JP5104644B2 - Compressor - Google Patents

Description

  The present invention relates to a compressor having an oil separator.

  For example, as disclosed in Patent Document 1, in a vane rotary compressor (compressor), a cylinder (cylinder block) is accommodated in a housing, and a front side block (front side plate) is provided on each end surface of the cylinder. ) And the rear side block (rear side plate) are joined. A rotor is rotatably accommodated in the cylinder, and the rotor is provided with a plurality of vanes. A compression chamber is formed in the cylinder by these vanes and both side blocks. The refrigerant gas is compressed in the compression chamber by rotating the rotor and the vane.

  Further, in Patent Document 1, a discharge chamber (discharge region) into which compressed high-pressure refrigerant gas is discharged is formed in the housing, and refrigeration oil (lubricating oil) is separated from the refrigerant gas in the rear side block. A cyclone block (oil separator) is attached. The centrifugal main body of the cyclone block is formed with a cylindrical inner wall surface (oil separation chamber) surrounded by a cylindrical inner wall surface for rotating the refrigerant gas and a bottom wall surface continuous with the cylindrical inner wall surface. The cyclone block has an inner cylindrical gas exhaust part (oil separation cylinder) disposed in the columnar space. The gas exhaust part has a hollow cylinder part that spirally turns the refrigerant gas introduced into the centrifugal separation body part from the introduction hole, and the refrigerant gas after centrifugation is centrifuged at the upper part of the hollow cylinder part. An upper opening that exhausts air to the outside of the main body is formed.

  An oil drain hole for discharging the refrigerating machine oil separated in the cylindrical space to the lower part (oil storage chamber) of the discharge chamber is formed in the lower part of the centrifugal separation main body part in the cyclone block. The oil drain hole is formed so that the opening on the lower side of the discharge chamber is located below the oil level of the refrigerating machine oil stored in the lower portion of the discharge chamber. On the other hand, the opening on the columnar space side of the oil drain hole is formed so that the lower edge thereof is positioned below the bottom wall surface. The oil discharge hole is formed so that the discharge direction of the refrigerating machine oil discharged from the opening on the lower side of the discharge chamber has at least a horizontal component with respect to the oil surface. Further, the rear side block is formed with an oil passage for guiding the refrigerating machine oil stored in the lower portion of the discharge chamber to each sliding portion and the back pressure space.

Then, the refrigerant gas introduced into the cylindrical space in the cyclone block descends spirally downward along the inner wall surface of the cylinder. As a result, the refrigerating machine oil contained in the refrigerant gas is centrifuged on the inner wall surface of the cylinder, and the separated refrigerating machine oil is sprayed onto the bottom wall surface, flows into the oil drainage hole from the opening, and enters the discharge chamber from the opening. Discharged. On the other hand, the refrigerant gas from which the refrigerating machine oil is separated in the cylindrical space rises from the lower opening of the hollow cylinder portion and is discharged into the discharge chamber from the upper opening, and is external to the vane rotary compressor. Discharged.
JP 2008-8259 A

  By the way, in the vane rotary compressor of Patent Document 1, when a high flow rate refrigerant gas in the cylindrical space flows into the oil discharge hole and is discharged from the oil discharge hole toward the discharge chamber, the high flow rate refrigerant gas in the discharge chamber is obtained. Refrigerating machine oil is wound up by the refrigerant gas, and as a result, the amount of refrigerating machine oil in the discharge chamber is reduced and the oil level is lowered. If the oil level fluctuates due to vibration or the like of the vane rotary compressor with the oil level lowered, the refrigerant gas enters the oil passage and is supplied from the oil passage to the compression chamber or the like. Therefore, in order to prevent high-flow-rate refrigerant gas from being discharged into the discharge chamber via the oil drain hole, the volume of the cylindrical space in the cyclone block is increased, and the flow rate of the refrigerant gas is reduced in the cylindrical space. It is possible. However, when the volume of the cylindrical space in the cyclone block is increased, the cyclone block is increased in size, and the physique of the vane rotary compressor is increased in size.

  The present invention has been made paying attention to such problems existing in the prior art, and its purpose is to suppress the rolling-up of the lubricating oil in the oil storage chamber without increasing the size of the compressor. It is to provide a compressor that can.

In order to solve the above-mentioned problems, the invention according to claim 1 is characterized in that the partition member provided in the housing discharges the inside of the housing to the compression mechanism side and the refrigerant gas compressed by the compression mechanism. is partitioned into a region side, the said discharge region, is housed in a state where the oil separator for separating lubricating oil contained in refrigerant gas discharged from the compression mechanism is joined to the partition member, the oil separation The separator is communicated to the outside of the compressor so that the refrigerant gas after oil separation is discharged from the compressor, and the oil separator has an oil separation chamber formed in a cylindrical case and the oil separation An oil separation cylinder extending in the vertical direction is accommodated in the upper part of the chamber, and an oil storage chamber communicated with the sliding portion in the housing via an oil supply passage outside the oil separator in the discharge region. And the oil separator One end a compressor oil discharge hole and the other end with an opening is open toward the outside of the case is formed toward the bottom of the oil separation chamber,
An oil discharge passage connecting the oil discharge hole and the oil storage chamber is provided. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage is connected to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole and at least a part thereof extends upward along the vertical direction. The refrigerant gas flowing through the oil discharge passage is further separated from the lubricating oil after being discharged from the discharge port, and merged with the flow of the refrigerant gas from the oil separator to the outside of the compressor. It is what. Here, “upper part”, “upper part”, and “lowermost part” mean the upper part, the upper part, and the lowermost part when the compressor is mounted on the vehicle.

