JP2015175280A - compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide technique capable of improving flexibility in design of a discharge passage and a delivery passage in a compressor in which a side plate and an oil separator are integrated.SOLUTION: A compressor 10 includes a shell 11, a compression mechanism, a side plate 20, and an oil separating cylinder 54. The side plate divides an inside of the shell into a first space in which the compression mechanism is arranged, and a second space in which lubricating oil contained in refrigerant gas delivered from the compression mechanism is stored. The side plate includes a base part, an oil separating chamber forming part 20c, a delivery passage forming part 20d, and a discharge passage forming part 20e, and the members are integrally formed. An expansion amount of the delivery passage forming part is reduced as being separated from the oil separating chamber forming part. Delivery passages 44 and 45 and a discharge passage 46 are formed in a straight line. The delivery passages 44 and 45 are opened to an end surface on the first space side of the base part, and are communicated with the first space. An outflow port of the discharge passage 46 is opened to the discharge passage forming part, and is communicated with the second space.

Description

  The technology disclosed in this specification relates to a compressor.

  Patent Document 1 discloses a vane type compressor. In this compressor, the inside of the shell is divided into a compression mechanism side and a discharge region side from which refrigerant gas compressed by the compression mechanism is discharged by side plates provided in the shell. An oil separator that separates the lubricating oil contained in the refrigerant gas discharged from the compression mechanism is disposed in the discharge region. The oil separator is provided separately from the side plate, and is assembled to the side plate. The oil separator is formed with an oil separation chamber in which the separated lubricating oil drops. A cylindrical oil separation cylinder for transferring the separated refrigerant gas is disposed in the upper part of the oil separation chamber (that is, the upper part in a state where the compressor is mounted on a vehicle or the like). The outside of the oil separator in the discharge region is an oil storage chamber. The oil separation chamber and the oil storage chamber are connected by a discharge passage. One end of the discharge passage opens to the oil separation chamber, and the other end of the discharge passage opens to the oil storage chamber. The lubricating oil in the oil separation chamber is discharged from the other end to the oil storage chamber via the discharge passage. The lubricating oil discharged to the oil storage chamber is supplied to the compression mechanism via a passage formed in the side plate. The oil supplied to the compression mechanism is used for back pressure and sliding portion lubrication.

JP 2010-48099 A

  In the compressor of Patent Document 1, the oil separator is provided separately from the side plate. For this reason, it is desired to integrate the side plate and the oil separator to increase the manufacturing efficiency and reduce the manufacturing cost. When the side plate and the oil separator are integrated, an oil separation chamber is formed inside the side plate. Specifically, a first bulging portion that bulges toward the discharge region side is formed on an end surface of the side plate on the discharge region side, and an oil separation chamber is formed inside the first bulge portion. In addition to the first bulge portion, a second bulge portion and a third bulge portion that bulge toward the discharge region side are formed on the end surface on the discharge region side. A discharge passage is formed in the second bulging portion to transfer the refrigerant gas discharged from the compression mechanism to the oil separation chamber. A discharge passage for discharging the lubricating oil in the oil separation chamber to the oil storage chamber is formed inside the third bulge portion. The discharge passage and the discharge passage are formed by machining using a tool. Here, if each bulging portion integrally bulges in the same direction from the end surface on the discharge area side of the side plate, the movable range of the tool is the second when the discharge passage is formed in the third bulging portion. There is a case where the direction of the discharge passage is limited by the bulging portion. Similarly, when the discharge passage is formed in the second bulge portion, the direction of the discharge passage may be limited by the third bulge portion. That is, when the side plate and the oil separator are integrated, the degree of freedom in designing the discharge passage and the discharge passage may be lowered.

  The present specification provides a technique for improving the degree of freedom in designing a discharge passage and a discharge passage in a compressor in which a side plate and an oil separator are integrated.

  A compressor disclosed in the present specification includes a shell, a compression mechanism disposed in the shell, a side plate, and an oil separation cylinder. The side plate partitions the inside of the shell into a first space in which the compression mechanism is disposed and a second space in which lubricating oil contained in the refrigerant gas discharged from the compression mechanism is stored. The oil separation cylinder separates the lubricating oil contained in the refrigerant gas discharged from the compression mechanism. The side plate has a base portion, an oil separation chamber forming portion, a discharge passage forming portion, and a discharge passage forming portion. The base portion partitions the first space and the second space. The oil separation chamber forming portion bulges from the end surface of the base portion on the second space side, and forms an oil separation chamber in which the oil separation cylinder is accommodated. The discharge passage forming portion bulges from the end surface of the base portion on the second space side and is connected to the side wall of the oil separation chamber forming portion, and connects the first space and the upper portion of the oil separation chamber. Is formed inside. The discharge passage forming portion bulges from the end surface of the base portion on the second space side, and is connected to the side wall of the oil separation chamber forming portion, and has a discharge passage that communicates the lower portion of the oil separation chamber and the second space. Form inside. The base portion, the oil separation chamber forming portion, the discharge passage forming portion, and the discharge passage forming portion are integrally formed. The amount of swelling of the discharge passage forming portion decreases as the distance from the oil separation chamber forming portion increases. The discharge passage is formed in a straight line from the inflow port to the outflow port, and the discharge passage opens at the end surface of the base portion on the first space side and communicates with the first space. The discharge passage is formed in a straight line from the inflow port to the outflow port, and the outflow port of the discharge passage opens into the discharge passage forming portion and communicates with the second space.

