Blowby gas plate and reciprocation compressor

Abstract

To provide a blowby gas plate which can reduce a rise of oil caused by a return of a blowby gas to a suction chamber by a simple structure.SOLUTION: A blowby gas plate according to at least one embodiment of the present disclosure faces a recess as a part of an equal pressure flow passage formed at a casing of a reciprocation compressor so as to form the equal pressure flow passage which returns a blowby gas of the reciprocation compressor to a suction side, and can be attached to the casing. The blowby gas plate according to at least one embodiment of the present disclosure comprises one or more opening parts which are formed at a position facing the recess, and a mesh part arranged at the opening part and allowing the permeation of the blowby gas.SELECTED DRAWING: Figure 3

Description

[Technical field]

[0001] The present disclosure relates to a blow-by gas plate provided in a reciprocating compressor, and to a reciprocating compressor including the blow-by gas plate. [Background technology]

[0002] A reciprocating compressor converts the rotational motion of the crankshaft (drive shaft) into the reciprocating motion of a piston in a crank chamber, compressing the refrigerant gas circulating in the refrigeration cycle. The inside of the reciprocating compressor is divided into a suction chamber, a discharge chamber, a cylinder, and a crank chamber, and the lower part of the crank chamber is an oil reservoir that stores lubricating oil. The lubricating oil stored in the oil reservoir is supplied to each sliding part of the reciprocating compressor by a forced oil supply system using an oil pump.

[0003] The refrigerant gas circulating in the refrigeration cycle is drawn from the suction chamber into the cylinder through the suction valve by the reciprocating motion of the piston, compressed, and discharged into the discharge chamber through the discharge valve.

[0004] Conventionally, in order to prevent the pressure in the crank chamber from increasing due to refrigerant gas (blow-by gas) leaking into the crank chamber through the gap between the inner wall surface of the cylinder and the piston ring, a pressure equalizing passage (balance hole) has been provided connecting the crank chamber and the suction chamber to return the blow-by gas to the suction chamber.

[0005] When the blow-by gas that flows into the suction chamber through the pressure equalizing passage returns to the suction chamber, it carries with it oil droplets in the crank chamber, which may result in an oil rise that reduces the amount of oil in the oil storage chamber that stores the lubricating oil.

[0006] As a mechanism for preventing such oil leaking, for example, Patent Document 1 listed below discloses a reciprocating compressor that includes a partition member arranged between an opening end on the crank chamber side of a pressure equalizing passage that communicates between the crank chamber and the suction chamber, and a crankshaft to which a piston is connected, and further includes an oil separator arranged between the partition member and the opening end of the pressure equalizing passage.

[0007] In the reciprocating compressor thus constructed, the partition member prevents oil droplets in the crank chamber from flowing directly into the open end of the pressure equalizing passage, and the oil separator further reduces the amount of lubricating oil flowing into the open end of the pressure equalizing passage, thereby preventing oil rise, which is a reduction in the amount of oil in the oil chamber. [Prior art documents] [Patent documents]

[0008] [Patent Document 1] International Publication No. 2014 / 054092 Summary of the Invention [Problem to be solved by the invention]

[0009] However, compared to the configuration of Patent Document 1, there is a demand for preventing oil rise caused by returning blow-by gas to the suction chamber without installing a partition member in the crank chamber or installing an oil separator that protrudes into the crank chamber.

[0010] In view of the above circumstances, at least one embodiment of the present disclosure aims to provide a blow-by gas plate and a reciprocating compressor that can reduce oil rise caused by returning blow-by gas to the suction chamber with a simple structure. [Means for solving the problem]

[0011] (1) At least one embodiment of the blow-by gas plate according to the present disclosure includes: A blow-by gas plate that can be attached to a casing of a reciprocating compressor so as to face a recess that is a part of the pressure equalizing flow passage provided in the casing, so as to form a pressure equalizing flow passage for returning blow-by gas of the reciprocating compressor to an intake side, One or more openings provided at a position opposite the recess; a mesh portion provided in the opening portion and allowing the blow-by gas to pass through; Equipped with.

