JP2017180285A - Compressor - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a compressor enabling a sufficient lubrication to be carried out, hardly producing a discharge pulsation and enabling a small-sized formation and a less-expensive manufacturing cost to be realized.SOLUTION: A compressor of this invention comprises a housing 1, a compression mechanism 5, an oil separation mechanism 7 and an oil supplying mechanism 9. The housing 1 has a second side plate 25 and a cover plate 27. An oil discharging passage 71 is comprised of a first flow passage 71a passed and arranged at the cover plate 27 and extending from an oil separation chamber 65 toward a second side plate 25; and a second flow passage 71c recessed at the cover plate 27 and communicated with the first flow passage 71a. The second flow passage 71c is formed by aligning the second side plate 25 with the cover plate 27 and an outlet 71d of the second flow passage 71c is positioned more upwardly in a vertical direction than an inlet 71b.SELECTED DRAWING: Figure 1

Description

  The present invention relates to a compressor.

  Patent Document 1 discloses a conventional vane type compressor. In this compressor, a cylinder block is accommodated in a housing, and a front side plate and a rear side plate are joined and fixed to both ends thereof. An oil storage chamber, which is a discharge chamber, is formed between the rear side plate and the housing. An oil separator is provided on the rear side plate. The oil separator includes a case and an oil separation cylinder fixed to an upper portion of an oil separation chamber formed in the case.

  Lubricating oil is separated from the refrigerant in the oil separation chamber. The refrigerant from which the lubricating oil is separated is discharged from the discharge chamber to an external refrigeration circuit. On the other hand, the lubricating oil in the oil separation chamber is stored in the oil storage chamber through the oil drain passage. Lubricating oil in the oil storage chamber is supplied to sliding portions such as a vane groove and a bearing as a back pressure chamber that forms a back pressure for pressing the vane through an oil supply passage communicating with the oil storage chamber.

Japanese Patent Laid-Open No. 7-12072

  However, in the above compressor, the oil drainage passage connects the oil separation chamber and the oil storage chamber in a straight line, and the flow rate of the lubricating oil is difficult to decrease. When the amount is large, the lubricating oil discharged from the oil discharge passage is easily rolled up by the lubricating oil in the oil storage chamber. For this reason, the refrigerant in the discharge chamber easily mixes with the lubricating oil in the oil storage chamber, and the lubricating oil mixed with the refrigerant is easily supplied from the opening of the oil supply passage to the vane groove and the bearing. In this case, lubrication with the lubricating oil is not sufficiently performed at the sliding portion, noise and vibration may be generated and silence may be impaired, and durability may also be impaired.

  In order to eliminate this concern, for example, as described in Japanese Patent Application Laid-Open No. 2010-31757 or the like, a space for storing lubricating oil in the case of the oil separator may be defined in the discharge chamber. In this case, it is difficult to mix the lubricant oil that is sequentially discharged from the oil drainage path and the separated refrigerant gas, and supply the lubricant oil that is not so mixed with the refrigerant to the vane groove and the sliding portion. It is considered that the durability and durability can be realized.

  However, as described above, if a space for storing lubricating oil is provided in the case of the oil separator, the oil separator becomes large and processing becomes troublesome. If the size of the oil separator is increased, the volume of the discharge chamber is reduced and discharge pulsation is likely to occur, or the entire compressor is increased in size and the mountability to a vehicle or the like is impaired. In addition, troublesome processing increases the manufacturing cost.

  The present invention has been made in view of the above-described conventional situation, and provides a compressor capable of sufficient lubrication, hardly causing discharge pulsation, and capable of realizing downsizing and manufacturing cost reduction. Is a problem to be solved.