  According to this, when the high-flow-rate refrigerant gas swirls the oil separation cylinder and then flows into the oil discharge hole, the refrigerant gas flows through the oil discharge hole and then moves upward along the vertical direction in the oil discharge passage. Flow and discharged from the discharge port to the oil storage chamber. For this reason, for example, when the oil discharge passage does not communicate with the oil discharge hole and the refrigerant gas is discharged into the oil storage chamber without flowing upward along the vertical direction after flowing through the oil discharge hole In comparison with this, it is possible to lengthen the distance through which the refrigerant gas flows before being discharged from the oil separation chamber to the oil storage chamber. Therefore, the flow rate of the refrigerant gas discharged into the oil storage chamber can be reduced as compared with when flowing in the oil separation chamber, and the lubricating oil in the oil storage chamber is wound up by the refrigerant gas discharged into the oil storage chamber. Can be suppressed. Therefore, in order to reduce the flow rate of the refrigerant gas discharged from the oil discharge hole to the oil storage chamber, it is not necessary to increase the volume of the oil separation chamber in order to reduce the flow rate in the oil separation chamber. It is possible to prevent the lubricating oil in the oil storage chamber from being rolled up without increasing the size and the size of the compressor.

  The discharge port may be located on the same plane as the lower end of the oil separation cylinder. According to this, since the refrigerant gas swirls above the lower end of the oil separation cylinder in the oil separation chamber, the lubricating oil in the oil separation chamber is pushed downward from the lower end of the oil separation cylinder by this refrigerant gas. . Therefore, it is possible to store lubricating oil below the lower end of the oil separation cylinder in the oil separation chamber. Therefore, a large amount of lubricating oil can be stored in the oil separation chamber by positioning the discharge port on the same plane as the lower end of the oil separation cylinder.

  The oil discharge passage is formed in a groove shape on the end surface of the partition member, and is formed by joining the partition member and the oil separator, and the discharge port is connected to the partition member. You may open toward the said oil storage chamber from the edge of the mating surface with the said oil separator. According to this, it is only necessary to form an oil discharge passage in the shape of a groove on the end face of the partition member. For example, when the partition member is formed of a metal material, the oil discharge passage is simply formed by casting the partition member. It can be formed, and the manufacturing cost of the oil discharge passage can be kept low.

  The oil separator is joined to the partition member via a gasket, and the oil discharge passage is recessed in a surface of the gasket facing the partition member, and the partition member and the oil separator are It is formed by joining via a gasket, and the discharge port may open from the edge of the mating surface of the partition member and the gasket toward the oil storage chamber. According to this, it is possible to form the oil discharge passage only by recessing the oil discharge passage in the gasket, the manufacturing cost of the oil discharge passage can be kept low, and further the lubricating oil from the oil discharge passage can be reduced by the gasket. In addition, leakage of the refrigerant gas can be prevented.

  Moreover, the collision part which makes the said refrigerant gas collide may be arrange | positioned in the discharge direction of the said refrigerant gas from the said discharge port. According to this, the lubricating oil can be separated from the refrigerant gas by causing the refrigerant gas discharged from the outlet to collide with the collision portion.

  Further, a throttle may be provided on the discharge port side in the oil discharge passage. According to this, when the lubricating oil passes through the discharge port, the large bubble state refrigerant gas contained in the lubricating oil cannot pass through the throttle, and the refrigerant gas is removed from the discharge port of the oil discharge passage. The lubricating oil is discharged.

A mesh member that extends over the entire inner peripheral surface of the case that forms the oil separation chamber and covers the oil discharge hole is provided below the oil separation cylinder in the oil separation chamber. May be. According to this, when the refrigerant gas swirling in the oil separation chamber comes into contact with the mesh member, the flow rate of the refrigerant gas can be reduced, and the refrigerant gas discharged through the oil discharge passage into the oil storage chamber can be reduced. This can contribute to a decrease in the flow rate.
In order to solve the above problems, according to an eighth aspect of the invention, the partition member provided in the housing discharges the inside of the housing to the compression mechanism side and the refrigerant gas compressed by the compression mechanism. An oil separator that separates lubricating oil contained in the refrigerant gas discharged from the compression mechanism is accommodated in the discharge region in a state of being joined to the partition member. In the oil separator, an oil separation chamber is formed in a cylindrical case, and an oil separation tube extending in the vertical direction is accommodated in an upper portion of the oil separation chamber, and the outside of the oil separator in the discharge region The oil storage chamber is partitioned, and the oil separator is further provided with an oil discharge hole in which one end opens toward the bottom of the oil separation chamber and the other end opens out of the case. The oil discharge hole and the front And an oil discharge passage connecting the oil storage chamber. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage has a discharge port that opens to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole and at least a part thereof extends upward along the vertical direction. The end face of the partition member is recessed in a groove shape and is formed by joining the partition member and the oil separator, and the discharge port is a mating surface of the partition member and the oil separator It opens toward the said oil storage chamber from the edge of this.
In order to solve the above-mentioned problems, the invention according to claim 9 is that the partition member provided in the housing discharges the inside of the housing to the compression mechanism side and the refrigerant gas compressed by the compression mechanism. An oil separator that separates lubricating oil contained in the refrigerant gas discharged from the compression mechanism is accommodated in the discharge region in a state of being joined to the partition member. In the oil separator, an oil separation chamber is formed in a cylindrical case, and an oil separation tube extending in the vertical direction is accommodated in an upper portion of the oil separation chamber, and the outside of the oil separator in the discharge region The oil storage chamber is partitioned, and the oil separator is further provided with an oil discharge hole in which one end opens toward the bottom of the oil separation chamber and the other end opens out of the case. The oil discharge hole and the front And an oil discharge passage connecting the oil storage chamber. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage has a discharge port that opens to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole, and at least a part thereof extends upward along the vertical direction. By joining the partition member via a gasket, the oil discharge passage is recessed in a surface of the gasket facing the partition member, and the partition member and the oil separator are joined via the gasket. Further, the discharge port is opened from the edge of the mating surface of the partition member and the gasket toward the oil storage chamber.