[0012] (2) A reciprocating compressor according to at least one embodiment of the present disclosure, A blow-by gas plate having the configuration of (1) above; a housing in which a suction chamber, a discharge chamber, a cylinder, and a crank chamber are provided, the lower part of the crank chamber being configured as an oil reservoir for storing lubricating oil; A piston reciprocally disposed within the cylinder; a crankshaft rotatably disposed in the crank chamber and connected to the piston via a connecting rod; a bearing housing in which a bearing portion that supports the crankshaft is disposed; Equipped with The recess is formed in the bearing housing. Effect of the Invention

[0013] According to at least one embodiment of the present disclosure, it is possible to reduce oil rise caused by returning blow-by gas to the suction chamber with a simple structure. [Brief description of the drawings]

[0014] [Figure 1] 1 is a diagram showing a schematic vertical cross section of a reciprocating compressor according to an embodiment of the present invention together with a refrigeration cycle. [Diagram 2] FIG. 1 is a schematic cross-sectional view of a reciprocating compressor according to an embodiment of the present invention. [Diagram 3] FIG. 1 is a perspective cross-sectional view showing a reciprocating compressor according to an embodiment of the present invention. [Figure 4] 4 is a view of the bearing housing and the partition plate as viewed from the inside to the outside of the crank chamber. FIG. [Diagram 5] FIG. 2 is a view of the bearing housing as viewed from the inside to the outside of the crankcase. [Figure 6] 6 is a schematic cross-sectional view taken along line VI-VI of FIG. 5. FIG. DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENTS

[0015] Hereinafter, some embodiments of the present disclosure will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, etc. of components described as the embodiments or shown in the drawings are merely illustrative examples and are not intended to limit the scope of the present disclosure. For example, expressions expressing relative or absolute configuration, such as "in a certain direction," "along a certain direction," "parallel," "orthogonal," "center," "concentric," or "coaxial," not only strictly express such a configuration, but also express a state in which there is a relative displacement with a tolerance or an angle or distance to the extent that the same function is obtained. For example, expressions indicating that things are in an equal state, such as "identical," "equal," and "homogeneous," not only indicate a state of strict equality, but also indicate a state in which there is a tolerance or a difference to the extent that the same function is obtained. For example, expressions describing shapes such as a rectangular shape or a cylindrical shape do not only refer to rectangular shapes, cylindrical shapes, etc. in the strict geometric sense, but also refer to shapes that include uneven portions, chamfered portions, etc., to the extent that the same effect is obtained. On the other hand, the expressions "comprise," "include," "have," "includes," or "have" of one element are not exclusive expressions excluding the presence of other elements.

[0016] An embodiment of the present invention will be described with reference to Fig. 1 to Fig. 6. In the description of the drawings, the same elements are given the same reference numerals, and duplicated description will be omitted. The dimensional ratios in the drawings are exaggerated for the convenience of explanation, and may differ from the actual ratios.

[0017] FIG. 1 is a schematic longitudinal section of a reciprocating compressor 1 according to the present embodiment, together with a refrigeration cycle. FIG. 2 is a schematic transverse section of the reciprocating compressor 1 according to the present embodiment. FIG. 3 is a perspective cross-sectional view of the reciprocating compressor 1 according to the present embodiment. FIG. 4 is a view of the bearing housing 60 and the partition plate 70 as viewed from the inside to the outside of the crank chamber 34. FIG. 5 is a view of the bearing housing 60 as viewed from the inside to the outside of the crank chamber 34. FIG. 6 is a schematic cross-sectional view taken along the line VI-VI in FIG. 5. In FIG. 5, the opening 71 of the partition plate 70 is indicated by a two-dot chain line for ease of understanding.

[0018] First, the configuration of the refrigeration cycle will be described with reference to FIG.

[0019] The refrigeration cycle has a circular refrigerant circuit 10 through which the refrigerant circulates, and a reciprocating compressor 1, a condenser (high-pressure heat exchanger) 12, an expansion valve (expander) 14, and an evaporator (low-pressure heat exchanger) 16 are connected and arranged in this order in the refrigerant circulation direction in the refrigerant circuit 10. In this embodiment, an oil separator 18 and a receiver 20 are further arranged in the refrigerant circuit 10.