The compressor of the present invention includes a housing,
A compression mechanism that is housed in the housing to form a suction chamber, a discharge chamber, and a compression chamber together with the housing, sucks the refrigerant in the suction chamber into the compression chamber, compresses it, and discharges it to the discharge chamber;
An oil separation mechanism that is provided in the discharge chamber and separates the lubricant from the refrigerant and stores the lubricant in the discharge chamber;
An oil supply mechanism that guides the lubricating oil in the discharge chamber to the compression mechanism;
The housing includes a housing body having an inner peripheral surface extending in a circumferential direction, a first partition body provided in the housing body and partitioning the compression chamber and the discharge chamber, and the first partition body And a second partition body provided with the oil separation mechanism,
The oil separation mechanism is formed in the second partition body and separates the lubricating oil from the refrigerant guided from the compression chamber; and an oil discharge passage that communicates the oil separation chamber with the discharge chamber. Have
The oil supply mechanism is a compressor that is formed in the second partition body and has an oil supply port that opens downward in the vertical direction so as to take in the lubricating oil in the discharge chamber,
The oil drainage passage is provided in the second partition body, and opens from the oil separation chamber toward the first partition body, and includes at least one of the first partition body and the second partition body. Consists of a second channel formed in cooperation with the first partition body and the second partition body so as to be recessed in one side and communicate with the first channel,
The outlet of the second flow path is located vertically above the inlet of the second flow path while avoiding a direction toward the fuel filler port.

  In the compressor of this invention, the 1st division body and 2nd division body of the housing are couple | bonded, and the oil drainage path consists of the 1st flow path and the 2nd flow path. The first flow path penetrates through the second partition and extends from the oil separation chamber toward the first partition. For this reason, the lubricating oil discharged from the oil separation chamber first collides with the first partition body, and its momentum is alleviated.

  Further, the second flow path is recessed in at least one of the first partition body and the second partition body, is formed by cooperation of the first partition body and the second partition body, and communicates with the first flow path. The outlet of the second channel is located vertically above the inlet of the second channel. For this reason, the direction in which the lubricating oil is discharged from the outlet of the second flow path is not suitable for the oil supply port.

  For this reason, in this compressor, even when the amount of lubricating oil stored in the discharge chamber is large, the lubricating oil sequentially discharged from the oil separation chamber is difficult to wind up the lubricating oil in the discharge chamber. It is difficult to wind up the lubricant. For this reason, it is difficult for the refrigerant in the discharge chamber to be mixed again with the lubricating oil in the discharge chamber, and the lubricating oil that is stored in the discharge chamber and hardly contains the refrigerant is easily supplied from the oil supply port to the compression mechanism. For this reason, in this compressor, lubrication is sufficiently performed in the compression mechanism. For this reason, noise and vibration are less likely to occur, high silence is exhibited, and high durability is also exhibited.

  Moreover, in this compressor, a 2nd division body is not enlarged and a process is also easy. For this reason, in this compressor, it is easy to suppress the discharge pulsation by securing a large volume of the discharge chamber, and it is possible to realize the downsizing of the whole compressor and exhibit high mountability to a vehicle or the like. In addition, the compressor can be easily processed, so that the manufacturing cost can be reduced.

  Therefore, the compressor of the present invention can be sufficiently lubricated, hardly cause discharge pulsation, and can be downsized and the manufacturing cost can be reduced.

  It is preferable that the outlet of the second flow path faces the inner peripheral surface of the housing body. In this case, the lubricating oil sequentially discharged from the second flow path collides with the inner peripheral surface of the housing body, and the momentum is alleviated. For this reason, the effect of the present invention is more likely to occur.

  When the normal line is defined at a position where the outlet of the second flow path faces the inner peripheral surface of the housing body, the second flow path preferably intersects the normal line at an acute angle. In this case, the lubricating oil sequentially discharged from the second flow path is guided along the inner peripheral surface of the housing body. For this reason, the effect of the present invention is more likely to occur.

  The housing includes a cylinder block in which a cylinder chamber is formed, a housing body surrounding the cylinder block, a first partition body that forms a discharge chamber between the cylinder block and the housing body, and a second partition body. obtain. The compression mechanism may include a rotor provided in the cylinder chamber so as to be rotatable around a rotation axis, and a plurality of vane grooves formed therein, and a vane provided in each vane groove so as to be protruded and retracted. The compression mechanism can form a compression chamber by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and each vane. A back pressure chamber may be provided between each vane groove and each vane. The fuel filler port can communicate with the back pressure chamber through the back pressure channel. In this case, the present invention can be embodied as a vane type compressor.

  The first partition may be a side plate that forms one surface of the cylinder chamber. The first partition body may be a gasket.

  The compressor of the present invention can be sufficiently lubricated, and discharge pulsation hardly occurs. For this reason, in this compressor, higher silence and durability can be realized. In addition, the compressor can be downsized and the manufacturing cost can be reduced.