  According to the present invention, the rolling-up of the lubricating oil in the oil storage chamber can be suppressed without increasing the size of the compressor.

(First embodiment)
A first embodiment in which the compressor of the present invention is embodied as a vane compressor will be described below with reference to FIGS. In the following description, “front” and “rear” of the vane compressor are the directions of the arrow Y1 shown in FIG. 1, and “upper” and “lower” are the directions of the arrow Y2 shown in FIG. The upper and lower directions are “upper” and “lower” when the vane compressor is mounted on the car.

  As shown in FIG. 1, the housing H of the vane compressor 10 is formed of a rear housing 11 and a front housing 12 joined to a front end surface (one end surface) of the rear housing 11. The rear housing 11 and the front housing 12 are fastened together by a plurality of through bolts B (see FIG. 3). A cylindrical cylinder block 13 is accommodated in the rear housing 11 (housing H). The inner peripheral surface of the cylinder block 13 is formed in an elliptical shape extending vertically (see FIG. 2).

  Further, inside the rear housing 11 (housing H), the front side plate 14 is joined to the front end face (one end face) of the cylinder block 13, and the partition member is attached to the rear end face (other end face) of the cylinder block 13. The rear side plate 15 is joined. The outer peripheral surface of the cylinder block 13, the inner peripheral surface of the rear housing 11 (housing H) facing the outer peripheral surface, and the first end surface that is one end surface facing the cylinder block 13 in the front side plate 14 and the rear side plate 15. A discharge space Da is defined between the end surfaces 14a and 15a. In the front side plate 14, a back pressure groove 14 h is recessed in the end surface facing the cylinder block 13, and in the rear side plate 15, a back pressure groove 15 h is recessed in the end surface facing the cylinder block 13. .

  A rotating shaft 17 is rotatably supported by the front side plate 14 and the rear side plate 15, and the rotating shaft 17 passes through the cylinder block 13. In the cylinder block 13, a cylindrical rotor 18 is fixed to the rotary shaft 17 so as to be integrally rotatable with the rotary shaft 17. As shown in FIG. 2, on the outer circumferential surface of the rotor 18, vane grooves 18a are formed radially at a plurality of locations, and vanes 20 are accommodated in the respective vane grooves 18a so as to be able to appear and retract. Lubricating oil is supplied to each vane groove 18a. Each vane groove 18a is formed such that the front end (one end) can communicate with the back pressure groove 14h of the front side plate 14, and the rear end (other end) can be communicated with the back pressure groove 15h of the rear side plate 15. ing.

  When the tip surface of the vane 20 comes into contact with the inner peripheral surface of the cylinder block 13 due to the rotation of the rotor 18 accompanying the rotation of the rotating shaft 17, the outer peripheral surface of the rotor 18 and the inner peripheral surface of the cylinder block 13 are adjacent to the vane. A pair of compression chambers 21 is defined between the front side plate 14 and the rear side plate 15. In the vane compressor 10, a stroke in which the compression chamber 21 increases in volume with respect to the rotation direction of the rotor 18 is a suction stroke, and a stroke in which the compression chamber 21 decreases in volume is a compression stroke. Therefore, the rear housing 11, the cylinder block 13, the front side plate 14, the rear side plate 15, the rotating shaft 17, the rotor 18, and the vane 20 constitute a compression mechanism C of the vane compressor 10.

  As shown in FIG. 1, in the vane compressor 10, a suction port 24 is formed in the upper part of the front housing 12, and a suction space Sa communicating with the suction port 24 is formed in the front housing 12. Yes. Further, the front side plate 14 is formed with a pair of suction ports 14b communicating with the suction space Sa. The cylinder block 13 is formed with a pair of suction passages 13b penetrating the cylinder block 13 in the entire axial direction. The compression chambers 21 and the suction space Sa in the suction stroke are communicated with each other via the suction port 14b and the suction passage 13b.

  As shown in FIG. 2, each of the outer peripheral surfaces located at the center portion in the vertical direction of the cylinder block 13 and at both side portions of the cylinder block 13 is formed to be recessed from the outer peripheral surface of the cylinder block 13. A discharge chamber 13d is formed by each of the portions recessed from the outer peripheral surface of the cylinder block 13, and the pair of discharge chambers 13d form part of the discharge space Da.

  Each of the discharge chambers 13d includes a step surface 13f extending from the outer peripheral surface of the cylinder block 13 toward the inside of the cylinder block 13, and a mounting surface 13g extending toward the outer peripheral surface of the cylinder block 13 while intersecting the step surface 13f. And the first end surfaces 14 a and 15 a of both side plates 14 and 15 and the inner peripheral surface of the rear housing 11. Of the two discharge chambers 13d, one (left in FIG. 2) discharge chamber 13d is formed such that the step surface 13f is positioned above the mounting surface 13g, and the other (right in FIG. 2) discharge chamber 13d. Is formed such that a step surface 13f is positioned below the mounting surface 13g.

  A discharge port 13a that connects the compression chamber 21 and the discharge chamber 13d (discharge space Da) during the compression stroke is formed in the outer peripheral surface of the central portion in the vertical direction of the cylinder block 13, that is, the mounting surface 13g. Each discharge port 13a can be opened and closed by a discharge valve 22 attached to the attachment surface 13g. The refrigerant gas compressed in the compression chamber 21 pushes the discharge valve 22 away and is discharged to the discharge chamber 13d (discharge space Da) through the discharge port 13a.

  As shown in FIG. 1, a discharge region 30 is defined by a rear side plate 15 on the rear side of the rear housing 11. That is, the interior of the rear housing 11 is partitioned by the rear side plate 15 into the compression mechanism C side and the discharge region 30 side. The discharge region 30 is a space surrounded by the second end surface 15 b as the other end surface of the rear side plate 15 and the rear inner surface of the rear housing 11. The second end surface 15 b is an end surface located on the opposite side of the first end surface 15 a in the thickness direction of the rear side plate 15.