  In the above compressor, the oil separation chamber forming portion, the discharge passage forming portion, and the discharge passage forming portion bulge in the same direction from the end face on the second space side of the base portion of the side plate. The base part and each forming part are integrated. The discharge passage is formed by machining a straight hole using a tool from the surface of the discharge passage forming portion toward the oil separation chamber. As a result, the outlet of the discharge passage opens into the discharge passage forming portion. In the above compressor, the bulge amount of the discharge passage forming portion located on the same side as the discharge passage forming portion with respect to the base portion of the side plate decreases as the distance from the oil separation chamber forming portion increases. For this reason, the movable range of a tool becomes wide compared with the structure where the amount of swelling of a discharge channel | path formation part is constant. Therefore, the discharge passage forming portion can be processed from a more free direction, and the degree of freedom in designing the discharge passage can be improved. Further, in the above compressor, the discharge passage opens at the end surface on the first space side of the base portion of the side plate. In other words, the discharge passage is formed in a linear shape by using a tool from the end surface on the first space side of the base portion (that is, the end surface opposite to the end surface on which each of the forming portions bulges) toward the oil separation chamber. It is formed by processing holes. For this reason, when processing a discharge channel, a tool does not contact each above-mentioned formation part. Therefore, the discharge passage can be processed from a more free direction. According to this configuration, in the compressor in which the side plate and the oil separator are integrated, the degree of freedom in designing the discharge passage and the discharge passage can be improved.

  Details of the technology disclosed in this specification and further improvements will be described in detail in the detailed description and examples.

Sectional drawing of the vane type compressor of Example 1 is shown. It is sectional drawing in the II-II line | wire of FIG. 1, and shows the inside of a compression mechanism. It is sectional drawing in the III-III line of FIG. 1, and shows the positional relationship of a discharge channel and a convex part. The perspective view of a rear side plate is shown. The positional relationship of the discharge passage and recessed part of the vane type compressor of Example 2 is shown. The positional relationship of the discharge passage and convex part of the vane type compressor of Example 3 is shown.

  The main features of the embodiments described below are listed. The technical elements described below are independent technical elements and exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. Absent.

(Characteristic 1) In the compressor disclosed in the present specification, the outlet of the discharge passage may be located above the inlet of the discharge passage. In the above compressor, the discharge passage opens at the upper part of the oil separation chamber, and the discharge passage opens at the lower part of the oil separation chamber. For this reason, the discharge passage forming portion is located above the discharge passage forming portion. In the above compressor, as described above, the bulging amount of the discharge passage forming portion decreases as the distance from the oil separation chamber forming portion increases. For this reason, even if it is the structure where the outflow port of a discharge passage is located above the inflow port of a discharge passage, a discharge passage formation part can be processed from a suitable direction using a tool. Further, according to this configuration, the flow rate of the lubricating oil discharged from the discharge passage is lowered in the process of passing through the discharge passage. For this reason, it can suppress that the oil level of the lubricating oil stored in 2nd space is disturb | confused with the lubricating oil mixed with the refrigerant gas discharged | emitted from a discharge channel. Therefore, it can suppress that refrigerant gas mixes in the lubricating oil of 2nd space, and can suppress that refrigerant gas mixes in the lubricating oil supplied to a compression mechanism.

(Characteristic 2) In the compressor which this specification discloses, the discharge passage formation part may be formed in the position which does not oppose the outflow port of a discharge passage. According to this structure, it can suppress that a tool contacts a discharge channel | path formation part, and a discharge channel | path formation part can be processed from a desired direction.

(Characteristic 3) In the compressor which this specification discloses, the convex part which protrudes from the inner wall face of the shell in 2nd space may be formed in the shell. The convex portion may be formed at a position facing the outlet of the discharge passage. In this configuration, the lubricating oil mixed with the refrigerant gas discharged from the outlet of the discharge passage collides with a convex portion protruding from the inner wall surface of the shell. Thereby, separation of the refrigerant gas and the lubricating oil is promoted, and it is possible to further suppress the refrigerant gas from being mixed into the lubricating oil stored in the second space. Further, the formation of the separation-promoting convex portion on the inner wall surface of the shell is less susceptible to manufacturing restrictions than the formation of the separation-promoting configuration on other members in the shell. For this reason, according to said structure, the freedom degree of design can be improved.

(Characteristic 4) In the compressor disclosed in the present specification, a concave portion that is recessed from the inner wall surface of the shell in the second space may be formed in the shell. The recess may be formed at a position facing the outlet of the discharge passage. In this configuration, the lubricating oil mixed with the refrigerant gas discharged from the outlet of the discharge passage collides with a recess that is recessed from the inner wall surface of the shell. Thereby, separation of the refrigerant gas and the lubricating oil is promoted, and it is possible to further suppress the refrigerant gas from being mixed into the lubricating oil stored in the second space. Moreover, a compressor can be reduced in weight by forming a recessed part in a shell.