FIG. 1 is a cross-sectional view of the vane type compressor according to the first embodiment. FIG. 2 is a cross-sectional view taken along the line II-II in FIG. 3 is an enlarged cross-sectional view of a main part of FIG. 1 according to the vane type compressor of the first embodiment. FIG. 4 is a cross-sectional view taken along the line IV-IV in FIG. FIG. 5 is a cross-sectional view taken along line VV in FIG. FIG. 6 is a back view of the gasket according to the vane type compressor of the first embodiment. FIG. 7 is a rear view of the cover plate according to the vane type compressor of the first embodiment. FIG. 8 is a partial cross-sectional view similar to FIG. 4 according to the vane type compressor of the second embodiment. FIG. 9 is a partial cross-sectional view similar to FIG. 4 according to the vane type compressor of the third embodiment.

  Embodiments 1 to 3 embodying the present invention will be described below with reference to the drawings. In the following description, the left side of FIG. 1 is the front side of the compressor, and the right side of FIG. 1 is the rear side of the compressor. Further, the upper side of the page of FIG. 1 is the upper side of the compressor, and the lower side of the page of FIG. 1 is the lower side of the compressor. In FIG. 2 and subsequent figures, the front-rear direction and the vertical direction are displayed in correspondence with FIG. In addition, the front-rear direction and the up-down direction in Examples 1 to 3 indicate the front-rear direction and the up-down direction when the compressor of the present invention is mounted on a vehicle, and the up-down direction corresponds to the vertical direction. Since the mounting posture of the compressor is appropriately changed in accordance with the vehicle or the like to be mounted, the front-rear direction and the vertical direction in the first to third embodiments are examples, and the present invention is not limited to this.

Example 1
The electric vane type compressor (hereinafter simply referred to as a compressor) of Example 1 shown in FIG. 1 is an example of a specific aspect of the compressor of the present invention. The compressor includes a housing 1, a motor mechanism 3, a compression mechanism 5, an oil separation mechanism 7, and an oil supply mechanism 9. The motor mechanism 3 is housed in the housing 1 and operates the compression mechanism 5. The compression mechanism 5 is housed in the housing 1 and forms a suction chamber 11, a discharge chamber 13 and compression chambers 15 together with the housing 1. The compression mechanism 5 sucks the refrigerant in the suction chamber 11 into each compression chamber 15, compresses it, and discharges it to the discharge chamber 13. The oil separation mechanism 7 is provided in the discharge chamber 13, separates the lubricating oil from the refrigerant, and stores the lubricating oil in the discharge chamber 13. The oil supply mechanism 9 guides the lubricating oil in the discharge chamber 13 to the compression mechanism 5.

  Specifically, the housing 1 includes a motor housing 17, a gasket 43, a compressor housing 19, a first side plate 21, a cylinder block 23, a second side plate 25, a gasket 59 and a cover plate 27. The compressor housing 19 corresponds to the housing body of the present invention, the second side plate 25 and the gasket 59 correspond to the first partition body of the present invention, and the cover plate 27 corresponds to the second partition body of the present invention.

  In the motor housing 17, a cylindrical peripheral wall 17a extends in the axial direction from the front end side to the rear end side. The peripheral wall 17a is closed at the front end side by the front wall 17b and has an opening 17c on the rear end side. The motor housing 17 forms a suction chamber 11 that also serves as a motor chamber. A suction port 17d communicating with the suction chamber 11 is formed in the peripheral wall 17a. A bearing 29 is provided on the front wall 17b, and a rotary shaft 31 is provided on the bearing 29 so as to be rotatable around the rotation axis X1. An evaporator is connected to the suction port 17d by a pipe (not shown). A compressor, a condenser, an expansion valve, and an evaporator constitute a vehicle air conditioner. The refrigerant that has passed through the evaporator is sucked into the suction chamber 11 from the suction port 17d.

  A stator 33 is fixed inside the peripheral wall 17 a of the motor housing 17, and a motor rotor 35 is fixed to the rotating shaft 31. The motor rotor 35 is disposed in the stator 33. A connection terminal 37 is fixed to the front wall 17b, and a lead wire 39 extending from the outside to the stator 33 in the suction chamber 11 is provided on the connection terminal 37. The lead wire 39 is provided with a cluster block 41 in the peripheral wall 17. The stator 33, motor rotor 35, connection terminal 37, lead wire 39 and cluster block 41 constitute the motor mechanism 3.