[0020] In the refrigeration cycle, the reciprocating compressor 1 is configured to suck in and compress a refrigerant at a pressure (suction pressure) of, for example, 0.1 MPa to 0.3 MPa, and discharge a refrigerant at a pressure (discharge pressure) of 1.5 MPa to 2 MPa, but the ranges of the suction pressure and discharge pressure of the refrigerant are not limited to these. The refrigerant is, for example, various alternative fluorocarbon refrigerants such as R32, or ammonia, carbon dioxide, etc.

[0021] Next, the configuration of a reciprocating compressor 1 according to this embodiment will be described with reference to Figs.

[0022] The reciprocating compressor 1 generally includes a housing 22, a piston 36 arranged in a cylinder 32 so as to be capable of reciprocating motion, a crankshaft 40 arranged in a crank chamber 34 so as to be rotatable, a bearing portion 50A on the oil pump 90 side for supporting the crankshaft 40, a bearing portion 50B on one end side (the right side in FIG. 1) of the crankshaft 40, a bearing housing 60 in which the bearing portion 50A on the oil pump 90 side is arranged, a partition plate 70 provided between the bearing housing 60 and the crank chamber 34 and forming a closed space V together with the bearing housing 60, and a pressure equalizing passage 80 communicating the closed space V and the suction chamber 28. Each component will be described below. For ease of description, the circumferential direction about the rotation axis AX of the crankshaft 40 is defined as the circumferential direction C, the extension direction of the rotation axis AX is defined as the axial direction X, and the radial direction about the rotation axis AX is defined as the radial direction R. The vertical direction is assumed to coincide with the up-down direction of the paper in each drawing.

[0023] 1, the housing 22 is provided with an intake port 24 and a discharge port 26. The intake port 24 is connected to the outlet of the evaporator 16 via a pipe, and the discharge port 26 is connected to the inlet of the oil separator 18 via a pipe.

[0024] 1 to 3, a suction chamber 28, a discharge chamber 30, a cylinder 32, a crank chamber 34, and an oil storage chamber 35 are provided inside the housing 22. A piston 36 is arranged in the cylinder 32 so as to be able to reciprocate, and a compression chamber W is defined inside the cylinder 32 by the piston 36. The suction chamber 28 communicates with the suction port 24, and can communicate with the compression chamber W via a suction valve. The discharge chamber 30 communicates with the discharge port 26, and can communicate with the compression chamber W via a discharge valve.

[0025] The lower end of the cylinder 32 communicates with a crank chamber 34, and a connecting rod 38 connected to a piston 36 extends into the crank chamber 34. A crankshaft 40 is rotatably disposed within the crank chamber 34, and the connecting rod 38 is connected to the crankshaft 40.

[0026] 1, the oil reservoir 35 is formed at the bottom of the crank chamber 34. The oil stored in the oil reservoir 35 is supplied as lubricating oil to each sliding part during operation of the reciprocating compressor 1. In this embodiment, oil filters 46, 48 for purifying the lubricating oil are installed in the oil reservoir 35 and outside the housing 22, respectively.

[0027] One end side (the right side in FIG. 1) of the crankshaft 40 airtightly penetrates the housing 22 via a shaft seal 43, and a driving source (not shown) is connected to the outer end of the crankshaft 40. When the crankshaft 40 is rotated by the driving source, the piston 36 reciprocates within the cylinder 32, thereby repeatedly executing a suction stroke, a compression stroke, and a discharge stroke of the refrigerant.

[0028] As shown in Fig. 3, bearing portion 50A is configured to support crankshaft 40 on the side of oil pump 90 opposite to the drive source. As shown in Fig. 3, a groove 51 is formed on the inner periphery of bearing portion 50A so that lubricating oil from oil reservoir 35 comes into contact with the outer periphery of crankshaft 40. One end side of bearing portion 50A (the front side in Fig. 3) has a flange shape and is configured to abut against bearing housing 60.

[0029] 3, the bearing portion 50A is disposed in the bearing housing 60. The bearing housing 60 is fixed to the housing 22 by a fixing portion (not shown). The fixing portion is not particularly limited, but may be, for example, a bolt.

[0030] In the reciprocating compressor 1 according to this embodiment, the housing 22 and the bearing housing 60 are included in the casing 2 of the reciprocating compressor 1 which forms the crank chamber 34 and the oil storage chamber 35. That is, the housing 22 and the bearing housing 60 are members which constitute the casing 2 of the reciprocating compressor 1 according to this embodiment.