  The second end surface 15b of the rear side plate 15 is formed with a bulging portion 15c that bulges to the rear side with a certain thickness. As shown in FIG. 3, a pair of discharge passages 15e is formed in the bulging portion 15c. The discharge passage 15e communicates with an elongated groove 15f recessed in the rear end surface of the bulging portion 15c and a lower end (one end) of the groove 15f, and extends so as to penetrate the entire rear side plate 15 in the thickness direction. 15g. The diaphragm portion 15g has a circular cross-section perpendicular to the axial direction. Each throttle portion 15g has a front end (one end) that opens toward the discharge chamber 13d (discharge space Da) and communicates with the discharge space Da, and a rear end (other end) that is the lower end (one end) of the groove portion 15f. ) And communicates with each other (see FIG. 1).

  As shown in FIG. 1, the front end of the throttle portion 15g is formed at the center in the vertical direction of the rear side plate 15 so as to correspond to the discharge port 13a (discharge chamber 13d). That is, the throttle portion 15g is formed at the center in the vertical direction of the rear side plate 15, and the throttle portion 15g is not formed below the rear side plate 15. Then, the refrigerant gas in the discharge space Da flows through the discharge passage 15e opened in the discharge chamber 13d and is supplied to the discharge region 30, so that the refrigerant gas is decompressed by being throttled by the throttle portion 15g in the discharge passage 15e. Accordingly, the discharge region 30 where the decompressed refrigerant gas is discharged is a low-pressure portion having a lower pressure than the discharge space Da, and is located downstream of the discharge space Da in the refrigerant gas flow direction. An oil supply passage 15d is formed in the bulging portion 15c. The oil supply passage 15 d is formed so as to extend linearly from the lower end surface of the bulging portion 15 c toward the rotating shaft 17 and to extend toward the back pressure groove 15 h of the rear side plate 15.

  In the vane compressor 10, an oil separator 40 for separating lubricating oil contained in the refrigerant gas is provided in the discharge region 30. The oil separator 40 has a low pressure that is the same as that of the discharge region 30. Has become a department. An oil storage chamber 31 is defined outside the oil separator 40 in the discharge region 30.

  As shown in FIG. 3, the oil separator 40 includes a plate-shaped joining plate portion 41, and a bolt insertion portion 41 b is formed in the joining plate portion 41. The oil separator 40 is fixed to the bulging portion 15c by screwing the mounting bolt V inserted through the bolt insertion portion 41b into the bulging portion 15c, and is joined to the rear side plate 15. The oil separator 40 is fixed to the bulging portion 15 c so as to cover both the discharge passages 15 e by the joining plate portion 41.

  Further, the oil separator 40 includes a cylindrical case 42 that is integrally formed with the joint plate portion 41 and extends in the vertical direction, an oil separation chamber 43 that extends in the vertical direction in a bottomed cylindrical shape formed in the case 42, and a case And an oil separation cylinder 44 which is fitted and fixed to the upper part of the oil separation chamber 43 in 42 and extends in a cylindrical shape in the vertical direction. The joining plate portion 41 is formed with a pair of communication passages 41 a so as to communicate with the upper end (the other end) of each discharge passage 15 e, and the communication passage 41 a is formed so as to face the outer peripheral surface of the oil separation cylinder 44. ing.

  Further, in the joining plate portion 41, shielding plates 42d as a collision portion are integrally formed at positions on both sides of the case 42. The shielding plate 42d is provided so as to project from the joining plate portion 41 in a plate shape, and is inclined so as to be inclined downward as it is separated from the case 42. The shielding plate 42 d covers the oil surface of the lubricating oil stored in the oil storage chamber 31. In the oil separator 40, a gas discharge port 42 a is formed in the upper portion of the case 42, and the refrigerant gas that has passed through the oil separation cylinder 44 passes from the gas discharge port 42 a to the outside of the vane compressor 10 (for example, It is discharged to an external refrigerant circuit).

  An oil discharge hole 42 b for discharging the lubricating oil stored in the oil separation chamber 43 to the outside of the oil separation chamber 43 is formed in the lower portion of the case 42. The oil discharge hole 42 b is formed so that one end opens toward the lowermost part of the oil separation chamber 43 and the lower end edge is located on the same plane as the bottom surface of the oil separation chamber 43. The oil discharge hole 42b is formed so that the other end opens toward the outside of the case 42. The oil discharge hole 42b is formed such that the axis L1 of the oil discharge hole 42b extends in the horizontal direction.

  Further, in the case 42, a wire net 46 as a mesh member is disposed in the lower part of the oil separation chamber 43. The metal mesh 46 is formed in a cylindrical shape, covers the entire inner peripheral surface of the case 42 in the lower part of the oil separation chamber 43, and opens on one end side (oil separation chamber 43 side) of the oil discharge hole 42b. Covering. Further, the wire mesh 46 is non-rotatably attached in the oil separation chamber 43 by a stopper (not shown).

  In the oil separator 40, a cylindrical passage forming portion 45 is joined to one side surface of the case 42. The passage forming portion 45 is joined to the side surface of the case 42 so as to extend upward from the lower end of the case 42 along the vertical direction. The passage forming portion 45 is joined to the case 42 so that its upper end (tip) is located on the same plane as the lower end of the oil separation cylinder 44.

  An oil discharge passage 50 communicating with the oil discharge hole 42b is formed in the passage forming portion 45. The oil discharge passage 50 is bent in an L shape in the passage forming portion 45. The oil discharge passage 50 opens at the side surface of the passage forming portion 45 so that the lower end (one end) communicates with the other end of the oil discharge hole 42 b, and the upper end (the other end) extends from the upper end of the passage forming portion 45 to the oil. It opens toward the storage chamber 31. The oil discharge passage 50 is formed by a first passage portion 51 that communicates with the other end of the oil discharge hole 42 b and a second passage portion 52 that extends perpendicular to the first passage portion 51.