  A compressor housing 19 is fixed to the rear end of the motor housing 17 by a plurality of bolts (not shown). The compressor housing 19 has a cylindrical peripheral wall 19a extending in the axial direction from the front end side to the rear end side. The peripheral wall 19a is closed at the rear end side by the rear wall 19b and has an opening 19c on the front end side. The peripheral wall 19a has an inner peripheral surface 19d extending in the circumferential direction. The inner peripheral surface 19d is coaxial with the rotation axis X1.

  The opening 19c of the compressor housing 19 is coupled to the opening 17c of the motor housing 17, and both the motor housing 17 and the compressor housing 19 are closed. A gasket 43 is provided between the opening 17 c of the motor housing 17 and the opening 19 c of the compressor housing 19. A first side plate 21 is fixed to the compressor housing 19 on the opening 19 c side together with the motor housing 17. The first side plate 21 extends in the radial direction, forms the suction chamber 11 between the motor housing 17 and the cylinder block 23, and partitions the compression chamber 15 and the suction chamber 11. An O-ring 45 is provided between the first side plate 21 and the compressor housing 19. A shaft hole 21 a is formed in the first side plate 21 coaxially with the bearing 29. The rotating shaft 31 is inserted into the shaft hole 21a.

  A cylinder block 23, a second side plate 25, and a cover plate 27 are accommodated in the compressor housing 19. As shown in FIG. 2, the cylinder block 23 and the second side plate 25 are assembled to the rear surface of the first side plate 21 by a plurality of bolts 47. As shown in FIG. 1, the cylinder block 23 is sandwiched between the first side plate 21 and the second side plate 25 from the front and rear. The second side plate 25 is fitted to the inner peripheral surface 19 d of the compressor housing 19. An O-ring 47 is provided between the second side plate 25 and the inner peripheral surface 19d. A shaft hole 25a is formed in the second side plate 25 coaxially with the bearing 29 and the shaft hole 21a. The rotary shaft 31 is also inserted into the shaft hole 25a.

  As shown in FIG. 2, the cylinder block 23 is formed with a cylinder chamber 23a. As shown in FIG. 1, the cylinder chamber 23 a is closed by the rear surface of the first side plate 21 and the front surface of the second side plate 25. A rotor 49 is integrally fixed to the rotary shaft 31 between the first side plate 21 and the second side plate 25. The rotor 49 is rotatable around the rotation axis X1 in the cylinder chamber 23a. As shown in FIG. 2, the rotor 49 is formed with a plurality of vane grooves 49a. Each vane 51 is provided in each vane groove 49a so that it can appear and disappear.

  The cylinder block 23 is formed with a suction passage 23b and a suction port 23c. The suction passage 23b extends in the front-rear direction in parallel with the rotation axis X1. The suction passage 23b communicates with the cylinder chamber 23a through a suction port 23c. Further, a discharge space 23 d is formed between the cylinder block 23 and the inner peripheral surface 19 d of the compressor housing 19. The discharge space 23d communicates with the cylinder chamber 23a through a discharge port 23e. A discharge reed valve 53 that opens and closes the discharge port 23e and a discharge retainer 55 that regulates the opening degree of the discharge reed valve 53 are provided in the discharge space 23d. The discharge reed valve 53 and the discharge retainer 55 are fixed to the cylinder block 23 by bolts 57.

  As shown in FIG. 1, the first side plate 21 is provided with a suction passage 21a that allows the suction chamber 11 and the suction passage 23b to communicate with each other. A gasket 59 is provided between the second side plate 25 and the cover plate 27. As shown in FIGS. 3 to 5, the second side plate 25, the gasket 59, and the cover plate 27 are assembled and fixed by a plurality of bolts 76. The second side plate 25, the gasket 59 and the cover plate 27 extend in the radial direction to form a discharge chamber 13 between the cylinder block 23 and the compressor housing 19, and partition the compression chamber 15 and the discharge chamber 13. ing.