  The vane type compressor 10 of Example 1 is demonstrated with reference to FIGS. As shown in FIG. 1, the shell 11 of the vane compressor 10 includes a front shell 12 and a rear shell 14. The front shell 12 and the rear shell 14 are fastened by four bolts 13 (see FIGS. 2 and 3). Three attachment feet 14 a are formed on the rear shell 14. The vane compressor 10 is fixed in the vehicle by attaching the mounting foot 14a to the vehicle engine or the like (not shown). In addition, the up-down direction and the front-back direction of FIG. 1 correspond with the up-down direction and the front-back direction in the state which attached the vane type compressor 10 to the vehicle. 1 to 4 are schematic diagrams, and it should be noted that the scales are not exactly the same. The same applies to other embodiments.

  A cylinder 16 having a cylindrical shape extending in the front-rear direction is disposed in front of the rear shell 14. A space extending in the front-rear direction is formed inside the cylinder 16. The cross section of the space in a plane orthogonal to the front-rear direction has an elliptical shape (see FIG. 2). A front side plate 18 is disposed in front of the cylinder 16. The rear end surface 18 a of the front side plate 18 is in contact with the front end surface of the cylinder 16. A rear side plate 20 is disposed behind the cylinder 16. A front end surface 20 a of the rear side plate 20 (specifically, a front end surface 20 a of a base portion 20 f (described later) of the rear side plate 20 is in contact with the rear end surface of the cylinder 16. An annular outer peripheral discharge space 40 is defined between the inner peripheral surface of the rear shell 14, the outer peripheral surface of the cylinder 16, the rear end surface 18 a of the front side plate 18, and the front end surface 20 a of the rear side plate 20.

  The front side plate 18 is formed with a through hole 18b through which a drive shaft 22 (described later) passes. A sliding bearing 26 is provided in the through hole 18b. The rear side plate 20 is formed with an insertion hole 20b in which the rear end portion of the drive shaft 22 is disposed. A sliding bearing 28 is provided in the insertion hole 20b. The drive shaft 22 extends in the front-rear direction in the shell 11 and is formed by a shaft seal device 24 provided in the front shell 12 and sliding bearings 26 and 28 provided in the through hole 18b and the insertion hole 20b, respectively. 11 and side plates 18 and 20 are rotatably supported.

  A cylindrical rotor 30 that can rotate integrally with the drive shaft 22 is disposed in the internal space of the cylinder 16, and the rotor 30 is fixed to the drive shaft 22. As shown in FIG. 2, five vane grooves 30 a having a depth in the radial direction are formed on the outer peripheral surface of the rotor 30 at equal intervals in the circumferential direction. A vane 32 slidable in the radial direction is accommodated in the vane groove 30a. A back pressure chamber 33 is formed between the vane groove 30 a and the vane 32. Lubricating oil is supplied to the back pressure chamber 33. The back pressure chamber 33 communicates with a groove 18 d formed in the rear end surface 18 a of the front side plate 18 and communicates with a passage 64 d formed in the rear side plate 20. When the rotor 30 rotates with the rotation of the drive shaft 22, the vane 32 is pushed outward in the radial direction by the back pressure of the back pressure chamber 33 and comes into contact with the inner peripheral surface of the cylinder 16. The compression chamber 34 is defined by the inner peripheral surface of the cylinder 16, the outer peripheral surface of the rotor 30, the two adjacent vanes 32 and 32, the rear end surface 18 a of the front side plate 18, and the front end surface 20 a of the rear side plate 20. The process in which the volume of the compression chamber 34 increases with the rotation of the rotor 30 is the suction process, and the process in which the volume of the compression chamber 34 decreases is the compression process. The cylinder 16, the front side plate 18 (strictly, the rear end surface 18a), the rear side plate 20 (strictly, the front end surface 20a), the drive shaft 22, the rotor 30, and the vane 32 constitute a compression mechanism C.

  As shown in FIG. 1, a suction chamber 36 is formed between the front shell 12 and the front side plate 18. A suction port 38 that opens to the outside of the vane compressor 10 is formed in the upper portion of the front shell 12. The suction chamber 36 communicates with a suction port 38. The suction port 38 is connected to an evaporator (described later). The front side plate 18 is formed with two through holes 18c that penetrate the front side plate 18 in the front-rear direction. The two through holes 18 c are formed at positions opposite to each other with respect to the drive shaft 22. The cylinder 16 is formed with two suction passages 16a penetrating the cylinder 16 in the front-rear direction. Each suction passage 16a communicates with each through hole 18c. The suction chamber 36 and the compression chamber 34 (strictly speaking, the compression chamber 34 in which the suction process is performed) are communicated with each other through the through hole 18c and the suction passage 16a.

  As shown in FIG. 2, two recesses 16 b that are recessed radially inward are formed on the outer peripheral surface of the cylinder 16 along the depth direction of FIG. 2 (that is, the front-rear direction of FIG. 1). Yes. The two recesses 16b are formed at the center of the cylinder 16 in the vertical direction (in other words, on the short axis direction side of the elliptical cross section of the internal space of the cylinder 16). The two recesses 16 b are formed at positions opposite to each other with respect to the drive shaft 22. A space 16 c formed by the recess 16 b communicates with the outer peripheral discharge space 40. For this reason, the space 16c is hereinafter referred to as a discharge space 16c. The cylinder 16 is formed with a discharge port 16d that allows the discharge space 16c and the compression chamber 34 (strictly speaking, the compression chamber 34 in which the compression step is performed) to communicate with each other. The discharge port 16d can be opened and closed by a discharge valve 42 disposed in the recess 16b. That is, the discharge valve 42 opens when the pressure of the refrigerant gas discharged from the compression chamber 34 through the discharge port 16d exceeds a predetermined value, and closes when the pressure of the refrigerant gas becomes a predetermined value or less. It is configured to valve.