  The first passage 51 is formed such that the axis L2 is located on the same axis as the axis L1 of the oil discharge hole 42b and extends in the horizontal direction. Further, the passage sectional area of the first passage portion 51 is the same as the passage sectional area of the oil discharge hole 42b. The second passage portion 52 is formed so that the axis L3 is orthogonal to the axis L2 of the first passage portion 51 and the axis L1 of the oil discharge hole 42b. Therefore, the second passage portion 52 is formed to extend upward from the first passage portion 51 along the vertical direction.

  A discharge port 53 for discharging the lubricating oil in the oil separation chamber 43 to the oil storage chamber 31 is formed at the tip (upper end) of the second passage portion 52, that is, at the upper end of the oil discharge passage 50. The oil discharge passage 50 includes a second passage portion 52 that extends upward along the vertical direction so that the discharge port 53 is located above the other end of the oil discharge hole 42b.

  In the oil discharge passage 50, the discharge port 53 side of the second passage portion 52 is a throttle 50 b that decreases in diameter toward the tip along the axis L <b> 3 of the second passage portion 52. The oil discharge passage 50 is formed so that the above-described shielding plate 42 d is positioned in the vicinity of the discharge port 53. That is, the oil discharge passage 50 (passage forming portion 45) is formed so as to be positioned near the shielding plate 42d so that the refrigerant gas (lubricating oil) discharged from the discharge port 53 can collide with it. Yes.

Next, the operation | movement is demonstrated about the vane compressor 10 of the said structure.
When the rotating shaft 17 is rotated, the rotor 18 and the vane 20 are rotated, and the refrigerant gas is sucked from the suction space Sa into the compression chambers 21 during the suction stroke through the pair of suction ports 14b and the suction passage 13b. Is done. The refrigerant gas sucked into each compression chamber 21 is compressed by the volume reduction of the compression chamber 21 during the compression stroke. The compressed refrigerant gas is discharged from each compression chamber 21 to each discharge chamber 13d (discharge space Da) through the discharge port 13a.

  The refrigerant gas discharged into the discharge chamber 13d (discharge space Da) is throttled by the throttle portion 15g and then flows into the groove portion 15f. The refrigerant gas flows into the communication passage 41a from the groove 15f, and is supplied to the oil separator 40 from the communication passage 41a. Then, the refrigerant gas is blown to the outer peripheral surface of the oil separation cylinder 44 and guided to the lower side of the oil separation chamber 43 while turning around the outer peripheral surface of the oil separation cylinder 44 and the inner peripheral surface of the case 42. At this time, the lubricating oil is separated from the refrigerant gas by centrifugal separation, and the lubricating oil is dropped toward the lower portion of the oil separation chamber 43. Part of the refrigerant gas separated from the lubricating oil flows upward in the oil separation cylinder 44 and is discharged from the gas discharge port 42a to the outside of the vane compressor 10 (for example, an external refrigerant circuit).

  In addition, since the refrigerant gas flowing toward the lower portion of the oil separation chamber 43 swirls along the inner peripheral surface of the case 42 and swirls along the wire mesh 46, the lubricating oil adheres to the wire mesh 46, and from the refrigerant gas. The lubricating oil is separated, and the separated lubricating oil is dropped toward the lower portion of the oil separation chamber 43. Further, when the refrigerant gas collides with the wire net 46, the flow velocity of the refrigerant gas that swirls decreases.

  In the oil separator 40, the oil discharge passage 50 communicating with the oil discharge hole 42b extends in the horizontal direction from the oil discharge hole 42b, and then extends upward in the vertical direction. It opens above the other end of the discharge hole 42b. For this reason, lubricating oil accumulates in the lower part of the oil separation chamber 43 and in the oil discharge hole 42b. In the state where the lubricating oil is stored in the lower part of the oil separation chamber 43 and in the oil discharge hole 42b, when the refrigerant gas flowing downward from the oil separation chamber 43 flows into the lubricating oil, the refrigerant gas in a bubble state is contained in the lubricating oil. Will be mixed.

  The lubricating oil stored in the lower portion of the oil separation chamber 43 passes through the mesh of the wire mesh 46 and is discharged from the oil discharge hole 42 b to the first passage portion 51. At this time, due to the squeezing action by the mesh of the metal mesh 46, the refrigerant gas existing in a large bubble state in the lubricant cannot pass through the mesh of the metal mesh 46 and is removed from the lubricant. The lubricating oil flows in the horizontal direction along the axis L2 of the first passage portion 51, then flows upward in the vertical direction along the axis L3 of the second passage portion 52, and is higher than the oil discharge hole 42b. To be guided to. Thereafter, the lubricating oil is discharged from the discharge port 53 of the oil discharge passage 50 to the oil storage chamber 31 and stored in the oil storage chamber 31. When the lubricating oil passes through the discharge port 53, the refrigerant gas existing in a large bubble state in the lubricating oil cannot pass through the throttle 50b, and the purity of the lubricating oil discharged from the discharge port 53 is increased.

  On the other hand, when the refrigerant gas is sprayed toward the lubricating oil in a state where the lubricating oil is stored in the lower part of the oil separation chamber 43, the refrigerant gas flows into the oil discharge passage 50 after flowing in the oil discharge hole 42b in the horizontal direction. To do. Then, the refrigerant gas flows in the horizontal direction by the first passage portion 51 of the oil discharge passage 50, and further flows upward in the vertical direction by the second passage portion 52, so that the flow velocity gradually decreases. For this reason, the refrigerant gas having a lower flow velocity than that when flowing in the oil separation chamber 43 is discharged into the oil storage chamber 31. Further, since the discharge port 53 is opened upward, the refrigerant gas discharged from the discharge port 53 is not directly blown onto the oil surface of the lubricating oil stored in the oil storage chamber 31. Further, since the shielding plate 42d is provided in the vicinity of the discharge direction of the refrigerant gas from the discharge port 53, the refrigerant gas discharged from the discharge port 53 collides with the shield plate 42d. Then, the lubricating oil contained in the refrigerant gas is separated from the refrigerant gas and dropped into the oil storage chamber 31.