  The second side plate 25, the gasket 59, and the cover plate 27 are provided with an introduction passage 25b that allows the discharge space 23d to communicate with an oil separation chamber 27a described later. The first side plate 21, the cylinder block 23, the second side plate 25, the rotor 49, each vane 51, the discharge reed valve 53, the discharge retainer 55, and the bolt 57 constitute the compression mechanism 5. In the compression mechanism 5, the compression chamber 15 is formed by the front surface of the cylinder chamber 23 a, the inner peripheral surface of the cylinder chamber 23 a, the rear surface of the cylinder chamber 23 a, the outer peripheral surface of the rotor 49, and the vanes 51. A back pressure chamber 61 is formed between each vane groove 49 a and each vane 51.

  As shown in FIG. 5, the second side plate 25 and the cover plate 27 are coupled to each other by an annular coupling region 73 via a gasket 59. Between the second side plate 25 and the cover plate 27, an intermediate pressure chamber 69 is formed that is located on the side of the rotation axis X1 with respect to the coupling region 73. As shown in FIGS. 3 and 4, the intermediate pressure chamber 69 separates a part of the second side plate 25 and a part of the cover plate 27 in the direction of the rotation axis X1. When viewed from the direction of the rotational axis X1, the intermediate pressure chamber 69 is disposed so as to overlap at least part of the rear surface of the cylinder chamber 23a.

  As shown in FIGS. 3 to 5, the cover plate 27 is provided with an oil separation mechanism 7. The oil separation mechanism 7 includes a cylindrical member 63, an oil separation chamber 65, and an oil drain passage 71. As shown in FIG. 3, the oil separation chamber 65 is coaxially wound in a columnar shape while communicating with the upper chamber 65a on the lower side of the upper chamber 65a and from the upper chamber 65a. The lower chamber 65b has a slightly small diameter. As shown in FIG. 5, the upper chamber 65 a and the lower chamber 65 b are formed so that the upper portion is slightly inclined inward with respect to the vertical direction on the slightly left side of the cover plate 27 in the drawing.

  A cylindrical tube member 63 is fixed to the upper end of the upper chamber 65a. As shown in FIG. 3, the cylindrical member 63 is formed with a large diameter and is press-fitted into the upper chamber 65a, and is integrally and coaxial with the large diameter portion 63a below the large diameter portion 63a. The small-diameter portion 63b is slightly smaller in diameter than the large-diameter portion 63a. The refrigerant guided to the oil separation chamber 65 from the discharge space 23d through the introduction passage 25b swirls in an annular space formed by the small diameter portion 63b and the inner peripheral surface of the upper chamber 65a. For this reason, centrifugal force acts on the refrigerant, the contained lubricating oil is separated, drops on the inner peripheral surface of the upper chamber 65a, and moves to the lower chamber 65b.

  As shown in FIG. 1, a discharge port 19 e is formed in the peripheral wall 19 a of the compressor housing 19. A condenser is connected to the discharge port 19e by a pipe (not shown). The refrigerant from which the lubricating oil is separated in the oil separation chamber 65 is discharged from the discharge port 19e to the condenser.

  As shown in FIG. 4, the cover plate 27 is formed with a through hole 71a extending at a right angle to the end surface of the gasket 59, which is the coupling region 73, at the lower end of the lower chamber 65b. The through hole 71a extends in the tangential direction from the direction in which the refrigerant swirls in the lower chamber 65b. As shown in FIG. 6, the gasket 59 has a flat end face facing the through hole 71 a of the cover plate 27. The through hole 71a is the first flow path. Further, as shown in FIGS. 4 and 7, the cover plate 27 is provided with a linear groove 71 c that communicates with the through hole 71 a and extends linearly on the outer peripheral side. The straight groove 71c is a recess. A straight groove 71c formed by combining the surfaces so that the end face of the cover plate 27 in which the straight groove 71c is formed and the end face of the gasket 59 face each other is the second flow path of the present invention.

  One end of the linear groove 71 c is an inlet 71 b that communicates with the through hole 71 a, and the other end is an outlet 71 d that opens to the discharge chamber 13. As shown in FIG. 7, the outlet 71d is located vertically above the inlet 71b. That is, the linear groove 71c extends at an angle of θ ° with respect to the horizontal direction when the compressor is mounted on the vehicle. Thereby, as shown in FIG. 5, the linear groove 71c is extended in the direction away from the oil supply port 75c mentioned later. Further, as shown in FIGS. 4 and 5, the outlet 71 d of the linear groove 71 c faces the inner peripheral surface 19 d of the compressor housing 19 with only a few millimeters. More specifically, as shown in FIG. 5, when the normal line L is defined at a position where the outlet 71d faces the inner peripheral surface 19d, the straight groove 71c intersects the normal line L at an acute angle. The through hole 71 a and the straight groove 71 c are the oil drainage passage 71.