  As shown in FIG. 1, a discharge chamber 60 is formed between the rear side plate 20 and the rear shell 14. Lubricating oil contained in the refrigerant gas discharged from the compression mechanism C is stored in the lower part of the discharge chamber 60 (the lubricating oil is not shown in FIG. 1). That is, the space in the shell 11 is divided into a space in which the compression mechanism C is disposed and a space in which lubricating oil is stored by the rear side plate 20 (strictly, the disk-shaped base portion 20f of the rear side plate 20). Partitioned. A discharge port 62 that opens to the outside of the vane compressor 10 is formed at the upper part of the rear shell 14. The discharge chamber 60 communicates with the discharge port 62. The discharge port 62 is connected to a condenser (described later).

  As shown in FIGS. 1 and 4, in the rear side plate 20, the center portion of the rear end surface 20 f 1 of the base portion 20 f bulges rearward (that is, toward the discharge chamber 60). Below, the said center part is called the bulging part 20c. The bulging portion 20c has a substantially rectangular parallelepiped shape, and an oil separator 50 for centrifuging the lubricating oil contained in the refrigerant gas is disposed therein. The oil separator 50 includes an oil separation chamber 52 and an oil separation cylinder 54. The oil separation chamber 52 has a substantially cylindrical space having a height in the vertical direction in the bulging portion 20c. The oil separation cylinder 54 has a substantially cylindrical shape, and is press-fitted into the upper part of the oil separation chamber 52. That is, the oil separation chamber 52 is a space formed in the rear side plate 20 and is a space extending inward from the surface of the rear side plate 20. Lubricating oil after centrifugation is dropped at the lower part of the oil separation chamber 52 (the lubricating oil is not shown in FIG. 1). The length of the oil separation cylinder 54 in the vertical direction is shorter than the length of the oil separation chamber 52, and the lower end of the oil separation cylinder 54 is located at the center in the vertical direction of the oil separation chamber 52. A cylindrical space 52 a is formed between the inner peripheral surface of the oil separation chamber 52 and the outer peripheral surface of the oil separation cylinder 54. An opening 54 a that opens to the discharge chamber 60 is formed on the upper surface of the oil separation cylinder 54. The opening 54 a is located at a position shifted from the vertically lower side of the discharge port 62. That is, the inner peripheral surface of the rear shell 14 is positioned vertically above the opening 54a. The oil separation cylinder 54 transfers the separated refrigerant gas upward from the lower end of the oil separation cylinder 54 and discharges it to the discharge chamber 60 from the opening 54a. The refrigerant gas discharged from the opening 54a is discharged from the discharge port 62. The bulging portion 20c corresponds to an example of an “oil separation chamber forming portion”.

  As shown in FIGS. 3 and 4, the rear side plate 20 has two bulging portions 20d that bulge from the rear end surface 20f1 of the base portion 20f. Each bulging portion 20d bulges in the same direction as the bulging portion 20c bulges (ie, the direction toward the bottom surface of the rear shell 14). Each bulging portion 20d is connected to two side walls of the bulging portion 20c (that is, side walls extending along the axial direction of the oil separation chamber 52) that are substantially orthogonal to the rear end surface 20f1 of the base portion 20f. Has been. As shown in FIG. 4, the bulging amount of each bulging portion 20d (that is, the length bulging from the rear end surface 20f1 of the base portion 20f) decreases as the distance from the side wall of the bulging portion 20c increases. . As shown in FIGS. 3 and 4, the rear side plate 20 is formed with two discharge passages 44 that connect the discharge space 16 c and the oil separator 50 (specifically, the oil separation chamber 52). The discharge passage 44 transfers the refrigerant gas discharged from the compression mechanism C to the oil separation chamber 52. The end of the discharge passage 44 on the discharge space 16c side is formed in the base portion 20f. The end of the discharge passage 44 on the oil separation chamber 52 side is formed in the bulging portion 20c. The remaining portion of the discharge passage 44 is formed in the bulging portion 20d. The inflow port 44a of the discharge passage 44 is formed in the front end surface 20a of the base portion 20f, and opens to the discharge space 16c (see FIGS. 1 and 2). The outlet 44b of the discharge passage 44 is located at the bulging portion 20c, and is open to an upper portion of the space 52a of the oil separator 50 (see FIGS. 1 and 3). The outlet 44b of the discharge passage 44 is located above the inlet 44a. The discharge passage 44 is formed by drilling the rear side plate 20 from the front end surface 20a of the base portion 20f toward the oil separation chamber 52. Therefore, the discharge passage 44 is formed in a straight line from the inlet 44a to the outlet 44b. That is, the axis of the discharge passage 44 is formed in a straight line without being bent from the inlet 44a to the outlet 44b. Further, the cross-sectional area of the cross section perpendicular to the axis of the discharge passage 44 is substantially constant. The bulging portion 20d corresponds to an example of a “discharge passage forming portion”.