The lubricating oil stored in the oil storage chamber 31 is guided from the oil supply passage 15d to the vane groove 18a and the sliding portions in the vane compressor 10, and each sliding portion is lubricated by the lubricating oil.
In the present invention (this embodiment), “upper part”, “upper part”, and “lowermost part” mean an upper part, an upper part, and a lowermost part when the compressor (vane compressor 10) is mounted on a vehicle. ing.

According to the above embodiment, the following effects can be obtained.
(1) In the vane compressor 10 provided with the oil discharge hole 42b of the lubricating oil in the oil separation chamber 43, an oil discharge passage 50 communicating with the other end of the oil discharge hole 42b is provided, and the oil discharge passage 50 is discharged with oil. It formed from the 1st channel | path part 51 extended in the horizontal direction from the hole 42b, and the 2nd channel | path part 52 extended toward upper direction from the 1st channel | path part 51 along a perpendicular direction. For this reason, for example, the oil discharge passage 50 does not communicate with the oil discharge hole 42b, and after the refrigerant gas flows through the oil discharge hole 42b, it does not flow upward along the vertical direction to the oil storage chamber 31. Compared with the case where the oil is discharged, the distance through which the refrigerant gas flows before the oil discharge passage 50 is discharged from the oil separation chamber 43 to the oil storage chamber 31 can be increased. Therefore, the flow rate of the refrigerant gas discharged to the oil storage chamber 31 can be reduced as compared with when flowing in the oil separation chamber 43. Therefore, even if the refrigerant gas is discharged to the oil storage chamber 31 through the oil discharge hole 42b, the lubricant gas is prevented from being rolled up by the refrigerant gas, and the lubricating oil is suppressed in the oil storage chamber 31. The oil level can be prevented from lowering. Therefore, the oil level of the lubricating oil can be maintained high around the oil supply passage 15d in the oil storage chamber 31, and the refrigerant gas enters the oil supply passage 15d by sealing the oil supply passage 15d with the lubricating oil. Can be prevented. As a result, the refrigerant gas can be prevented from being supplied from the oil supply passage 15d to the vane groove 18a via the back pressure grooves 14h and 15h, and the refrigerant gas is supplied to the compression chamber 21 and the suction space Sa. Can be prevented.

  (2) Since the oil discharge passage 50 is provided in the oil separator 40 as described above, the flow rate of the refrigerant gas can be reduced, so that it is not necessary to reduce the flow rate of the refrigerant gas in the oil separation chamber 43. Therefore, it is not necessary to increase the volume of the case 42 of the oil separator 40 in order to reduce the flow rate of the refrigerant gas in the oil separation chamber 43, and without increasing the size of the oil separator 40, that is, the vane compressor 10. It is possible to prevent the lubricating oil from being rolled up in the oil storage chamber 31 without increasing the size of the physique.

  (3) The oil discharge passage 50 is formed such that the second passage portion 52 which is a part thereof extends upward from the first passage portion 51 along the vertical direction, and the discharge port 53 is formed of the oil discharge hole 42b. It is located above the other end. Therefore, in a state where the oil discharge passage 50 communicates with the oil discharge hole 42b, the lubricating oil can be stored in the oil separation chamber 43 and the oil discharge hole 42b, and the lubricating oil in the oil separation chamber 43 is instantly stored in the oil storage chamber. It is not discharged to 31. Therefore, the oil discharge hole 42 b can be sealed with the lubricating oil, and the refrigerant gas in the oil separation chamber 43 can be prevented from being directly sprayed onto the lubricating oil in the oil storage chamber 31. As a result, it is possible to prevent the lubricating oil from being rolled up in the oil storage chamber 31.

  (4) The discharge port 53 of the oil discharge passage 50 is located on the same plane as the lower end of the oil separation cylinder 44 in the oil separator 40. Since the refrigerant gas swirls above the lower end of the oil separation cylinder 44, the lubricating oil in the oil separation chamber 43 is pushed downward from the oil separation cylinder 44 by this refrigerant gas, and the lubricating oil is contained in the oil separation chamber 43. Can be stored up to the lower end of the oil separation cylinder 44. Therefore, by positioning the discharge port 53 on the same plane as the lower end of the oil separation cylinder 44, the lubricating oil can be stored in the oil separation chamber 43 to the maximum extent.

  (5) The passage forming portion 45 is joined to the case 42 so that the shielding plate 42 d is positioned in the vicinity of the discharge port 53. The shielding plate 42d is positioned in the direction in which the refrigerant gas is discharged from the discharge port 53. Therefore, the refrigerant gas discharged from the discharge port 53 can collide with the shielding plate 42d, and the lubricating oil can be separated from the refrigerant gas using this collision, so that the separation efficiency of the lubricating oil can be improved.

  (6) A throttle 50b is provided on the oil discharge passage 50 on the discharge port 53 side. Therefore, when the lubricating oil is discharged from the discharge port 53, the refrigerant gas contained in the lubricating oil in a bubble state is removed by the throttle 50b, and the high purity (low refrigerant gas content) is lubricated from the discharge port 53. Oil can be drained.

  (7) In the lower part of the oil separation chamber 43, a wire mesh 46 is provided to cover the oil discharge hole 42b. For this reason, the flow rate of the refrigerant gas swirling in the oil separation chamber 43 can be reduced by the wire mesh 46. As a result, it is possible to contribute to a decrease in the flow rate of the refrigerant gas discharged from the oil discharge passage 50 through the oil discharge hole 42b.