  The cover plate 27 is formed with first and second oil flow paths 75a and 75b. The first oil passage 75a communicates with the bottom of the discharge chamber 13 at the lower end oil supply port 75c, and extends upward so as to approach the rotation axis X1. The second oil passage 75b extends to the intermediate pressure chamber 69 while continuing to the upper end of the first oil passage 75a. Thereby, the lubricating oil in the discharge chamber 13 is taken into the first and second oil flow paths 75 a and 75 b from the oil supply port 75 c and led to the intermediate pressure chamber 69. At this time, the first and second oil flow paths 75a and 75b function as throttle flow paths, and the lubricating oil is set so that the intermediate pressure chamber 69 has a lower pressure than the discharge chamber 13 and a higher pressure than the suction chamber 11. Is introduced into the intermediate pressure chamber 69.

  As shown in FIGS. 1 and 3, the second side plate 25 is provided with a communication passage 77 that communicates the intermediate pressure chamber 69 and the back pressure chamber 61. Further, the second side plate 25 is formed with an oil groove 25c having an annular shape coaxial with the rotation axis X1. Further, as shown in FIG. 1, the first side plate 21 is formed with an oil groove 21b that is coaxial with the rotation axis X1. The oil grooves 21 b and 25 c communicate with the bottom of each vane groove 49 a regardless of the rotation of the rotor 49. The oil supply port 75c, the first and second oil passages 75a and 75b, the intermediate pressure chamber 69, the communication passage 77, and the oil groove 25c are back pressure passages. The oil supply mechanism 75 includes the oil supply port 75 c, the first and second oil flow paths 75 a and 75 b, the intermediate pressure chamber 69, the communication passage 77, the oil groove 25 c, the back pressure chamber 61, and the oil groove 21 b.

  In this compressor, when electric power is supplied to the stator 33 shown in FIG. 1, the motor mechanism 3 operates and the rotating shaft 31 rotates around the rotation axis X1. For this reason, the compression mechanism 5 operates and the rotor 49 rotates in the cylinder chamber 23a. At this time, in the cylinder chamber 23 a, each vane 51 appears and disappears with respect to the vane groove 49 a according to the rotation of the rotor 49. Therefore, the refrigerant in the suction chamber 11 is sucked into the compression chamber 15, compressed in the compression chamber 15, and discharged into the discharge chamber 13.

  At this time, the lubricating oil is separated from the refrigerant in the oil separation chamber 65 of the oil separation mechanism 7. The refrigerant from which the lubricating oil has been separated is supplied from the discharge chamber 13 to the external condenser via the discharge port 19e. On the other hand, the lubricating oil in the oil separation chamber 65 is stored in the lower portion of the discharge chamber 13 through the oil drain passage 71.

  In the meantime, in this compressor, the second side plate 25 and the cover plate 27 are joined in the joining region 73, and the oil drainage passage 71 is composed of the through hole 71a and the straight groove 71c. The through hole 71 a extends through the cover plate 27 and extends from the lower chamber 65 b of the oil separation chamber 65 to the end surface of the gasket 59 that is the coupling region 73. For this reason, the lubricating oil sequentially discharged from the oil separation chamber lower chamber 65b first collides with the end face of the gasket 59, the direction of flow is changed, and the momentum is relaxed.

  The straight groove 71 c is recessed in the coupling region 73 of the cover plate 27. The outlet 71d of the straight groove 71c is located vertically above the inlet 71b. For this reason, the linear groove 71c communicates with the through hole 71a and extends so that the outlet 71d opens in a direction different from the direction toward the oil supply port 75c. For this reason, the lubricating oil sequentially discharged from the linear groove 71c is discharged into the discharge chamber 13 so as to leave the oil supply port 75c. In particular, in this compressor, since the outlet 71d of the linear groove 71c faces the inner peripheral surface 19d of the compressor housing 19, the lubricating oil sequentially discharged from the linear groove 71c also collides with the inner peripheral surface 19d. That is, the lubricating oil flowing in the oil drain passage 71 changes its flow through a bent path until it is stored in the discharge chamber 13, and collides with the wall surface at least twice. Alleviated. Further, since the straight groove 71c intersects the normal L at an acute angle, the lubricating oil sequentially discharged from the straight groove 71c is guided along the inner peripheral surface 19d.