[0031] As shown in Fig. 3, the bearing housing 60 is formed with an oil passage 61 extending radially outward, through which the lubricating oil passes. Furthermore, a recess 62 recessed in the axial direction of the crankshaft 40 is formed on one end side of the bearing housing 60 (the front side in Fig. 3). The recess 62 forms a closed space V when a partition plate 70 is fixed to the bearing housing 60. The closed space V includes a first closed space V1 connected to the pressure equalizing path 80 and a second closed space V2 connected to the oil passage 61. The lubricating oil supplied from the oil reservoir 35 to the bearing housing 60 flows into the second closed space V2 via the oil passage 61.

[0032] The recess 62 extends in the circumferential direction C so as to surround the bearing part 50A in the circumferential direction C in a radially outer region of the bearing part 50A. The recess 62 includes a first recess 621 that forms the first closed space V1 and a second recess 622 that forms the second closed space V2. The first recess 621 and the second recess 622 are separated by walls 623 and 624. In other words, when the partition plate 70 is fixed to the bearing housing 60, the first closed space V1 is separated from the second closed space V2. The first recess 621 and the second recess 622 each have a partial ring shape when viewed axially from the inside to the outside of the crank chamber 34. The second recess 622 is provided below the first recess 621 .

[0033] The recess 62 is formed with a plurality of protrusions that extend in the radial direction R within the recess 62 and protrude along the axial direction X from the outside to the inside of the crank chamber 34, i.e., toward the partition plate 70 described later, as ribs 66 for reinforcing the strength of the bearing housing 60. The rib 66 protrudes from the bottom surface 62a of the recess 62 in the axial direction X to a height less than that of the wall portions 623, 624. Therefore, when a partition plate 70 (described later) is fixed to the bearing housing 60, the partition plate 70 comes into close contact with the apexes 623a, 624a of the wall portions 623, 624 facing the axial direction X, but is spaced apart in the axial direction from the apex 66a of the rib 66 facing the axial direction X.

[0034] 3, the partition plate 70 is provided between the bearing housing 60 and the crank chamber 34. The partition plate 70 is fixed to the bearing housing 60 so as to cover the recessed portion 62 of the bearing housing 60. The means for fixing the partition plate 70 to the bearing housing 60 is not particularly limited, and may be, for example, fastening with bolts. That is, the partition plate 70 is disposed inside the crank chamber 34 along the axial direction X with respect to the recessed portion 62.

[0035] 3 and 4, the partition plate 70 has an opening 71 that communicates between the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricant oil discharge hole 74 that communicates between the crank chamber 34 and the second closed space V2.

[0036] 3 and 4, a plurality of openings 71 are formed at intervals in the circumferential direction C so as to communicate with the first closed space V1 which communicates with the pressure equalizing path 80. Each opening 71 is provided at a position facing the recess 62 (first closed space V1).

[0037] As shown in Fig. 3, the lubricant oil drain hole 74 is formed so as to communicate with the second closed space V2 which communicates with the oil passage 61 of the bearing housing 60. As shown in Fig. 3, the lubricant oil drain hole 74 is formed by a flat cutout portion whose opening shape is wide horizontally.

[0038] A mesh portion 72 is provided in each opening 71. The mesh portion 72 is a net member provided so as to cover each opening 71. It is preferable that the openings of the mesh portion 72 are specified so that blow-by gas can pass through but oil droplets of lubricating oil cannot or have difficulty in passing through.

[0039] The partition plate 70 has a non-opening region 73 in which no openings 71 are provided between two openings 71 adjacent to each other in the circumferential direction C. In the reciprocating compressor 1 according to this embodiment, the partition plate 70 has a plurality of non-opening regions 73. At least one of the plurality of non-opening regions 73 is provided in a position facing the rib 66 when the partition plate 70 is attached to the bearing housing 60.

[0040] The pressure equalizing passage 80 is provided to suppress an increase in pressure in the crank chamber 34 due to blow-by gas leaking from a gap between the piston 36 and the wall surface of the cylinder 32 during operation of the reciprocating compressor 1. The pressure equalizing passage 80 has an opening end (inlet end) 81 that opens into the first closed space V1, and an opening end (outlet end) 82 that opens into the suction chamber 28 (see FIG. 3). That is, in the reciprocating compressor 1 according to this embodiment, the recess 62 forming the first closed space V1, the partition plate 70, and the pressure equalizing passage 80 form a pressure equalizing passage 100 for returning the blow-by gas of the reciprocating compressor 1 to the intake side (specifically, the suction chamber 28).

