JP2008069698A - Oil return structure in refrigerant compressor - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide an oil return structure in a refrigerant compressor capable of improving the designing flexibility on the shape of an oil guide passage. <P>SOLUTION: A swash plate compressor 10 comprises an oil storage chamber 63 for storing lubricant oil separated in an oil separation chamber in a communication passage communicating a discharge chamber with an intake chamber. The oil storage chamber 63 and the intake chamber is communicated by an oil return passage constituting a part of the communication passage. The oil guide passage 41A which is a part of the oil return passage is formed in a sealing area of a gasket 41 for sealing the top end face 35a of a pedestal 35 and the bottom end face 40a of a muffler forming member 40. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

  The present invention relates to an oil return structure in a refrigerant compressor.

  In the swash plate type compressor (refrigerant compressor) disclosed in Patent Document 1, lubricating oil is mixed in the refrigerant gas, and the lubricating oil flows into each sliding portion as the refrigerant gas flows in the swash plate type compressor. The sliding portion is lubricated by being used in the above. A part of the lubricating oil mixed in the refrigerant gas is separated from the refrigerant gas by inertia or the like in the swash plate chamber. As shown in FIG. 13, the lubricating oil separated from the refrigerant gas is dropped and stored in an oil reservoir chamber 91 provided below the swash plate chamber in the lower part of the housing 90.

  The oil reservoir chamber 91 communicates with a suppression chamber 92 in the suction pressure region provided in the housing 90 via an oil guide passage 93. The restraint chamber 92 is divided on the housing 90 by a partition wall 95 facing each other on a mating surface 98a of a pair of cylinder blocks 98 (only one cylinder block 98 is shown in FIG. 13) constituting the housing 90. A gasket (not shown) is interposed between the mating surfaces 98a, and both the suppression chambers 92 are communicated with each other through a through hole 97 provided in the partition wall 95.

During the operation of the swash plate compressor, when the refrigerant gas passes through the suppression chamber 92 in the suction pressure region, a pressure difference occurs between the pressure in the swash plate chamber and the pressure in the through hole 97 due to the throttling action in the through hole 97. . Then, the lubricating oil stored in the oil reservoir 91 flows into the through hole 97 through the oil guide passage 93 and is introduced into the swash plate chamber together with the refrigerant gas sucked into the swash plate chamber from the suppression chamber 92. As a result, lubricating oil is provided to each sliding portion to be lubricated.
JP-A-9-287469

  However, in the swash plate compressor disclosed in Patent Document 1, the oil guide passage 93 is formed in a gasket so as to follow the mating surface 98a of the cylinder block 98 forming a pair. The mating surface 98a is a part that requires a high sealing performance in order to prevent the refrigerant gas from leaking out of the machine. Further, the mating surface 98a has a very narrow width. The oil guide passage 93 is formed at a position corresponding to the mating surface 98a in the gasket, and further, the seal width is secured to ensure the sealing performance at the mating surface 98a. The shape of 93 is limited to a certain shape.

  The present invention has been made in view of the above-described conventional problems, and an object of the present invention is to provide an oil return structure in a refrigerant compressor that can increase the degree of design freedom regarding the shape of the oil guide passage.

  In order to solve the above problems, the invention according to claim 1 is provided with an oil separation chamber for separating lubricating oil from the discharged refrigerant gas in a discharge pressure region, and a muffler for the discharged refrigerant gas. An oil return structure in a refrigerant compressor in which a muffler forming member forming a chamber is connected to a side outer surface or a lower outer surface of a housing, and a sealing gasket is interposed between the housing and the muffler forming member, An oil storage chamber for storing the lubricating oil separated in the oil separation chamber is provided on a communication passage communicating the discharge pressure region and a low pressure region lower than the discharge pressure region, and the oil storage chamber and the low pressure region are provided. The oil return passage that constitutes a part of the communication passage communicates, and the oil guide passage that is a part of the oil return passage is connected to the housing and the muffler forming member in the gasket. And summarized in that formed in the sealing region of the surface.

  The invention according to claim 2 is provided with an oil separation chamber for separating lubricating oil from the discharged refrigerant gas in a discharge pressure region, and a muffler forming member that forms a muffler chamber for the discharged refrigerant gas is a housing. An oil return structure in a refrigerant compressor connected to an upper outer surface of the compressor and having a sealing gasket interposed between the housing and the muffler forming member, wherein the discharge pressure region and a low pressure lower than the discharge pressure region An oil storage chamber for storing the lubricating oil separated in the oil separation chamber is provided on the communication passage communicating with the region, and the oil storage chamber and the low pressure region are provided by an oil return passage that constitutes a part of the communication passage. The gist of the invention is that an oil guide passage which is part of the oil return passage is formed in a seal region of the mating surface of the housing and the muffler forming member in the gasket. .