  For this reason, in this compressor, even when the amount of lubricating oil stored in the discharge chamber 13 is large, the lubricating oil sequentially discharged from the oil separation chamber 65 does not easily wind up the lubricating oil in the discharge chamber 13. For this reason, it is difficult for the refrigerant in the discharge chamber 13 to be mixed with the lubricating oil in the discharge chamber 13 again. In particular, since the outlet 71d of the linear groove 71c is not directed toward the oil supply port 75c, the lubricating oil discharged from the outlet 71d is suppressed from disturbing the refrigerant gas and the lubricating oil around the oil supply port 75c. For this reason, the lubricating oil that is stored in the discharge chamber 13 and contains almost no refrigerant is easily supplied to the compression mechanism 5 from the oil supply port 75c. Specifically, the lubricating oil taken in from the oil supply port 75 c reaches the intermediate pressure chamber 69 from the first and second oil flow paths 75 a and 75 b, and passes through the oil groove 25 c and the communication passage 77 from the intermediate pressure chamber 69. It is supplied to the pressure chamber 61. The lubricating oil in each back pressure chamber 61 lubricates the sliding portion between the vane groove 49a and the vane 51, and also lubricates the sliding portion between each vane 51 and the cylinder chamber 23a. The lubricating oil in each back pressure chamber 61 lubricates the shaft holes 21a and 25a through the oil grooves 21b and 25c. Thus, in this compressor, the compression mechanism 5 is sufficiently lubricated. For this reason, noise and vibration are less likely to occur, high silence is exhibited, and high durability is also exhibited. Moreover, since each vane 51 can be stably pressed by hydraulic pressure compared with the case where refrigerant gas is mixed, chattering of each vane 51 can be prevented and the quietness of the compressor can be improved.

  Moreover, in this compressor, since the end surface of the cover plate 27 provided with the linear groove 71c and the end surface of the gasket 59 are opposed to each other and the end surfaces are aligned with each other, the second flow path is formed. Processing is easy without increasing the size. For this reason, in this compressor, it is easy to suppress the discharge pulsation by securing a large volume of the discharge chamber 13, and it is possible to realize the downsizing of the entire compressor and exhibit high mountability to a vehicle or the like. In addition, the compressor can be easily processed, so that the manufacturing cost can be reduced.

  Accordingly, this compressor can be sufficiently lubricated, hardly cause discharge pulsation, and can be downsized and manufactured at a low cost.

(Example 2)
In the compressor of Example 2, as shown in FIG. 8, the cover plate 27 has a flat end surface on the outer peripheral side of the through hole 71a. Further, the gasket 59 is provided with a through hole 71e that is aligned with the through hole 71a of the cover plate 27. The second side plate 25 is formed with a linear straight groove 71f that communicates with the through hole 71a and the through hole 71e. The end face of the gasket 59 in which the through hole 71e is formed and the end face of the second side plate 25 in which the linear groove 71f is formed are formed so as to face each other. The through hole 71e and the linear groove 71f Is the second flow path of the present invention. The through hole 71 a, the through hole 71 e and the straight groove 71 c are the oil drainage passage 71.

  Other configurations are the same as those of the first embodiment. This compressor can achieve the same effects as those of the first embodiment.

(Example 3)
In the compressor of Example 3, as shown in FIG. 9, the cover plate 27 has a flat end surface on the outer peripheral side of the through hole 71a. The second side plate 25 also has a flat end surface on the outer peripheral side. The gasket 59 is formed with a linear notch 71g communicating with the through hole 71a of the cover plate 27. The end surfaces of the cover plate 27 and the end surface of the second side plate 25 are formed so that the end surfaces of the cover plate 27 and the end surfaces of the second side plate 25 face each other with respect to both end surfaces of the gasket 59 in which the notches 71g are formed. This is the second flow path of the invention. The through hole 71 a and the notch 71 g are the oil drainage passage 71.

  Other configurations are the same as those of the first embodiment. This compressor can achieve the same effects as those of the first embodiment.

