lubricating oil separated by the oil separator 50 is returned to the crank chamber 15, but the lubricating oil separated by the oil separator 50 may be returned to the suction chamber 26.

  In the above embodiment, the lubricating oil separated by the oil separator 50 is returned to the crank chamber 15, but the lubricating oil separated by the oil separator 50 may be stored in an oil reservoir. In this case, for example, in the above embodiment, the upstream side of the air supply passage 33 is connected to the discharge passage outside the oil separator 50 and downstream of the variable throttle 55 (for example, the check valve space 37a).

Next, the technical idea that can be grasped from the above embodiment and other examples will be described below.
(1) The oil separator includes a throttle arranged in parallel on the downstream side of the introduction port along the introduction direction of the refrigerant gas from the introduction port to the separation space, and further arranged in parallel on the downstream side of the swivel unit. The refrigerant compressor according to any one of claims 1 to 8, further comprising a check valve.

  (2) The oil separator includes an inlet for introducing the refrigerant gas into the separation space and an outlet for the refrigerant gas to the outside of the separation space, and is arranged along the direction of introduction of the refrigerant gas into the inlet. The refrigerant compressor according to any one of claims 1 to 8, wherein an axial direction of the swivel member extends, and a refrigerant gas outlet direction from the outlet port extends along the introduction direction.

The longitudinal section showing the refrigerant compressor of a 1st embodiment. The expanded sectional view showing the oil separator of a 1st embodiment. The expanded sectional view which shows the oil separator of 2nd Embodiment. (A) is a perspective view which shows the helical channel | path in the oil separator of 2nd Embodiment, (b) is the 4b-4b sectional view taken on the line of Fig.4 (a). The expanded sectional view which shows the oil separator of 3rd Embodiment. Sectional drawing which shows the oil separator of background art. Sectional drawing which shows the oil separator of background art.

Explanation of symbols

  M ... axial direction, S ... separation space, Z1 ... lead-out direction, Z2 ... introduction direction, 10 ... refrigerant compressor, 15 ... crank chamber constituting the compression mechanism, 16 ... drive shaft constituting the compression mechanism, 18 ... compression mechanism 23... Piston constituting the compression mechanism 27. Discharge chamber constituting the discharge passage 49. Connection passage constituting the discharge passage 50. Oil separator 50 b Oil outlet 51 a Circumferential wall 52 ... turning member constituting the turning part, 52a ... spiral groove as forced turning means, 52c, 68, 72c ... outlet port, 54a ... introducing port, 66 ... projection forming the turning part, 67 ... as forced turning means A spiral passage, 72... A cylindrical portion constituting the turning portion, 74... A guide hole as a forced turning means.

Claims (8)

Refrigerant gas is compressed by the operation of the compression mechanism, and has a swivel portion and a peripheral wall surrounding the swivel portion along the axial direction of the swivel portion on the discharge passage of the compressed refrigerant gas, and the swivel portion An oil separator that separates the lubricating oil contained in the refrigerant gas by swirling the refrigerant gas along the swirl portion in the separation space; In the refrigerant compressor in which the peripheral wall is provided with an oil outlet for allowing the lubricating oil separated from the refrigerant gas to flow out of the oil separator,
The oil separator includes a refrigerant gas inlet to the separation space and a refrigerant gas outlet to the outside of the separation space, and the swivel portion is disposed between the inlet and the outlet. A refrigerant characterized in that the introduction port and the outlet port are arranged so that the direction in which the refrigerant gas is led out from the outlet port is the same as the direction in which the refrigerant gas is introduced into the inlet port. Compressor. 2. The refrigerant compressor according to claim 1, wherein a direction in which the refrigerant gas is introduced into the inlet and a direction in which the refrigerant gas is led out from the outlet are parallel to each other. 2. The inlet port and the outlet port are located on the same straight line, and a direction in which the refrigerant gas is introduced into the inlet port coincides with a direction in which the refrigerant gas is led out from the outlet port. The refrigerant compressor described in 1. 4. The refrigerant according to claim 3, wherein a direction in which a straight line connecting the introduction port and the discharge port extends and an axial direction of the swivel portion that extends from the introduction port side to the discharge port side of the swivel unit coincide with each other. Compressor. The refrigerant compressor according to any one of claims 1 to 4, wherein the oil separator includes forced swirling means that swirls the refrigerant gas spirally around the swirl portion along the axial direction of the swirl portion. . 6. The refrigerant compressor according to claim 5, wherein the forced swirl means is configured by a spiral groove that spirally extends from one end side to the other end side along the axial direction of the swivel portion on a circumferential surface of the swivel portion. . The refrigerant compressor according to claim 5, wherein the forced swirling unit is configured by a spiral passage that spirally extends from one end side to the other end side along the axial direction of the swivel portion in the separation space. The forced swivel means is constituted by a guide hole that communicates with the introduction port, extends from the introduction port toward the separation space, and extends in a direction obliquely intersecting the axial direction of the swivel unit. Item 6. The refrigerant compressor according to Item 5.

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