  According to the invention described in claim 1 or claim 2, the seal region of the gasket is a region corresponding to the mating surface of the housing and the muffler forming member, and the mating surface is widely secured in the housing and the muffler forming member. Therefore, the width (area) of the seal region is wider than the cylinder block mating surface in the background art. For this reason, the oil guide passage that can be formed in the seal region of the gasket has a higher degree of design freedom with respect to its shape than the background art. As a result, the passage width of the oil guide passage can be increased, and a sufficient seal width can be secured even if the oil guide passage is formed. As a result, it is possible to suppress foreign matter clogging caused by the passage width being too narrow and leakage of the refrigerant gas to the outside caused by insufficient seal width.

  The oil return passage includes an oil discharge passage communicating the oil storage chamber and the oil guide passage, an oil supply passage communicating the oil guide passage and the low pressure region, and the oil guide passage. The oil discharge passage may have an inlet communicating with the bottom side of the oil storage chamber and an outlet communicating with the oil guide path above the inlet.

  According to this configuration, the oil storage chamber and the oil guide passage are communicated by the oil discharge passage that extends from the bottom side to the upper side of the oil storage chamber. Since the lubricating oil stored in the oil storage chamber always flows into the oil discharge passage, the oil storage chamber and the oil guide passage are sealed with the lubricating oil in the oil discharge passage. Therefore, the refrigerant gas in the discharge pressure region is prevented from being led out from the oil storage chamber to the low pressure region via the oil return passage (oil supply passage).

  The oil guide passage functions as a throttle passage in the oil return passage. According to this configuration, the lubricating oil supplied from the oil storage chamber to the low pressure region can be depressurized when passing through the oil guide passage. And since lubricating oil is cooled with pressure reduction, the viscosity fall of lubricating oil accompanying high temperature can be prevented, and the fall of the cooling effect of a sliding part can be suppressed. In addition, since the oil guide passage functions as a throttle passage, the amount of lubricating oil supplied from the oil storage chamber to the low pressure region via the oil guide passage compared to the case where the oil guide passage is not provided with a throttle passage. And the excessive supply of lubricating oil to the low pressure region can be prevented.

  Further, the oil guide passage may be formed so as to surround the oil storage chamber in the seal region. Alternatively, the oil guide passage may be formed so as to extend in a folded state over a plurality of times in the seal region. According to this configuration, it is possible to ensure a long passage length of the oil guide passage, and to effectively exhibit the throttling function of the oil guide passage.

  ADVANTAGE OF THE INVENTION According to this invention, the design freedom regarding the shape of an oil guide path can be raised.

  Hereinafter, an embodiment in which the oil return structure in the refrigerant compressor of the present invention is embodied as an oil return structure in a swash plate compressor will be described with reference to FIGS. In the following description, “front” and “rear” of the swash plate compressor 10 have the direction of the arrow Y1 shown in FIG. 1 as the front-rear direction, and “upper” and “lower” indicate the directions of the arrow Y2 shown in FIG. The vertical direction.

  As shown in FIG. 1, the housing of the swash plate compressor 10 is joined to a cylinder block 11 having a cylindrical shape, a front housing 12 having a covered cylinder fixedly joined to the front end thereof, and a rear end of the cylinder block 11. The rear housing 14 has a fixed bottomed cylindrical shape. An intake valve forming plate 36, a valve plate 13, a discharge valve forming plate 28, and a retainer 33 are interposed between the cylinder block 11 and the rear housing 14 from the cylinder block 11 side to the rear housing 14 side. ing.

  A control pressure chamber 15 is defined between the cylinder block 11 and the front housing 12, and a rotating shaft 16 can rotate in the cylinder block 11 and the front housing 12 so as to penetrate the control pressure chamber 15. It is supported by. The front end portion (one end portion) of the rotating shaft 16 is operatively connected to the engine E of the vehicle, and the rotating shaft 16 is rotated by the driving force of the engine E. The front side of the rotary shaft 16 is inserted into a shaft hole 12 b formed in the front housing 12 and is rotatably supported by the front housing 12 by a radial bearing 18. The rear side of the rotating shaft 16 is inserted into a shaft hole 11 b formed in the cylinder block 11 and is rotatably supported by the cylinder block 11 by a radial bearing 19.

  In the control pressure chamber 15, a rotary support 22 is fixed to the rotary shaft 16, and the rotary support 22 is fixed to the rotary shaft 16 so as to be integrally rotatable. A thrust bearing 23 is provided between the rotary support 22 and the inner wall surface of the front housing 12. A swash plate 24 is accommodated in the control pressure chamber 15. An insertion hole 24a is formed in the center of the swash plate 24, and the rotary shaft 16 is inserted through the insertion hole 24a. A hinge mechanism 25 is interposed between the rotary support 22 and the swash plate 24. The swash plate 24 can be rotated synchronously with the rotary shaft 16 and the rotary support 22 by the hinge connection with the rotary support 22 via the hinge mechanism 25 and the support of the rotary shaft 16 via the insertion hole 24a. In addition, the tilt angle can be changed with respect to the rotation shaft 16 while being slid in the axial direction along the central axis of the rotation shaft 16.