  As shown in FIGS. 3 and 4, the rear side plate 20 has a bulging portion 20e that bulges from the rear end surface 20f1 of the base portion 20f. The bulging portion 20e bulges in the same direction as the bulging portions 20c and 20d bulge (that is, the direction toward the bottom surface of the rear shell 14). The bulging part 20e is connected to one of the two side walls of the bulging part 20c to which the bulging part 20d is connected. The bulging portions 20c, 20d, 20e and the base portion 20f are integrally formed by die casting. The rear side plate 20 is constituted by the bulging portions 20c, 20d, 20e and the base portion 20f. In the rear side plate 20, a discharge passage 46 that connects the oil separator 50 (specifically, the oil separation chamber 52) and the discharge chamber 60 is formed. The discharge passage 46 discharges the lubricating oil separated by the oil separator 50 to the discharge chamber 60. The end of the discharge passage 46 on the oil separation chamber 52 side is formed in the bulging portion 20c. The remaining portion of the discharge passage 46 is formed in the bulging portion 20e. The inlet 46 a of the discharge passage 46 is located in the bulging portion 20 c and opens at the lowermost part of the oil separation chamber 52. The outlet 46 b of the discharge passage 46 is located on the surface of the bulging portion 20 e and opens to the discharge chamber 60. The discharge chamber 60 stores lubricating oil discharged from the outlet 46 b through the discharge passage 46. The outflow port 46b is located above the inflow port 46a. The discharge passage 46 is formed by drilling the rear side plate 20 from the surface of the bulging portion 20 e toward the oil separation chamber 52. Therefore, the discharge passage 46 is formed in a straight line from the inlet 46a to the outlet 46b. That is, the axis of the discharge passage 46 is formed in a straight line without bending from the inlet 46a to the outlet 46b. The cross-sectional area of the cross section perpendicular to the axis of the discharge passage 46 is substantially constant. Further, as shown in FIG. 1, the inlet 46 a of the discharge passage 46 is located behind the outlet 44 b of the discharge passage 44 (that is, the front side in FIG. 3). The bulging portion 20e corresponds to an example of a “discharge passage forming portion”.

  On the inner peripheral surface of the rear shell 14 in the discharge chamber 60, a protruding portion 15 that protrudes from the inner peripheral surface is formed. The protrusion 15 has a flat surface 15a. 3 indicates a virtual extension line in the discharge direction of the lubricating oil discharged from the outlet 46b of the discharge passage 46. The protrusion 15 is formed at a position facing the outflow port 46b, that is, at a position where the virtual extension line is substantially orthogonal to the plane 15a. For this reason, the lubricating oil discharged from the outlet 46 b collides with the flat surface 15 a of the protruding portion 15 in the vertical direction.

  As shown in FIG. 1, a recess 14 b that is recessed downward is formed on the lower surface of the rear shell 14. A gap 60 a is formed between the lower surface of the rear side plate 20 and the rear shell 14 by the recess 14 b. The gap 60 a communicates with the discharge chamber 60. An oil supply passage 64 (64a, 64b, 64c, 64d) is formed in the rear side plate 20. The passage 64a extends vertically upward, and one end thereof opens into the gap 60a, and the other end communicates with the insertion hole 20b. The passage 64b extends in the front-rear direction and branches from the passage 64a. The passage 64c goes around the outer periphery of the insertion hole 20b and communicates with the passage 64b. Two passages 64 d are formed, and each passage 64 d communicates with each back pressure chamber 33 in order as the rotor 30 rotates. The oil supply passage 64 is constituted by the passages 64a to 64d.

  The operation of the vane compressor 10 will be described. When the drive shaft 22 is driven by an engine or the like (not shown), the rotor 30 rotates integrally with the drive shaft 22. When the rotor 30 rotates, the volume of the compression chamber 34 changes. Specifically, the volume of the compression chamber 34 communicating with the suction passage 16a is increased. As a result, low-temperature and low-pressure refrigerant gas (gas) is sucked into the suction port 38 from the evaporator (not shown) through the pipe (not shown (the same applies to other pipes)), and the suction chamber 36 and the through hole 18c. The refrigerant gas (gas) compressed by the volume change of the compression chamber 34 is discharged to the discharge space 16c and the outer discharge space 40 from the discharge port 16d. The oil is discharged into the space 52a of the oil separator 50 through the discharge passage 44. The lubricating oil contained in the discharged refrigerant gas is cylindrical along the inner peripheral surface of the oil separation chamber 52 in the oil separator 50. The refrigerant gas is centrifugally separated by swirling in the space 52a, and dropped to the lower part of the oil separation chamber 52 through the inner peripheral surface of the oil separation chamber 52. On the other hand, the refrigerant gas from which the lubricating oil has been separated is separated into oil. From the lower end of the tube 54 The refrigerant gas discharged to the discharge chamber 60 collides with the inner peripheral surface of the rear shell 14 located vertically above the opening 54a, thereby separating the oil. The lubricating oil that could not be separated by the vessel 50 is separated from the refrigerant gas, and the lubricating oil is stored in the lower part of the discharge chamber 60 along the inner peripheral surface or the bottom surface (the rear surface in FIG. 1) of the rear shell 14. The refrigerant gas that has collided with the inner peripheral surface of the rear shell 14 is sent from a discharge port 62 to a condenser (not shown) via a pipe, and the refrigerant gas cooled and liquefied by the condenser expands via the pipe. The refrigerant gas rapidly expanded by the expansion valve is sent to the evaporator via the pipe, and the refrigerant gas that has been absorbed into the gas by the evaporator is converted into gas. Re via piping The air is sucked into the suction port 38 of the vane compressor 10. The vane compressor 10, the condenser, the expansion valve, and the evaporator are connected in this order via a pipe, and the refrigeration circuit of the vehicle air conditioner is connected to the vane compressor 10. It is composed.