[0041] Next, the effects of the reciprocating compressor 1 according to this embodiment will be described.

[0042] For example, in the case of a reciprocating compressor that is not provided with the partition plate 70, during operation of the reciprocating compressor, droplets of the lubricating oil after lubricating the bearings, etc., are scattered from the crankshaft or the bearings, and the lubricating oil is entrained by the blow-by gas that flows into the suction chamber through the pressure equalizing passage, reducing the amount of oil in the oil storage chamber and causing oil rise.

[0043] In contrast, according to the reciprocating compressor 1 of this embodiment, the partition plate 70 is provided between the bearing housing 60 and the crank chamber 34, so that the lubricating oil that is to be entrained in the blow-by gas passing through the mesh portion 72 covering each opening 71 is difficult to pass through the mesh portion 72, and is returned to the oil storage chamber 35. Furthermore, even if a small amount of lubricating oil entrained in the blow-by gas passes through the mesh portion 72, the entrained oil droplets become large while passing through the first closed space V1, and are separated from the blow-by gas by gravity settling. The oil droplets separated from the blow-by gas are returned to the oil storage chamber 35 from the lower part of the first closed space V1 through the opening 71 and the mesh portion 72. Meanwhile, the blow-by gas from which the oil droplets have been separated moves from the first closed space V1 to the suction chamber 28 through the pressure equalizing path 80. As a result, the amount of lubricating oil flowing into the suction chamber 28 through the pressure equalizing path 80 is reduced, and oil rising in the reciprocating compressor 1 can be prevented.

[0044] In the reciprocating compressor 1 according to this embodiment, by providing the mesh portion 72 at the opening 71, the area of ​​the opening 71 can be made relatively large, the flow velocity of the blow-by gas entering the first recess 621 can be reduced, and the oil droplet entraining force of the blow-by gas can be reduced, so that the amount of oil droplets entering the first recess 621 can be reduced. Furthermore, according to the reciprocating compressor 1 according to this embodiment, the mesh portion 72 can prevent the oil droplets from entering the first recess 621, so that the amount of oil droplets entering the first recess 621 can be reduced. This can reduce oil rising.

[0045] In the reciprocating compressor 1 according to this embodiment, the first recess 621 forming the first closed space V1 is formed in an annular shape, and is provided such that an end 621a on one side and an end 621b on the other side in the circumferential direction C face downward (are positioned lower than other portions). The opening 71 is formed to include a position facing at least one of the end 621a on one side or the end 621b on the other side. In the example shown in FIG. 5, the opening 71 is formed to include a position facing the end 621a on one side and the end 621b on the other side. For example, as shown in Fig. 6, at least one of the ends 621a, 621b, a wall surface 621c facing the circumferential direction C that defines the first recess 621 is inclined downward from the bottom surface 62a of the first recess 621 toward the partition plate 70. Note that Fig. 6 shows the vicinity of one end 621a. This allows the lubricating oil that has flowed down the wall surface 621c and accumulated in the first recess 621 to easily return to the crank chamber 34 via the opening 71 and the mesh portion 72, thereby reducing oil rise.

[0046] In the reciprocating compressor 1 of this embodiment, the openings 71 are provided at intervals in the circumferential direction C at positions facing the annularly formed recess 62 when the partition plate 70 is attached to the casing 2 (bearing housing 60). By providing the openings 71 divided in the circumferential direction C, the length of each opening 71 in the circumferential direction C is shortened. This shortens the extension length of the mesh portion 72 in the circumferential direction C, improving the rigidity of the mesh portion 72. Therefore, even if an external force acts on the mesh portion 72 as the blow-by gas passes through the mesh portion 72 when it flows into the first recess 621, deformation of the mesh portion 72, etc. can be suppressed.