  In the cylinder block 11, a plurality of cylinder bores 26 (only one cylinder bore 26 is shown in FIG. 1) are formed through the rotation shaft 16 in the front-rear direction at equal angular intervals. A single-headed piston 27 is accommodated in the cylinder bore 26 so as to be movable in the front-rear direction. The front and rear openings of the cylinder bore 26 are closed by the valve plate 13 and the piston 27, and a compression chamber 37 whose volume changes in accordance with the movement of the piston 27 in the front and rear direction is defined in the cylinder bore 26. The piston 27 is anchored to the outer peripheral portion of the swash plate 24 via a pair of shoes 29.

  In the rear housing 14, facing the valve plate 13, a suction chamber 30 as a suction pressure region and a discharge chamber 31 as a discharge pressure region are defined. Specifically, the suction chamber 30 is provided in the center of the rear housing 14, and the discharge chamber 31 is provided on the outer peripheral side of the suction chamber 30. In the valve plate 13, suction ports 32 are formed radially inward of the valve plate 13 and discharge ports 34 are formed radially outward of the valve plate 13 at positions facing the respective cylinder bores 26. .

  The suction valve forming plate 36 is formed with a suction valve 36 a that opens and closes the suction port 32 at a position corresponding to the suction port 32. Further, the suction valve forming plate 36 is formed with a discharge hole 36 b at a position corresponding to the discharge port 34. The discharge valve forming plate 28 is formed with a discharge valve 28 a that opens and closes the discharge port 34 at a position corresponding to the discharge port 34. The discharge valve forming plate 28 is formed with a suction hole 28 b at a position corresponding to the suction port 32. The opening position of the discharge valve 28a is regulated by the retainer 33. A capacity control valve 45 composed of an electromagnetic valve is assembled to the rear housing 14.

  A pedestal 35 is integrally formed on the upper portion of the cylinder block 11. As shown in FIG. 6, the upper end surface 35a of the pedestal 35 (the upper outer surface of the cylinder block 11) is flat. 2, 5, and 6, a later-described oil storage chamber 63 is recessed inside the pedestal 35, and as shown in FIG. 4, a plan view is formed around the upper opening of the oil storage chamber 63. A square annular upper end surface 35a is formed. The upper end surface 35a of the base 35 is formed so as to extend wide along the circumferential direction.

  As shown in FIG. 1, a muffler forming member 40 is fixed to the upper end surface 35 a of the pedestal 35 via a gasket 41 for sealing, and the muffler forming member 40 and the gasket 41 are fastened and fixed to the pedestal 35 with screws 42. (See FIG. 4). As shown in FIGS. 3 and 6, the gasket 41 has a rectangular plate shape, and is configured by baking rubber layers 412 and 413 on both surfaces of a metal plate 411 as a core material.

  As shown in FIG. 1, the muffler forming member 40 is formed in a covered box shape and is formed to open downward. Further, the lower end surface 40a of the muffler forming member 40 has a quadrangular annular shape and is formed in substantially the same shape as the upper end surface 35a of the pedestal 35. That is, the lower end surface 40a of the muffler forming member 40 is formed so as to extend wide along the circumferential direction. For this reason, when the muffler forming member 40 is fixed to the upper end surface 35 a of the pedestal 35, the upper end surface 35 a of the pedestal 35 and the lower end surface 40 a of the muffler forming member 40 are matched.

  In the state where the muffler forming member 40 is fixed to the pedestal 35 via the gasket 41, the muffler chamber 43 is defined between the gasket 41 and the space inside the muffler forming member 40. Further, by tightening the muffler forming member 40 with the screw 42, the upper end surface 35a of the pedestal 35 and the lower end surface 40a of the muffler forming member 40 become mating surfaces, and the upper end surface 35a and the lower end surface 40a are pressed against the gasket 41. Thus, the upper end surface 35a and the lower end surface 40a are sealed (sealed). Therefore, refrigerant leakage from between the base 35 and the muffler forming member 40 is suppressed.

  A discharge passage 44 is formed in the pedestal 35 and the rear housing 14, and a through hole 41 a is formed through the gasket 41 in the plate thickness direction of the gasket 41 (see FIG. 4). The discharge passage 44 is formed so as to communicate with the through hole 41a of the gasket 41, and the muffler chamber 43 and the discharge chamber 31 communicate with each other through the discharge passage 44 and the through hole 41a. The muffler chamber 43 is connected to the external refrigerant circuit 50. A heat exchanger 51 for removing heat from the refrigerant, an expansion valve 52, and a heat exchanger 53 for transferring ambient heat to the refrigerant are interposed on the external refrigerant circuit 50.