  (8) In the lower part of the oil separation chamber 43, a wire mesh 46 is provided to cover the oil discharge hole 42b. For this reason, when the lubricating oil in the oil separation chamber 43 passes through the mesh of the metal mesh 46, the refrigerant gas contained in the lubricating oil in a bubble state can be removed by the mesh of the metal mesh 46. As a result, lubricating oil with high purity (low refrigerant gas content) can be discharged from the discharge port 53.

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

  As shown in FIG. 4, an oil discharge hole 42 b is formed in the case 42 of the oil separator 40. An oil discharge passage 60 communicating with the other end of the oil discharge hole 42b is formed by the rear end surface of the bulging portion 15c and the joining plate portion 41 joined to the bulging portion 15c. The oil discharge passage 60 is sealed by a metal seal between the bulging portion 15 c and the joining plate portion 41.

  The oil discharge passage 60 is formed such that an axis L4 on one end side thereof extends upward along the vertical direction, and further extends obliquely toward the side portion of the joining plate portion 41 in the oil separator 40. Is formed. A discharge port 60 a provided at the other end of the oil discharge passage 60 opens from the edge of the mating surface between the bulging portion 15 c and the joining plate portion 41 toward the oil storage chamber 31. Further, a throttle 60 b is formed on the other end side of the oil discharge passage 60. The other end of the oil discharge passage 60 is opened in the vicinity of the through bolt B so that the through bolt B is positioned in the direction of discharging the lubricating oil from the discharge port 60a.

Therefore, according to 2nd Embodiment, in addition to the effect similar to (1)-(4) and (6)-(8) as described in 1st Embodiment, the following effects can be acquired. .
(9) The oil discharge passage 60 is formed in a groove shape on the rear end surface of the bulging portion 15 c and is formed by joining the bulging portion 15 c and the joining plate portion 41. Therefore, the oil discharge passage 60 can be formed in the bulging portion 15c by casting when the rear side plate 15 is cast. For this reason, the manufacturing cost of the oil discharge passage 60 and, in turn, the manufacturing cost of the vane compressor 10 can be kept low.

  (10) The oil discharge passage 60 is recessed in the rear end face of the bulging portion 15c so that the through bolt B is positioned in the vicinity of the discharge direction of the refrigerant gas from the discharge port 60a. Therefore, the refrigerant gas discharged from the discharge port 60a can be caused to collide with the bolt B and the lubricating oil can be separated from the refrigerant gas by using this collision, and the separation efficiency of the lubricating oil can be increased.

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

  As shown in FIG. 5, the oil separator 40 is joined to the rear end surface of the bulging portion 15c via a gasket G. An oil discharge hole 42 b is formed in the case 42 of the oil separator 40. An oil discharge passage 70 communicating with the other end of the oil discharge hole 42b is formed between the rear end surface of the bulging portion 15c and the gasket G facing the bulging portion 15c. That is, the oil discharge passage 70 is formed by joining the oil separator 40 to the bulging portion 15c via the gasket G. The oil discharge passage 70 is formed by digging (depressing) a surface of the gasket G facing the bulging portion 15c into a groove shape.

  The oil discharge passage 70 is formed such that an axis L5 on one end side thereof extends upward along the vertical direction, and further extends obliquely toward the side portion of the joining plate portion 41 in the oil separator 40. Is formed. A discharge port 70 a provided at the other end of the oil discharge passage 70 opens from the mating surface of the rear end surface of the bulging portion 15 c and the surface of the gasket G facing the bulging portion 15 c toward the oil storage chamber 31. ing. Further, a throttle 70 b is formed on the other end side of the oil discharge passage 70. The other end of the oil discharge passage 70 is opened in the vicinity of the through bolt B so that the through bolt B is positioned in the direction of discharging the refrigerant gas from the discharge port 70a.

Therefore, according to the third embodiment, the following effects can be obtained in addition to the same effects as (1) to (4) and (6) to (8) described in the first embodiment. .
(11) The oil discharge passage 70 is recessed in the gasket G so that the through bolt B is positioned in the vicinity of the discharge direction of the refrigerant gas from the discharge port 70a. Therefore, the refrigerant gas discharged from the discharge port 70a can be caused to collide with the bolt B, and the lubricating oil can be separated from the refrigerant gas by using this collision, and the separation efficiency of the lubricating oil can be improved.

  (12) Since the gasket G is interposed between the rear end surface of the bulging portion 15 c of the rear side plate 15 and the oil separator 40, the leakage of the refrigerant gas and the lubricating oil from the oil discharge passage 70 is prevented by the gasket G. Can do. Further, since the oil discharge passage 70 can be formed only by digging a groove in the gasket G, the manufacturing cost of the oil discharge passage 70 can be kept low.

In addition, you may change the said embodiment as follows.
In each embodiment, the wire mesh 46 may not be provided. Alternatively, in each embodiment, the mesh member provided in the oil separation chamber 43 may be made of resin.

In each embodiment, the throttles 50b, 60b, 70b of the oil discharge passages 50, 60, 70 need not be formed.
In each embodiment, the shielding plate 42d and the through bolt B may not be provided in the direction in which the refrigerant gas is discharged from the discharge ports 53, 60a, and 70a.

In the second and third embodiments, the oil discharge passages 60 and 70 may be formed so that the mounting bolt V is positioned in the vicinity of the discharge ports 60a and 70a.
In each embodiment, the discharge ports 53, 60 a and 70 a may be located below the lower end of the oil separation cylinder 44.

  In the first embodiment, the oil discharge passage 50 has one end communicating with the other end of the oil discharge hole 42b and extending in the horizontal direction, and the other discharge port 53 is the upper edge of the other end of the oil discharge hole 42b. And may be formed so as to open upward on the same plane.

  The present invention may be embodied in a scroll compressor as a compressor. In this case, the compression mechanism C is a scroll type and the partition member is formed by a fixed scroll end plate.