  On the other hand, the lubricating oil dropped on the lower portion of the oil separation chamber 52 after separation by the oil separator 50 is discharged from the outlet 46b to the discharge chamber 60 through the discharge passage 46 and collides with the flat surface 15a of the protrusion 15 from the vertical direction. And stored in the lower part of the discharge chamber 60. The lubricating oil stored in the discharge chamber 60 is supplied to the insertion hole 20 b and the back pressure chamber 33 through the gap 60 a and the oil supply passage 64. The lubricating oil supplied to the insertion hole 20b lubricates the sliding bearing 28. The lubricating oil supplied to the back pressure chamber 33 urges the vane 32 radially outward and lubricates between the vane 32 and the vane groove 30a. Further, the lubricating oil lubricates the sliding bearing 26 via the back pressure chamber 33 and the groove 18 d and is sent to the suction chamber 36.

  In the vane type compressor 10 described above, the bulging amount of the bulging part 20d decreases as the distance from the bulging part 20c increases. For this reason, the movable range (movable angle) of the drill for forming the discharge passage 46 becomes wider as compared with the configuration in which the bulging amount of the bulging portion 20d is constant. Accordingly, the degree of freedom in designing the discharge passage 46 can be improved. In the vane compressor 10, the discharge passage 44 is formed by drilling the rear side plate 20 from the front end face 20a of the base portion 20f. For this reason, the drill for forming the discharge passage 44 does not contact the bulging portions 20c, 20d, and 20e, and the degree of freedom in designing the discharge passage 44 can be improved.

  In particular, in this embodiment, the outlet 46b of the discharge passage 46 is located above (more specifically, obliquely above) the inlet 46a. For this reason, the bulging portion 20 e is processed in a state where the tip of the drill is inclined obliquely downward toward the oil separation chamber 52. Therefore, the possibility that the drill comes into contact with the bulging portion 20d located above the bulging portion 20e is increased. However, according to the configuration of the present embodiment, the bulging amount of the bulging portion 20d decreases as the bulging portion is separated from the bulging portion 20c, and the bulging portion extends on the virtual extension line extending in the axial direction from the outlet 46b of the discharge passage 46. The protruding portion 20c is not located. For this reason, even if the drill is inclined obliquely downward, the direction of the drill is not limited by the bulging portion 20c, and the discharge passage 46 can be formed in an appropriate direction.

  Further, an oil separation chamber 52 is formed in the rear side plate 20, and the peripheral wall of the oil separation chamber 52 and the rear side plate 20 are shared. That is, since the rear side plate 20 and the oil separator 50 are integrated, the internal structure of the vane type compressor 10 can be simplified and reduced in size as compared with a configuration in which both are separate. Further, by disposing the oil separator 50 in the rear side plate 20, a seal member and the like that are required when the rear side plate and the oil separator are formed separately are not required, and the manufacturing efficiency can be improved and the manufacturing cost can be improved. Can be reduced.

  Further, in the vane compressor 10, the shape of the discharge passage 44 is a straight line. For this reason, pressure loss when the refrigerant gas flows through the discharge passage 44 can be reduced as compared with a configuration in which the discharge passage 44 has a bent portion (that is, a portion where the traveling direction of the refrigerant gas changes). Accordingly, it is possible to suppress a decrease in the flow rate of the refrigerant gas in the process of flowing through the discharge passage 44, and it is possible to suppress a decrease in the separation efficiency in the oil separator 50. Further, since the discharge passage 44 does not have a bent portion, lubricating oil (that is, lubricating oil mixed in the refrigerant gas) stays in the bent portion, and the amount of lubricating oil stored in the discharge chamber 60 decreases. Can be prevented.

  Further, in the vane type compressor 10 described above, the outlet 46 b of the discharge passage 46 is positioned above the inlet 46 a that is opened at the lowermost portion of the oil separation chamber 52. For this reason, the flow rate of the lubricating oil discharged from the discharge passage 46 decreases in the process of flowing upward in the discharge passage 46. For this reason, it can suppress that the lubricating oil of the discharge chamber 60 is rolled up by the lubricating oil discharged | emitted from the outflow port 46b, and mixes with the refrigerant gas in the discharge chamber 60. FIG. Therefore, supply of the refrigerant gas mixed with the lubricating oil to the back pressure chamber 33 and the insertion hole 20b can be suppressed. Further, when the lubricating oil in the discharge chamber 60 is rolled up, the oil level is lowered. In this state, when the vane compressor 10 is shaken by vibration or the like, the lubricating oil that has filled the gap 60a is retreated, and refrigerant gas is mixed into the gap 60a, so that the refrigerant gas enters the back pressure chamber 33 and the insertion hole 20b. May be supplied. However, according to the above configuration, since the lubricating oil in the discharge chamber 60 is suppressed from being rolled up, it is possible to suppress the oil level height of the discharge chamber 60 from being lowered. For this reason, it can suppress that refrigerant gas is supplied to back pressure room 33 and penetration hole 20b. That is, it is possible to suppress the supply of the refrigerant gas to the back pressure chamber 33 and the insertion hole 20b by suppressing the rolling-up of the lubricating oil in the discharge chamber 60 and stabilizing the oil surface.