  During operation of the swash plate compressor 10, the refrigerant gas in the suction chamber 30 passes through the suction hole 28 b and the suction port 32 as the piston 27 moves, and is sucked into the compression chamber 37 by pushing away the suction valve 36 a. . The refrigerant gas sucked into the compression chamber 37 is compressed in the compression chamber 37 by the movement of the piston 27. The refrigerant gas compressed in the compression chamber 37 passes through the discharge hole 36 b and the discharge port 34 from the compression chamber 37, pushes out the discharge valve 28 a, and is discharged into the discharge chamber 31. The high-pressure refrigerant gas discharged to the discharge chamber 31 is led to the external refrigerant circuit 50 through the discharge passage 44, the through hole 41 a and the muffler chamber 43. When the high-pressure refrigerant gas is led to the muffler chamber 43, the pressure pulsation component is attenuated by the expansion type muffler function of the muffler chamber 43. Further, the return gas from the external refrigerant circuit 50 is sucked into the suction chamber 30, and the swash plate compressor 10 of this embodiment forms a refrigerant circulation circuit with the external refrigerant circuit 50.

  Further, the swash plate compressor 10 is provided with a supply passage 54 for communicating the discharge chamber 31 with the control pressure chamber 15 and supplying the refrigerant gas in the discharge chamber 31 to the control pressure chamber 15 as a control gas. It has been. The capacity control valve 45 is provided on the supply passage 54. Further, the swash plate compressor 10 is provided with a discharge passage 55 that allows the control pressure chamber 15 and the suction chamber 30 to communicate with each other and discharges the refrigerant gas in the control pressure chamber 15 to the suction chamber 30 as a control gas. The refrigerant gas discharged into the discharge chamber 31 passes through the supply passage 54 and is supplied to the control pressure chamber 15. The capacity control valve 45 adjusts the amount of refrigerant gas that passes through the supply passage 54 and is supplied to the control pressure chamber 15.

  The refrigerant gas in the control pressure chamber 15 is discharged to the suction chamber 30 through the discharge passage 55. The balance between the refrigerant gas supply amount to the control pressure chamber 15 via the supply passage 54 and the refrigerant gas discharge amount from the control pressure chamber 15 via the discharge passage 55 is controlled to determine the pressure in the control pressure chamber 15. (The control pressure chamber 15 is regulated). When the pressure in the control pressure chamber 15 is changed, the differential pressure between the control pressure chamber 15 and the cylinder bore 26 via the piston 27 is changed, and the inclination angle of the swash plate 24 is changed. As a result, the stroke of the piston 27 (discharge capacity of the swash plate compressor 10) is adjusted.

  In the swash plate compressor 10, an oil separation chamber 49 having a diameter larger than that part of the discharge passage 44 is formed on the upstream side and the downstream side in the refrigerant gas flow direction. Since the oil separation chamber 49 is formed on the discharge passage 44, the oil separation chamber 49 is the same high pressure discharge pressure region as the discharge chamber 31. An oil separation cylinder 62 is provided in the oil separation chamber 49. The oil separation cylinder 62 has a substantially cylindrical shape, and is joined to the inner peripheral surface of the oil separation chamber 49 so as to be coaxial with the oil separation chamber 49.

  Next, the oil return structure provided in the swash plate compressor 10 will be described. In the swash plate compressor 10, an oil storage chamber 63 is recessed inside the pedestal 35, and the upper end surface 35 a serving as a mating surface with the lower end surface 40 a of the muffler forming member 40 around the upper opening of the oil storage chamber 63. Is formed. In a state where the muffler forming member 40 is fixed to the pedestal 35 via the gasket 41, the oil storage chamber 63 is partitioned from the muffler chamber 43 by the gasket 41, and the oil storage chamber 63 is located below the muffler chamber 43. Yes.

  The oil storage chamber 63 communicates with the oil separation chamber 49 via a connection passage 67 formed in the base 35 and the rear housing 14. The oil storage chamber 63 is in the discharge pressure region, but is slightly lower in pressure than the oil separation chamber 49. Therefore, the lubricating oil centrifuged in the oil separation chamber 49 due to the differential pressure between the oil separation chamber 49 and the oil storage chamber 63 is sent to the oil storage chamber 63 via the connection passage 67. . The lubricating oil sent to the oil storage chamber 63 is stored in the oil storage chamber 63.

  As shown in FIGS. 2, 5, and 6, an oil discharge passage 64 is formed in the pedestal 35, and an inlet 64 a of the oil discharge passage 64 is formed on a side surface of the oil storage chamber 63 that is the bottom side of the oil storage chamber 63. The outlet 64b of the oil discharge passage 64 opens toward the upper end surface 35a of the pedestal 35. That is, the outlet 64b of the oil discharge passage 64 is located above the inlet 64a. The oil discharge passage 64 is provided to discharge the lubricating oil stored in the oil storage chamber 63 from the oil storage chamber 63. As shown in FIGS. 1 and 6, an oil supply passage 65 is formed in the base 35 and the rear housing 14, and an inlet 65 a of the oil supply passage 65 opens toward the upper end surface 35 a of the base 35. The outlet 65b of the supply passage 65 communicates with the suction chamber 30 that is in a lower pressure region than the discharge pressure region (see FIG. 1). The oil supply passage 65 is provided for supplying lubricating oil to the suction chamber 30.