[0047] The first closed space V1 in the bearing housing 60 is shaped to have a relatively large cross-sectional area, which reduces the flow rate of the blow-by gas returning to the suction chamber 28 and promotes gravitational settling of oil droplets. In addition, a plurality of the above-mentioned ribs 66 are provided in the space formed by the recess 62 in the bearing housing 60. At least one of the non-opening regions 73 is provided in a position facing the rib 66 when the partition plate 70 is attached to the casing 2 (bearing housing 60).

[0048] By providing the rib 66 in this way, the blow-by gas passes through a complicated flow path, which further promotes oil separation. That is, when the blow-by gas and oil droplets flow in the recess 62 in the circumferential direction C, the rib 66 and the non-opening region 73 act as a throttle to generate pressure loss, and the flow speed of the blow-by gas and oil droplets in the recess 62 can be reduced, thereby reducing the number of oil droplets carried away from the recess 62 together with the blow-by gas. In addition, the blow-by gas and oil droplets flowing in the circumferential direction C between the rib 66 and the non-opening region 73 form a vortex flow downstream of the throttle formed by the rib 66 and the non-opening region 73 facing it, which promotes the coalescence of the oil droplets, and the oil droplets are expected to become larger. As a result, it is expected that the number of oil droplets carried away from the recess 62 together with the blow-by gas can be reduced.

[0049] In the reciprocating compressor 1 according to this embodiment, the partition plate 70 may include at least one non-opening region 73 in which no openings 71 are provided between two openings 71 adjacent to each other in the circumferential direction C. At least one of the non-opening regions 73 may be provided in a position facing an opening end 81 of the pressure equalizing path 80 that opens into the first recess 621 when the partition plate 70 is attached to the casing 2 (bearing housing 60). This makes it possible to reduce the amount of oil droplets carried away along with the blow-by gas from the opening end 81 opening into the first recess 621, compared to when the opening 71 is located at a position opposite the opening end 81 opening into the first recess 621.

[0050] The present disclosure is not limited to the above-described embodiments, and includes modifications to the above-described embodiments and appropriate combinations of these modifications. For example, in the above-described embodiment, the partition plate 70 has the lubricant drain hole 74, but it does not have to have the lubricant drain hole 74. In the above-described embodiment, the recess 62 is provided in the bearing housing 60, but it may be provided in the housing 22. That is, the recess 62 may be provided in the casing 2. The partition plate 70 may be fixed to the casing 2 so as to cover the recess 62.

[0051] The contents described in each of the above embodiments can be understood, for example, as follows. (1) The blow-by gas plate (partition plate 70) according to at least one embodiment of the present disclosure is a blow-by gas plate (partition plate 70) that can be attached to the casing 2 of the reciprocating compressor 1 so as to face a recess 62 (first recess 621) that is a part of the pressure equalizing passage 100 provided in the casing 2 of the reciprocating compressor 1, so as to form a pressure equalizing passage 100 for returning the blow-by gas of the reciprocating compressor 1 to the intake side. The blow-by gas plate (partition plate 70) according to at least one embodiment of the present disclosure includes one or more openings 71 provided at positions facing the recesses 62, and a mesh portion 72 provided in the openings 71 and allowing the blow-by gas to pass through.

[0052] According to the above configuration (1), by providing the mesh portion 72 at the opening 71, the area of ​​the opening 71 can be made relatively large, the flow velocity of the blow-by gas entering the recess 62 (pressure equalizing passage 100) can be reduced, and the oil droplet entraining force of the blow-by gas can be reduced, so that the amount of oil droplets entering the recess 62 (pressure equalizing passage 100) can be reduced. Also, according to the above configuration (1), the mesh portion 72 can prevent the oil droplets from entering the recess 62 (pressure equalizing passage 100), so that the amount of oil droplets entering the recess 62 (pressure equalizing passage 100) can be reduced. This can reduce oil rising.

[0053] (2) In some embodiments, in the configuration of (1) above, the opening 71 may be formed so as to include a position facing at least one of the ends 621a, 621b of the one side end 621a or the other side end 621b of the recess 62, which is formed in an annular shape and has one end 621a and the other end 621b facing downward in the circumferential direction C, when the blow-by gas plate (partition plate 70) is attached to the casing 2. The mesh portion 72 may be provided in the opening 71 so as to cover at least one of the ends 621a, 621b when the blow-by gas plate (partition plate 70) is attached to the casing 2.