  Further, in the vane compressor 10 described above, the protruding portion 15 is formed on the inner peripheral surface of the rear shell 14. When the lubricating oil discharged from the discharge passage 46 collides with the protrusion 15, the refrigerant gas mixed in the lubricating oil is easily separated from the lubricating oil. In particular, in this embodiment, the flat surface 15a of the protrusion 15 is formed so that the lubricating oil discharged from the discharge passage 46 collides vertically. For this reason, compared with the structure where the collision angle is not vertical, the impact when the lubricating oil collides with the flat surface 15a is increased, and the separation efficiency between the lubricating oil and the refrigerant gas is improved. Accordingly, it is possible to further suppress the refrigerant gas from being mixed into the lubricating oil in the discharge chamber 60. Further, by forming the protruding portion 15 on the rear shell 14, the degree of freedom in designing the protruding portion 15 is improved as compared with a configuration in which the protruding portion 15 is formed on other members such as the rear side plate 20. The refrigerant gas that collides with and is separated from the flat surface 15a of the protrusion 15 is discharged from the discharge port 62 and sent to the condenser.

  Next, the vane type compressor of Example 2 is demonstrated with reference to FIG. Hereinafter, only differences from the first embodiment will be described, and detailed description of the same configurations as those of the first embodiment will be omitted. The same applies to other embodiments.

  In the vane type compressor of the second embodiment, a recess 115 that is recessed from the inner peripheral surface is formed on the inner peripheral surface of the rear shell 14 in the discharge chamber 60. The recess 115 forms a part of the circumferential surface of a cylinder having a height in the depth direction of FIG. 5 (that is, the front-rear direction of FIG. 1). That is, the peripheral surface of the recess 115 shown in FIG. 5 has an arc shape. The recess 115 faces the outlet 46 b of the discharge passage 46, and is formed at a position where the lubricating oil discharged from the outlet 46 b of the discharge passage 46 collides with the recess 115. 5 indicates a virtual extension line in the discharge direction of the lubricating oil discharged from the lowermost part of the outlet 46b of the discharge passage 46. The virtual extension line is a tangent to a virtual circle formed by the arc-shaped peripheral surface of the recess 115 at a boundary point 115 a between the peripheral surface of the recess 115 and the inner peripheral surface of the rear shell 14. For this reason, the lubricant discharged from the outlet 46b collides with the recess 115 (specifically, the peripheral surface near the boundary point 115a), and the lubricant rebounded at the time of the collision moves along the peripheral surface of the recess 115. And stored in the discharge chamber 60. Also with this configuration, the same effects as those of the first embodiment can be obtained. Further, according to the configuration of the present embodiment, most of the lubricating oil that has collided with the peripheral surface of the recess 115 rebounds above the boundary point 115a, so that the lubricating oil can be prevented from rebounding below the boundary point 115a. Therefore, the refrigerant gas separated at the time of the collision can be suppressed from flowing below the boundary point 115a, and the refrigerant gas can be further suppressed from entering the lubricating oil in the discharge chamber 60. The separated refrigerant gas is transferred to the upper side of the discharge chamber 60 along the peripheral surface of the recess 115 and is appropriately discharged from the discharge port 62. That is, the peripheral surface of the recess 115 serves as a guide for guiding the separated refrigerant gas to above the discharge chamber 60. Moreover, since the recessed part 115 is formed by extracting the rear shell 14, the vane type compressor can be reduced in weight. In the above description, for convenience of explanation, the boundary between the peripheral surface of the recess 115 and the inner peripheral surface of the rear shell 14 is referred to as a “boundary point”, but it is noted that the boundary extends in the depth direction of FIG. I want.

  Next, the vane type compressor of Example 3 is demonstrated with reference to FIG. As shown in FIG. 6, the vane compressor of the third embodiment has a configuration in which the compression mechanism C of the vane compressor 10 of the first embodiment is rotated counterclockwise by a predetermined angle (acute angle). . The discharge passage 146 extends in a straight line in the bulging portion 20c in the horizontal direction, and the outflow port 146b is formed on the outer surface of the bulging portion 20c. That is, the outflow port 146b is located at the same height as the inflow port 146a. That is, in the vane type compressor of the present embodiment, the bulging portion 20e is not formed, and the discharge passage 146 is formed in the bulging portion 20c. A protrusion 215 is formed on the inner peripheral surface of the rear shell 14 in the discharge chamber 60. The protrusion 215 has a flat surface 215a. The flat surface 215a is formed so that the lubricating oil discharged from the outlet 146b collides perpendicularly with the flat surface 215a. The passage 64a extends vertically upward from the lowermost portion of the discharge chamber 60. That is, the passage 64a is formed in the rear side plate 20 in advance at an angle that extends vertically upward with the vane compressor attached to the vehicle.