  In the gasket 41, a region corresponding to the mating surface of the upper end surface 35a of the pedestal 35 and the lower end surface 40a of the muffler forming member 40, that is, a region where the upper end surface 35a and the lower end surface 40a are sealed in the gasket 41 is a sealing region. S (shaded portion in FIG. 4) is formed. As shown in FIGS. 3 and 4, the seal region S is a region around the upper opening of the oil storage chamber 63 in the gasket 41, and an elongated oil guide passage 41 </ b> A is formed in the seal region S. ing. The seal region S in the gasket 41 is a quadrangular ring corresponding to the upper end surface 35a and the lower end surface 40a, and is a region extending broadly along the circumferential direction of the seal region S similarly to the upper end surface 35a and the lower end surface 40a.

  As shown in FIGS. 4 and 6, the oil guide passage 41 </ b> A is formed so as to penetrate in the plate thickness direction of the gasket 41, and is sandwiched between the upper end surface 35 a of the pedestal 35 and the lower end surface 40 a of the muffler forming member 40. Is forming. In a state where the gasket 41 is interposed between the base 35 and the muffler forming member 40, one end side of the oil guide passage 41A is at a position corresponding to the outlet 64b of the oil discharge passage 64, and the outlet 64b and the oil guide passage It communicates with 41A. When the gasket 41 is interposed between the pedestal 35 and the muffler forming member 40, the other end of the oil guide passage 41A is in a position corresponding to the inlet 65a of the oil supply passage 65, and is guided to the inlet 65a. The oil passage 41A communicates.

  As shown in FIGS. 3 and 4, the oil guide passage 41 </ b> A is formed in a substantially U shape in plan view, extends linearly from a position corresponding to the outlet 64 b of the oil discharge passage 64, and the oil storage chamber 63. The upper opening of the oil supply passage 65 is bent so as to extend along the periphery, and further extends linearly toward the inlet 65 a of the oil supply passage 65. In addition, the oil guide passage 41A is set so that its passage width is not too narrow in order to avoid clogging due to foreign matter. Furthermore, the oil guide passage 41A is formed with a narrower passage width than the oil discharge passage 64 and the oil supply passage 65, and is bent a plurality of times, so that the oil storage chamber 63 and the suction chamber 30 It functions as a throttle passage between them.

  The oil storage chamber 63 and the suction chamber 30 communicate with each other through the oil discharge passage 64, the oil guide passage 41A, and the oil supply passage 65. The oil discharge passage 64, the oil guide passage 41A, and the oil supply passage 65 form an oil return passage for returning (supplying) the lubricating oil stored in the oil storage chamber 63 to the suction chamber 30. Further, the discharge passage 44 (oil separation chamber 49), the oil storage chamber 63, the oil discharge passage 64, the oil guide passage 41A, and the oil supply passage 65 include a discharge chamber 31 serving as a discharge pressure region, and the discharge chamber 31. A communication passage is formed to communicate with the suction chamber 30 which is a lower pressure region. The oil return passage constitutes a part of the communication passage. Further, in the swash plate compressor 10, the oil return from the oil storage chamber 63 and the oil return passage (the oil discharge passage 64, the oil guide passage 41A, the oil supply passage 65) that connects the oil storage chamber 63 and the suction chamber 30 is performed. The structure is structured.

  Now, lubricating oil is put in the refrigerant circuit consisting of the swash plate compressor 10 and the external refrigerant circuit 50, and this lubricating oil flows together with the refrigerant gas. The refrigerant gas introduced from the discharge passage 44 into the oil separation chamber 49 swirls along the peripheral surface of the oil separation cylinder 62, and the mist-like lubricating oil flowing together with the refrigerant gas is centrifuged from the refrigerant gas. Here, since the oil separation chamber 49 is a discharge pressure region and is a higher pressure region than the oil storage chamber 63, the lubricating oil centrifuged from the refrigerant gas passes from the oil separation chamber 49 to the oil storage chamber 63 via the connection passage 67. And is stored in the oil storage chamber 63.

  During operation of the swash plate compressor 10, when refrigerant gas circulates from the external refrigerant circuit 50 to the suction chamber 30, a differential pressure is generated between the suction chamber 30 and the oil storage chamber 63 that is a high pressure region. Then, the lubricating oil stored in the oil storage chamber 63 is supplied to the suction chamber 30 via the oil discharge passage 64, the oil guide passage 41A, and the oil supply passage 65, that is, the oil return passage. At this time, the inlet 64a of the oil discharge passage 64 communicates with the bottom side of the oil storage chamber 63 and is positioned below the outlet 64b (see FIG. 6). For this reason, lubricating oil always flows into the oil discharge passage 64, and the oil storage chamber 63 and the oil guide passage 41A are sealed by the lubricating oil.

  The oil return passage 41 </ b> A in the oil return passage is bent at a plurality of locations so as to surround the upper opening of the oil storage chamber 63, and the passage width is narrower than that of the oil discharge passage 64 and the oil supply passage 65, so that the passage is elongated. (See FIG. 4). For this reason, the oil guide passage 41A functions as a throttle passage in the oil return passage, and the pressure is reduced when the lubricating oil passes through the oil guide passage 41A. As a result, the lubricating oil is cooled.