[0054] According to the above configuration (2), the lubricating oil accumulated in the recess 62 (pressure equalizing passage 100) can easily return to the outside of the recess 62 (pressure equalizing passage 100) through the opening 71 and the mesh portion 72, thereby reducing oil rise.

[0055] (3) In some embodiments, in the configuration of (1) or (2) above, the openings 71 may be provided at multiple intervals in the circumferential direction C at positions facing the annularly formed recess 62 when the blow-by gas plate (partition plate 70) is attached to the casing 2.

[0056] According to the above configuration (3), the openings 71 are divided and provided in the circumferential direction C, thereby shortening the length of each opening 71 in the circumferential direction C. This shortens the extension length of the mesh portion 72 in the circumferential direction C, improving the rigidity of the mesh portion 72. Therefore, even if an external force acts on the mesh portion 72 as the blow-by gas passes through the mesh portion 72 when flowing into the recess 62 (pressure equalizing flow path 100), deformation of the mesh portion 72, etc. can be suppressed.

[0057] (4) In some embodiments, in the configuration of (3) above, the blow-by gas plate (partition plate 70) may have at least one non-opening region 73 in which no openings 71 are provided between two openings 71 adjacent to each other in the circumferential direction C. At least one of the non-opening regions 73 may be provided in a position facing a protrusion (rib 66) that is provided in the recess 62 and protrudes toward the blow-by gas plate (partition plate 70) when the blow-by gas plate (partition plate 70) is attached to the casing 2.

[0058] According to the above configuration (4), when the blow-by gas and oil droplets flow in the recess 62 (pressure equalizing passage 100) in the circumferential direction C, the protrusions (ribs 66) and the non-opening region 73 act as throttles to cause pressure loss, and the flow speed of the blow-by gas and oil droplets in the recess 62 (pressure equalizing passage 100) is reduced, thereby reducing the number of oil droplets carried away from the recess 62 (pressure equalizing passage 100) together with the blow-by gas. In addition, the blow-by gas and oil droplets flowing in the circumferential direction C between the protrusions (ribs 66) and the non-opening region 73 form a vortex flow downstream of the throttle formed by the protrusions (ribs 66) and the non-opening region 73 facing the protrusions, which promotes the coalescence of the oil droplets and increases their size. This is expected to reduce the number of oil droplets carried away from the recess 62 (pressure equalizing passage 100) together with the blow-by gas.

[0059] (5) In some embodiments, in the configuration of (3) or (4) above, the blow-by gas plate (partition plate 70) may have at least one non-opening region 73 in which no openings 71 are provided between two openings 71 adjacent to each other in the circumferential direction C. At least one of the non-opening regions 73 may be provided in a position facing an opening end 81 that opens into the recess 62 when the blow-by gas plate (partition plate 70) is attached to the casing 2.

[0060] According to the above configuration (5), the amount of oil droplets carried away together with the blow-by gas from the opening end 81 opening into the recess 62 can be reduced compared to when the opening 71 is provided in a position opposite the opening end 81 opening into the recess 62.

[0061] (6) The reciprocating compressor 1 according to at least one embodiment of the present disclosure includes any one of the blow-by gas plates (partition plate 70) described above in (1) to (5). The reciprocating compressor 1 according to at least one embodiment of the present disclosure includes a housing 22 in which a suction chamber 28, a discharge chamber 30, a cylinder 32, and a crank chamber 34 are provided, and a lower part of the crank chamber 34 is configured as an oil storage chamber 35 for storing lubricating oil. The reciprocating compressor 1 according to at least one embodiment of the present disclosure includes a piston 36 arranged to be capable of reciprocating within the cylinder 32, a crankshaft 40 arranged to be rotatable in the crank chamber 34 and connected to the piston 36 via a connecting rod, and a bearing housing 60 in which a bearing portion 50A for bearing the crankshaft 40 is arranged. The recess 62 is formed in the bearing housing 60.

[0062] According to the above configuration (6), by providing the mesh portion 72 at the opening 71, the area of ​​the opening 71 can be made relatively large, the flow velocity of the blow-by gas entering the recess 62 (pressure equalizing passage 100) can be reduced, and the oil droplet entraining force of the blow-by gas can be reduced, so that the amount of oil droplets entering the recess 62 (pressure equalizing passage 100) can be reduced. Also, according to the above configuration (6), the mesh portion 72 can prevent the oil droplets from entering the recess 62 (pressure equalizing passage 100), so that the amount of oil droplets entering the recess 62 (pressure equalizing passage 100) can be reduced. This can reduce oil rising.