  In the above, the present invention has been described with reference to the first to third embodiments. However, the present invention is not limited to the first to third embodiments, and can be appropriately modified and applied without departing from the spirit of the present invention. Needless to say.

  For example, in the first to third embodiments, the second flow path is formed in a straight line by the straight straight groove 71c, the straight groove 71f, or the notch 71g, but the second flow path may be formed in a curved shape.

  In the compressors according to the first to third embodiments, the three vanes 51 are provided. However, the number of vanes is not limited to three. For example, the number of vanes may be two or four.

  In the first to third embodiments, the present invention is embodied in the vane type compressor, but the present invention can also be embodied in a scroll type compressor or the like.

  The present invention is applicable to an air conditioner such as a vehicle.

DESCRIPTION OF SYMBOLS 1 ... Housing 11 ... Suction chamber 13 ... Discharge chamber 15 ... Compression chamber 5 ... Compression mechanism 7 ... Oil separation mechanism 9 ... Oil supply mechanism 19d ... Inner peripheral surface 19 ... Housing main body (compressor housing)
25, 59 ... 1st division body (25 ... 2nd side plate, 59 ... gasket)
27 ... Second compartment (cover plate)
65 ... Oil separation chamber 71 ... Oil drain passage 75c ... Oil supply port 71a ... First flow path (through hole)
71c ... 2nd flow path (straight groove)
71b ... Inlet 71d ... Outlet L ... Normal 23a ... Cylinder chamber 23 ... Cylinder block X1 ... Rotational axis 49a ... Vane groove 49 ... Rotor 51 ... Vane 61 ... Back pressure chamber 75c, 75a, 75b, 69, 77, 25c ... Back pressure channel

Claims (6)

A housing;
A compression mechanism that is housed in the housing to form a suction chamber, a discharge chamber, and a compression chamber together with the housing, sucks the refrigerant in the suction chamber into the compression chamber, compresses it, and discharges it to the discharge chamber;
An oil separation mechanism that is provided in the discharge chamber and separates the lubricant from the refrigerant and stores the lubricant in the discharge chamber;
An oil supply mechanism that guides the lubricating oil in the discharge chamber to the compression mechanism;
The housing includes a housing body having an inner peripheral surface extending in a circumferential direction, a first partition body provided in the housing body and partitioning the compression chamber and the discharge chamber, and the first partition body And a second partition body provided with the oil separation mechanism,
The oil separation mechanism is formed in the second partition body and separates the lubricating oil from the refrigerant guided from the compression chamber; and an oil discharge passage that communicates the oil separation chamber with the discharge chamber. Have
The oil supply mechanism is a compressor that is formed in the second partition body and has an oil supply port that opens downward in the vertical direction so as to take in the lubricating oil in the discharge chamber,
The oil drainage passage is provided in the second partition body, and opens from the oil separation chamber toward the first partition body, and includes at least one of the first partition body and the second partition body. Consists of a second channel formed in cooperation with the first partition body and the second partition body so as to be recessed in one side and communicate with the first channel,
The compressor is characterized in that the outlet of the second flow path is positioned vertically above the inlet of the second flow path while avoiding the direction toward the fuel filler port.   The compressor according to claim 1, wherein the outlet of the second flow path faces the inner peripheral surface of the housing body.   The normal line is defined at a position where the outlet of the second flow channel faces the inner peripheral surface of the housing body, and the second flow channel intersects the normal line at an acute angle. 2. The compressor according to 2. The housing includes a cylinder block in which a cylinder chamber is formed, the housing body surrounding the cylinder block, the first partition body forming the discharge chamber between the cylinder block and the housing body, A second compartment,
The compression mechanism is provided in the cylinder chamber so as to be rotatable around a rotation axis, and a rotor formed with a plurality of vane grooves;
A vane provided so as to be able to appear and disappear in each vane groove,
The compression mechanism forms the compression chamber by one surface of the cylinder chamber, the inner peripheral surface of the cylinder chamber, the other surface of the cylinder chamber, the outer peripheral surface of the rotor, and the vanes,
A back pressure chamber is formed between each vane groove and each vane.
The compressor according to any one of claims 1 to 3, wherein the oil supply port communicates with the back pressure chamber through a back pressure channel.   The compressor according to claim 4, wherein the first partition is a side plate that forms one surface of the cylinder chamber.   The compressor according to claim 4, wherein the first partition body is a gasket.

Images