  The lubricating oil supplied to the suction chamber 30 is sucked into the compression chamber 37 together with the refrigerant gas sucked into the compression chamber 37, and further returned to the control pressure chamber 15 from the discharge passage 55. As a result, the lubricating oil is supplied to the compression mechanism and each sliding portion, and the lubrication required portion in the control pressure chamber 15 (sliding contact portion between the swash plate 24 and the shoe 29, radial bearings 18, 19, thrust bearing 23, etc.) Lubricate.

According to the above embodiment, the following effects can be obtained.
(1) The oil guide passage 41A that forms a part of the oil return passage is formed in the seal region S that seals the mating surface of the upper end surface 35a of the base 35 and the lower end surface 40a of the muffler forming member 40 in the gasket 41. Yes. The upper end surface 35a of the pedestal 35 and the lower end surface 40a of the muffler forming member 40 are generally wide and have a larger area than the mating surface 98a of the cylinder block 98 in the background art. Therefore, by forming the oil guide passage 41A in the seal region S of the gasket 41, the design freedom regarding the shape of the oil guide passage 41A can be reduced as compared with the case of forming the oil guide passage 93 on the mating surface 98a of the background art. The degree can be increased.

  (2) The seal area S of the gasket 41 is wider than the mating surface 98a of the cylinder block 98 in the background art. For this reason, even if the oil guide passage 41 </ b> A is formed in the gasket 41, it is possible to secure a sufficient seal width for suppressing leakage of the refrigerant gas by the gasket 41. When the oil guide passage 93 is formed at a position corresponding to the mating surface 98a of the cylinder block 98 as in the background art, the passage width of the oil guide passage 41A is limited, specifically, it is formed to be quite narrow. Had to do. And when the passage width of the oil guide passage 41A is very narrow, foreign matters mixed in the refrigerant gas are easily clogged, but in this embodiment, the passage width and the passage length of the oil guide passage 41A are suitably set. The oil guide passage 41A is formed with a passage width that is not too thin. Therefore, it is possible to set the oil guide passage 41A in a shape in which the oil guide passage 41A is not easily clogged with foreign matters.

  (3) A part of the oil return passage (oil guide passage 41A) was formed using a configuration (a pedestal 35, a muffler forming member 40, and a gasket 41) provided in the housing to form the muffler chamber 43. That is, the degree of freedom in designing the shape of the oil guide passage 41A can be increased while using the existing configuration of the swash plate compressor 10.

  (4) The oil guide passage 41A functions as a throttle passage, and the lubricating oil supplied from the oil storage chamber 63 to the suction chamber 30 can be decompressed. And since lubricating oil is cooled with pressure reduction, the viscosity fall of lubricating oil accompanying high temperature can be prevented, and the fall of the cooling effect of a compression mechanism or each sliding part can be suppressed. In addition, since the oil guide passage 41A functions as a throttle passage, it is possible to prevent the lubricating oil from being excessively supplied from the oil storage chamber 63 to the suction chamber 30 via the oil guide passage 41A. Therefore, the lubricating oil is excessively supplied to the suction chamber 30 and the oil storage chamber 63 is emptied, and the separation of the lubricating oil in the oil separation chamber 49 and the feeding of the lubricating oil to the oil storage chamber 63 are not in time, and the compression mechanism And each sliding portion can be prevented from being poorly lubricated.

  (5) The inlet 64a of the oil discharge passage 64 communicates with the side surface located on the bottom side of the oil storage chamber 63, and the outlet 64b communicates with the oil guide passage 41A above the inlet 64a. For this reason, lubricating oil always flows into the oil discharge passage 64, and the oil storage chamber 63 and the oil guide passage 41A are sealed by the lubricating oil. Therefore, the high-pressure refrigerant gas introduced into the oil storage chamber 63 can be prevented from passing through the oil discharge passage 64. Therefore, the refrigerant gas introduced into the oil separation chamber 49 is led out from the oil storage chamber 63 to the suction chamber 30 via the oil discharge passage 64, the oil guide passage 41A, and the oil supply passage 65, that is, a gas path is prevented. be able to. As a result, a decrease in compression efficiency of the swash plate compressor 10 can be suppressed.

  (6) The oil guide passage 41 </ b> A is formed so as to surround the upper opening of the oil storage chamber 63. For this reason, the passage length of the oil guide passage 41A can be increased, and the cooling efficiency of the lubricating oil passing through the oil guide passage 41A can be increased.