[0063] (7) In some embodiments, in the configuration of (6) above, the recess 62 may be formed in an annular shape, and an end 621a on one side and an end 621b on the other side in the circumferential direction C may be provided so as to face downward. The opening 71 may be formed to include a position facing at least one of the end 621a on one side or the end 621b on the other side of the recess 62. At least one of the ends 621a, 621b, a wall surface 621c facing the circumferential direction C that defines the recess 62 may be inclined downward from the bottom surface 62a of the recess 62 toward the opening 71.

[0064] According to the above configuration (7), the lubricating oil that has flowed down the wall surface 621c and accumulated in the recess 62 (pressure equalizing passage 100) easily returns to the crank chamber 34 via the opening 71 and the mesh portion 72, thereby reducing oil rise. [Explanation of symbols]

[0065] 1 Reciprocating Compressor 2 Casing 22 Housing 24 Intake port 26 Discharge port 28 Suction chamber 30 Discharge chamber 32 cylinders 34 Crankcase 35 Oil storage room 36 Piston 38 Connecting rod 40 Crankshaft 50A bearing part 60 Bearing housing 62 Recess 62a Bottom 66 Ribs 66a Top 70 Partition 71 Opening 72 Mesh section 73 Non-opening area 74 Lubricating oil drain hole 80 Pressure Equalizing Road 81 Open end (inlet end) 82 Open end (outlet end) 100 Equal pressure channel 621 First recess 621a End 621b End 621c Wall 622 Second recess 623 Wall 623a Top 624 Wall 624a Top

Claims

1. A blow-by gas plate that can be attached to a casing of a reciprocating compressor so as to face a recess that is a part of the pressure equalizing flow passage provided in the casing, so as to form a pressure equalizing flow passage for returning blow-by gas of the reciprocating compressor to an intake side, One or more openings provided at a position opposite to the recess; a mesh portion provided in the opening portion and allowing the blow-by gas to pass through; Equipped with a blow-by gas plate.

2. the opening is formed so as to include a position facing at least one of an end portion on one side or an end portion on the other side of the recess formed in an annular shape and provided so that an end portion on one side and an end portion on the other side in a circumferential direction face downward when the blow-by gas plate is attached to the casing, the mesh portion is provided in the opening so as to cover at least one of the ends when the blow-by gas plate is attached to the casing.

2. The blow-by gas plate according to claim 1.

3. The openings are provided at intervals in a circumferential direction at positions facing the recessed portion that is formed in an annular shape when the blow-by gas plate is attached to the casing.

3. A blow-by gas plate according to claim 1 or 2.

4. at least one non-opening region in which no opening is provided between two of the openings adjacent to each other in the circumferential direction; At least one of the non-opening regions is provided in the recess at a position facing a protrusion that protrudes toward the blow-by gas plate when the blow-by gas plate is attached to the casing.

4. The blow-by gas plate according to claim 3.

5. at least one non-opening region in which no opening is provided between two of the openings adjacent to each other in the circumferential direction; At least one of the non-opening regions is provided at a position opposite to an opening end that opens into the recess when the blow-by gas plate is attached to the casing.

4. The blow-by gas plate according to claim 3.

6. A blow-by gas plate according to claim 1 or 2; a housing in which a suction chamber, a discharge chamber, a cylinder, and a crank chamber are provided, the lower part of the crank chamber being configured as an oil reservoir for storing lubricating oil; A piston reciprocally disposed within the cylinder; a crankshaft rotatably disposed in the crank chamber and connected to the piston via a connecting rod; a bearing housing in which a bearing portion that supports the crankshaft is disposed; Equipped with The recess is formed in the bearing housing. Reciprocating compressor.

7. The recess is formed in an annular shape and is provided such that one end and the other end in the circumferential direction face downward, the opening is formed to include a position facing at least one of the end portion on the one side or the end portion on the other side of the recess, At least one of the ends, a wall surface facing the circumferential direction defining the recess is inclined downward from a bottom surface of the recess toward the opening. The reciprocating compressor according to claim 6.

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