  Also with this configuration, the same effects as those of the first embodiment can be obtained. In the present embodiment, the discharge passage 146 is formed only in the bulging portion 20c, and the length thereof is shorter than the length of the discharge passage 46 of the first embodiment. For this reason, the pressure loss at the time of lubricating oil flowing through the discharge passage 146 can be further reduced. When the vane compressor is rotated and attached to the vehicle as in the present embodiment, the oil separation chamber 52 may be formed so that the lower surface of the oil separation chamber 52 extends in the horizontal direction when attached to the vehicle. Good. Further, the lower surface thereof may be positioned at substantially the same height as the inlet 146a (and outlet 146b) of the discharge passage 146. According to this configuration, the lubricating oil can be efficiently discharged from the discharge passage 146 without the lubricating oil remaining on the lower surface of the oil separation chamber 52.

  As mentioned above, although the Example of the technique which this specification discloses was described in detail, these are only illustrations, and the vane type compressor which this specification discloses is what variously changed and changed said Example. Is included.

  For example, the discharge passage may be formed on the side opposite to the above-described embodiment (that is, the left side in FIGS. 3 to 6) with respect to the oil separator. In this case, the protruding portion or the recessed portion may also be formed on the side opposite to the above embodiment. Moreover, the protrusion part does not need to have a plane. Further, even when the protrusion has a flat surface, the lubricating oil discharged from the discharge passage may not collide with the flat surface perpendicularly. Further, the peripheral surface of the recess is not limited to an arc shape, and may be, for example, an ellipse. Further, even when the peripheral surface of the recess is an arc, the direction in which the lubricant collides with the recess may not be a tangential direction at the boundary of the recess. For example, the lubricating oil may collide with the central portion of the recess.

  Further, a throttle portion having a smaller diameter than the discharge passage 46 may be attached to the outlet 46 b of the discharge passage 46. Thereby, it can suppress that refrigerant gas is contained in the lubricating oil discharged | emitted from the discharge channel | path 46. FIG.

  Further, the invention disclosed in this specification may be applied to a compressor other than the vane compressor.

  Specific examples of the present invention have been described in detail above, but these are merely examples and do not limit the scope of the claims. The technology described in the claims includes various modifications and changes of the specific examples illustrated above. The technical elements described in this specification or the drawings exhibit technical usefulness alone or in various combinations, and are not limited to the combinations described in the claims at the time of filing. In addition, the technology illustrated in the present specification or the drawings achieves a plurality of objects at the same time, and has technical utility by achieving one of the objects.

10: vane type compressor, 11: shell, 12: front shell, 14: rear shell, 15: convex part, 15a: flat surface, 18: front side plate, 20: rear side plate, 20c, 20d, 20e: bulge part, 20f: Base portion, 20f1: Rear end surface, 44: Discharge passage, 44a: Inlet, 44b: Inlet, 46: Discharge passage, 46a: Inlet, 46b: Inlet, 50: Oil separator, 60: Discharge chamber 115: Recess

Claims (5)

Shell,
A compression mechanism disposed in the shell;
A side plate that divides the shell into a first space in which the compression mechanism is disposed and a second space in which lubricating oil contained in the refrigerant gas discharged from the compression mechanism is stored;
An oil separation cylinder for separating the lubricating oil contained in the refrigerant gas discharged from the compression mechanism,
The side plate is
A base section that divides the first space and the second space;
An oil separation chamber forming portion that swells from an end surface of the base portion on the second space side and that forms an oil separation chamber that houses the oil separation cylinder;
The base portion swells from the end surface on the second space side, and is connected to the side wall of the oil separation chamber forming portion, and has a discharge passage that communicates the first space and the upper portion of the oil separation chamber. A discharge passage forming portion to be formed on,
The base portion swells from the end surface on the second space side and is connected to the side wall of the oil separation chamber forming portion, and has a discharge passage that communicates the lower portion of the oil separation chamber and the second space. A discharge passage forming portion formed on the base portion, the oil separation chamber forming portion, the discharge passage forming portion, and the discharge passage forming portion are formed integrally.
The amount of swelling of the discharge passage forming portion decreases as the distance from the oil separation chamber forming portion increases.
The discharge passage is formed in a straight line from the inlet to the outlet,
The discharge passage opens at an end surface of the base portion on the first space side and communicates with the first space;
The discharge passage is formed in a straight line from the inlet to the outlet,
The outlet of the discharge passage is a compressor that opens to the discharge passage forming portion and communicates with the second space.   The compressor according to claim 1, wherein the outlet of the discharge passage is located above the inlet of the discharge passage.   The compressor according to claim 1 or 2, wherein the discharge passage forming portion is formed at a position not facing the outlet of the discharge passage. The shell is formed with a protrusion that protrudes from the inner wall surface of the shell in the second space,
The compressor according to any one of claims 1 to 3, wherein the convex portion is formed at a position facing the outlet of the discharge passage. The shell is formed with a recess that is recessed from the inner wall surface of the shell in the second space,
The said recessed part is a compressor as described in any one of Claims 1-3 currently formed in the position facing the outflow port of the said discharge passage.

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