In addition, you may change this embodiment as follows.
As shown in FIGS. 7A and 7B, the pedestal 35 is extended from the side outer surface of the cylinder block 11 to the side, and the muffler forming member 40 is fixed to the side end surface 35b of the pedestal 35. It may be. In addition, the oil discharge passage 64 of the oil return passage is formed in the side end surface 35 b of the pedestal 35 so as to be adjacent to the gasket 41, and communicates with the oil guide passage 41 </ b> A of the gasket 41. For this reason, the lubricating oil in the oil storage chamber 63 always flows into the oil discharge passage 64, and a gas path through the oil discharge passage 64 is not generated. In the swash plate compressor 10 shown in FIG. 7, the oil discharge passage 64 has an arbitrary position on the bottom surface (lower surface) of the oil storage chamber 63 and the oil guide passage 41 </ b> A as shown by a two-dot chain line in FIG. May be formed on the pedestal 35 so as to communicate with each other.

  As shown in FIGS. 8A and 8B, the swash plate compressor 10 may be reversed 180 degrees (upside down) with respect to the first embodiment. In this case, the base 35 is a cylinder block. 11, the muffler forming member 40 is fixed to the lower end surface 35c of the base 35. In this case, the oil storage chamber 63 is located above the muffler chamber 43 via the gasket 41. Further, the oil discharge passage 64 of the oil return passage is notched in the lower end surface 35 c so as to be adjacent to the gasket 41, and communicates with the oil guide passage 41 </ b> A of the gasket 41. For this reason, the lubricating oil in the oil storage chamber 63 always flows into the oil discharge passage 64, and a gas path through the oil discharge passage 64 is not generated.

  As shown in FIG. 9, the partition wall 35 </ b> A is erected so as to divide the inside of the pedestal 35 into a plurality, and the partition 40 </ b> A is formed so as to divide the inside of the muffler forming member 40 into a plurality. Then, the oil storage chamber 63 and the muffler chamber 43 may be partitioned side by side by combining the partition wall 35A and the partition wall 40A.

  As shown in FIG. 10, the pedestal 35 may be extended from the side outer surface of the cylinder block 11 to the side, and the muffler forming member 40 may be fixed to the side end surface 35 b of the pedestal 35. Further, a partition wall 35A is erected so as to divide the inside of the pedestal 35 into a plurality, and a partition wall 40A is formed so as to divide the muffler forming member 40 into a plurality of parts. Then, the muffler chamber 43 may be partitioned above the oil storage chamber 63 by combining the partition wall 35A and the partition wall 40A. In the gasket 41, a through hole 41 b is provided in a plate thickness direction at a position corresponding to the muffler chamber 43 and the oil storage chamber 63. The muffler chamber 43 and the oil storage chamber 63 straddle the gasket 41 and the base 35 and the muffler forming member 40. Is formed. In this case, the oil discharge passage 64 of the oil return passage is cut out and formed on the side end face 40 b of the muffler forming member 40 so as to be adjacent to the gasket 41. As shown by the two-dot chain line in FIG. 10, the oil discharge passage 64 may be formed in the side end surface 35 b of the pedestal 35 so as to be adjacent to the gasket 41. Further, the oil discharge passage 64 may be formed in the gasket 41 itself so as to communicate the through hole 41b of the gasket 41 and the oil guide passage 41A.

  As shown in FIG. 11, the swash plate compressor 10 may be reversed 180 degrees (upside down) with respect to the first embodiment, and the pedestal 35 extends downward from the lower outer surface of the cylinder block 11. Then, the muffler forming member 40 is fixed to the lower end surface 35 c of the pedestal 35. Further, the partition wall 35A is erected so as to divide the inside of the pedestal 35 into a plurality of parts. Then, the oil storage chamber 63 and the muffler chamber 43 may be partitioned side by side with the partition wall 35A. The oil storage chamber 63 is located above the gasket 41, and the oil discharge passage 64 is formed in the gasket 41 itself so as to communicate the oil storage chamber 63 and the oil guide passage 41A. Alternatively, the oil discharge passage 64 may be notched in the lower end surface 35 c of the pedestal 35 so as to be adjacent to the gasket 41.

  The oil storage chamber 63 may be formed in the pedestal 35 and the muffler forming member 40 across the gasket 41. In this case, the oil discharge passage 64 is formed on the inner surface of the oil storage chamber 63 on the bottom surface (lower surface) side. May be formed in the muffler forming member 40 so that the outlet 64b communicates with the oil guide passage 41A. Alternatively, the oil discharge passage 64 may be formed in the muffler forming member 40 so as to be adjacent to the gasket 41.

  The oil guide passage 41A is not formed so as to surround the upper opening of the oil storage chamber 63, and may be changed to an arbitrary shape. For example, as shown in FIG. 12, the oil guide passage 41 </ b> A may be folded back and forth over a plurality of times in a plan view. Even if comprised in this way, the passage length of 41 A of oil guide paths can be ensured long, and also the pressure reduction efficiency of lubricating oil can be improved by returning in multiple times, and the throttle function by oil guide path 41A is effective. Can be demonstrated. Alternatively, the oil guide passage 41A may extend so as to draw an arc.

The oil supply passage 65 may be formed so that the outlet 65 b communicates with the control pressure chamber 15 that is in a lower pressure region than the oil storage chamber 63.
○ The swash plate compressor 10 is not a one-sided compressor that compresses the single-headed piston 27, but is compressed into a double-headed piston in the cylinder bores 26 provided on both front and rear sides with the control pressure chamber 15 in between. It is good also as a double-sided compressor which performs.