The longitudinal cross-sectional view which shows the vane compressor of 1st Embodiment. The 2-2 sectional view taken on the line of FIG. 1 which shows the inside of the vane compressor of 1st Embodiment. Fig. 3 is a cross-sectional view taken along line 3-3 in Fig. 1 showing an oil separator and an oil discharge passage. Sectional drawing which shows the oil discharge passage of 2nd Embodiment. Sectional drawing which shows the oil discharge passage of 3rd Embodiment.

Explanation of symbols

  B ... Through bolt as collision part, C ... Compression mechanism, G ... Gasket, H ... Housing, 10 ... Vane compressor as compressor, 15 ... Rear side plate as partition member, 30 ... Discharge area, 31 ... Oil storage Chamber, 40 ... oil separator, 42 ... case, 42b ... oil discharge hole, 42d ... shielding plate as collision part, 43 ... oil separation chamber, 44 ... oil separation cylinder, 46 ... wire mesh as mesh member, 50, 60 , 70 ... Oil discharge passage, 50b, 60b, 70b ... throttle, 53, 60a, 70a ... discharge port.

Claims (9)

A partition member provided in the housing partitions the inside of the housing into a compression mechanism side and a discharge region side from which refrigerant gas compressed by the compression mechanism is discharged. An oil separator that separates lubricating oil contained in the discharged refrigerant gas is accommodated in a state of being joined to the partition member, and the oil separator discharges the refrigerant gas after oil separation from the compressor. The oil separator communicates with the outside of the compressor, and the oil separator has an oil separation chamber formed in a cylindrical case, and an oil separation cylinder extending in the vertical direction is accommodated in the upper portion of the oil separation chamber, An oil storage chamber communicating with the sliding portion in the housing is defined outside the oil separator in the discharge region via an oil supply passage , and one end of the oil separator is connected to the oil separator. Open to the bottom and A compressor oil discharge hole having one end opening toward the outside of the case is formed,
An oil discharge passage connecting the oil discharge hole and the oil storage chamber is provided. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage is connected to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole and at least a part thereof extends upward along the vertical direction. The refrigerant gas flowing through the oil discharge passage is further separated from the lubricating oil after being discharged from the discharge port, and merged with the flow of the refrigerant gas from the oil separator to the outside of the compressor. compressor to be.   The compressor according to claim 1, wherein the discharge port is located on the same plane as a lower end of the oil separation cylinder.   The oil discharge passage is formed in a groove shape on the end surface of the partition member and is formed by joining the partition member and the oil separator, and the discharge port is formed by connecting the partition member and the oil. The compressor according to claim 1 or 2, wherein the compressor opens from the edge of the mating surface with the separator toward the oil storage chamber.   The oil separator is joined to the partition member via a gasket, the oil discharge passage is recessed in a surface of the gasket facing the partition member, and the partition member and the oil separator are connected to the gasket. Further, the discharge port is opened from the edge of the mating surface of the partition member and the gasket toward the oil storage chamber. The compressor described.   The compressor according to any one of claims 1 to 4, wherein a collision unit that causes the refrigerant gas to collide is disposed in a direction in which the refrigerant gas is discharged from the discharge port.   The compressor according to any one of claims 1 to 5, wherein a throttle is provided on the discharge port side in the oil discharge passage.   A mesh member is provided below the oil separation cylinder in the oil separation chamber and extends over the entire circumference of the inner peripheral surface of the case forming the oil separation chamber and covers the oil discharge hole. The compressor according to any one of claims 1 to 6.   A partition member provided in the housing partitions the inside of the housing into a compression mechanism side and a discharge region side from which refrigerant gas compressed by the compression mechanism is discharged. An oil separator that separates lubricating oil contained in the discharged refrigerant gas is accommodated in a state of being joined to the partition member, and the oil separator has an oil separation chamber formed in a cylindrical case and the oil separator. An oil separation cylinder extending in the vertical direction is accommodated in an upper portion of the separation chamber, an oil storage chamber is defined outside the oil separator in the discharge region, and one end of the oil separator is disposed on the oil separator. A compressor formed with an oil discharge hole that opens toward the bottom of the separation chamber and the other end of which opens toward the outside of the case;
  An oil discharge passage connecting the oil discharge hole and the oil storage chamber is provided. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage is connected to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole and at least a part thereof extends upward along the vertical direction;
  The oil discharge passage is formed in a groove shape on the end surface of the partition member and is formed by joining the partition member and the oil separator, and the discharge port is formed by connecting the partition member and the oil. A compressor that opens from an edge of a mating surface with a separator toward the oil storage chamber.   A partition member provided in the housing partitions the inside of the housing into a compression mechanism side and a discharge region side from which refrigerant gas compressed by the compression mechanism is discharged. An oil separator that separates lubricating oil contained in the discharged refrigerant gas is accommodated in a state of being joined to the partition member, and the oil separator has an oil separation chamber formed in a cylindrical case and the oil separator. An oil separation cylinder extending in the vertical direction is accommodated in an upper portion of the separation chamber, an oil storage chamber is defined outside the oil separator in the discharge region, and one end of the oil separator is disposed on the oil separator. A compressor formed with an oil discharge hole that opens toward the bottom of the separation chamber and the other end of which opens toward the outside of the case;
  An oil discharge passage connecting the oil discharge hole and the oil storage chamber is provided. One end of the oil discharge passage communicates with the other end of the oil discharge hole, and the other end of the oil discharge passage is connected to the oil storage chamber. The oil discharge passage is formed such that the discharge port is located above the other end of the oil discharge hole and at least a part thereof extends upward along the vertical direction;
  The oil separator is joined to the partition member via a gasket, the oil discharge passage is recessed in a surface of the gasket facing the partition member, and the partition member and the oil separator are connected to the gasket. In addition, the compressor is formed by joining through, and the discharge port is opened from an edge of a mating surface of the partition member and the gasket toward the oil storage chamber.

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