  The refrigerant compressor is replaced with a configuration in which the swash plate 24 rotates integrally with the rotary shaft 16, and the rotary support 22 is supported so as to be rotatable relative to the rotary shaft 16. It may be a wobble) type compressor.

  The swash plate compressor 10 may be a fixed capacity type in which the stroke of the piston 27 cannot be changed.

The longitudinal cross-sectional view which shows the swash plate type compressor of embodiment. The AA sectional view taken on the line of FIG. 1 which shows a base. The top view which shows a gasket. The top view which shows the state which mounted the gasket on the base. The fragmentary sectional view which shows a muffler chamber and an oil storage chamber. Sectional drawing which shows the inner side of a base and a muffler formation member. (A) is a fragmentary sectional view which shows a swash plate type compressor provided with the base extended toward the side, (b) is the 7b-7b diagram of Fig.7 (a). (A) is a fragmentary sectional view which shows the state which reversed the top and bottom of the swash plate type compressor, (b) is the 8b-8b diagram of Fig.8 (a). The fragmentary sectional view which shows the swash plate type compressor formed by dividing | segmenting a muffler chamber and an oil storage chamber. The fragmentary sectional view which shows the state which divided | segmented the muffler chamber and the oil storage chamber. The fragmentary sectional view which shows the swash plate type compressor which divided | segmented the muffler chamber and the oil storage chamber, and reversed the top and bottom. The top view which shows another example of an oil guide path. The figure which shows the swash plate type compressor of background art.

Explanation of symbols

  DESCRIPTION OF SYMBOLS S ... Seal area | region, 10 ... Swash plate type compressor as a refrigerant compressor, 11 ... Cylinder block as a housing, 30 ... Suction chamber as a low pressure area, 31 ... Discharge chamber as a discharge pressure area, 35a ... As a mating surface Upper end surface, 40 ... muffler forming member, 40a ... lower end surface as a mating surface, 41 ... gasket, 41A ... oil guide passage (communication passage) constituting oil return passage, 43 ... muffler chamber (communication passage), 44 ... communication A discharge passage constituting the passage, 49 ... an oil separation chamber (communication passage) as a discharge pressure region, 63 ... an oil storage chamber (communication passage) as a discharge pressure region, 64 ... an oil discharge passage (communication passage) constituting an oil return passage ), 64a ... inlet, 64b ... outlet, 65 ... oil supply passage (communication passage) constituting the oil return passage.

Claims (6)

An oil separation chamber for separating lubricating oil from the discharged refrigerant gas is provided in the discharge pressure region, and a muffler forming member that forms a muffler chamber for the discharged refrigerant gas is connected to a side outer surface or a lower outer surface of the housing And an oil return structure in a refrigerant compressor in which a sealing gasket is interposed between the housing and the muffler forming member,
An oil storage chamber for storing the lubricating oil separated in the oil separation chamber is provided on a communication passage communicating the discharge pressure region and a low pressure region lower than the discharge pressure region, and the oil storage chamber and the low pressure region are provided. A refrigerant compressor which is communicated by an oil return passage constituting a part of the communication passage, and an oil guide passage which is a part of the oil return passage is formed in a seal region of a mating surface of the housing and the muffler forming member in the gasket. Oil return structure. An oil separation chamber for separating lubricating oil from the discharged refrigerant gas is provided in a discharge pressure region, and a muffler forming member that forms a muffler chamber for the discharged refrigerant gas is connected to an upper outer surface of the housing, and the housing And an oil return structure in a refrigerant compressor in which a gasket for sealing is interposed between the muffler forming member,
An oil storage chamber for storing the lubricating oil separated in the oil separation chamber is provided on a communication passage communicating the discharge pressure region and a low pressure region lower than the discharge pressure region, and the oil storage chamber and the low pressure region are provided. A refrigerant compressor which is communicated by an oil return passage constituting a part of the communication passage, and an oil guide passage which is a part of the oil return passage is formed in a seal region of a mating surface of the housing and the muffler forming member in the gasket. Oil return structure. The oil return passage includes an oil discharge passage that communicates the oil storage chamber and the oil guide passage, an oil supply passage that communicates the oil guide passage and the low pressure region, and the oil guide passage. The oil return structure in the refrigerant compressor according to claim 2, wherein an inlet of the passage communicates with a bottom side of the oil storage chamber, and an outlet communicates with the oil guide passage above the inlet. The oil return structure in the refrigerant compressor according to any one of claims 1 to 3, wherein the oil guide passage functions as a throttle passage in the oil return passage. The oil return structure in the refrigerant compressor according to claim 4, wherein the oil guide passage is formed so as to surround the oil storage chamber in the seal region. The oil return structure in the refrigerant compressor according to claim 4, wherein the oil guide passage is formed so as to extend in a state of being folded back a plurality of times in the seal region.

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