Blow-by plate and reciprocating compressor

Abstract

A blow-by plate according to at least one embodiment of the present disclosure can be attached to a housing facing a recess provided in the housing of a reciprocating compressor as a part of a pressure equalizing flow path to form the pressure equalizing flow path for returning blow-by gas of the reciprocating compressor to an intake side. A blow-by plate according to at least one embodiment of the present disclosure is provided with: one or more openings provided at positions facing a recess; and a mesh part which is provided in the opening part and through which blow-by gas can pass.

Description

TECHNICAL FIELD

[0001] The present disclosure relates to a blow-by gas plate provided to a reciprocating compressor and a reciprocating compressor provided with the blow-by gas plate. BACKGROUND

[0002] A reciprocating compressor changes a rotational motion of a crankshaft (drive shaft) into a reciprocating motion of a piston in a crank chamber, and compresses refrigerant gas circulating in a 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 portion of the crank chamber becomes an oil reservoir chamber that stores lubricating oil. The lubricating oil stored in the oil reservoir chamber is supplied to each sliding portion of the reciprocating compressor by a forced oil supply method based on an oil pump.

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

[0004] In the past, in order to prevent the pressure in the crank chamber from rising due to refrigerant gas (blow-by gas) leaking from the gap between the inner wall surface of the cylinder and the piston ring into the crank chamber, a pressure equalization passage (balance hole) that communicates the crank chamber with the suction chamber is provided to return the blow-by gas to the suction chamber.

[0005] The return of the blow-by gas flowing into the suction chamber through the pressure equalization passage to the suction chamber can entrain oil droplets in the crank chamber, and thus it is possible to cause blow-by oil (Japanese: oil up) in which the amount of lubricating oil stored in the oil reservoir chamber is reduced.

[0006] As a mechanism for preventing such blow-by oil, for example, a reciprocating compressor is disclosed in Patent Literature 1 described below, which is provided with a partition member that is disposed between the crankshaft to which the piston is connected and the opening end of the pressure equalization passage on the crank chamber side that communicates the crank chamber with the suction chamber, and is further provided with an oil separator that is disposed between the partition member and the opening end of the pressure equalization passage.

[0007] According to the reciprocating compressor thus configured, the oil droplets in the crank chamber are prevented from directly flowing into the opening end of the pressure equalization passage by the partition member, and further the amount of lubricating oil flowing into the opening end of the pressure equalization passage is reduced by the oil separator, and blow-by oil in which the amount of lubricating oil in the oil reservoir chamber is reduced is prevented.

[0008] PRIOR ART DOCUMENTS PATENT LITERATURE Patent Literature 1: International Publication No. 2014 / 054092 SUMMARY

[0009] (1) Problem to be Solved However, for the structure of Patent Literature 1, it is required to prevent blow-by oil due to the return of blow-by gas to the suction chamber without providing the partition member in the crank chamber and without providing the oil separator that protrudes into the crank chamber.

[0010] At least one embodiment of the present disclosure, in view of the above, aims to provide a blow-by gas plate capable of reducing blow-by oil due to return of blow-by gas to a suction chamber by a simple configuration, and a reciprocating compressor.

[0011] (II) Technical Solution (1) The blow-by gas plate of at least one embodiment of the present disclosure is capable of being installed in a housing of a reciprocating compressor so as to face a recess portion provided in the housing as a part of a pressure equalization flow path, to form the pressure equalization flow path for returning blow-by gas of the reciprocating compressor to an intake side, The blow-by gas plate has: one or more opening portions provided at a position opposite to the recess portion; and a mesh portion provided in the opening portion and through which the blow-by gas is capable of passing.

[0012] (2) The reciprocating compressor of at least one embodiment of the present disclosure has: the blow-by gas plate of the structure of (1) above; a housing provided with a suction chamber, a discharge chamber, a cylinder, and a crank chamber, a lower portion of the crank chamber being configured as an oil reservoir chamber that stores lubricating oil; a piston configured to reciprocate within the cylinder; a crank configured to rotate in the crank chamber and linked to the piston via a connecting rod; and a bearing housing configured with a bearing portion that axially supports the crank, the recess portion is formed in the bearing housing.

[0013] (III) Advantageous Effects According to at least one embodiment of the present disclosure, blow-by oil due to return of blow-by gas to a suction chamber can be reduced by a simple configuration. BRIEF DESCRIPTION OF DRAWINGS

[0014] Figure 1 is a view showing a schematic longitudinal cross section of a reciprocating compressor of the present embodiment together with a refrigeration cycle.

[0015] Figure 2 is a view showing a schematic cross section of a reciprocating compressor of the present embodiment.

[0016] Figure 3 is a view showing a perspective cross section of a reciprocating compressor of the present embodiment.

[0017] Figure 4 is a view showing a bearing housing and a partition from the inside of a crank chamber toward the outside.

[0018] Figure 5is a view of the bearing housing as viewed from the inside of the crank chamber toward the outside.

[0019] Figure 6 is a view schematically showing a VI-VI cross section. Figure 5 DETAILED DESCRIPTION

[0020] Hereinafter, some embodiments of the present disclosure will be described with reference to the drawings. However, the size, material, shape, relative arrangement, and the like of the constituent components described as embodiments or shown in the drawings are not intended to limit the scope of the present disclosure to them, but are merely illustrative.

[0021] For example, expressions such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric", or "coaxial" or the like indicating relative or absolute arrangement do not mean only a strictly meaning arrangement, but also mean a state of angularly or distantly displaced to the extent that the same function can be obtained with a tolerance.

[0022] For example, expressions such as "same", "equal", and "homogeneous" or the like indicating that things are in an equal state do not mean only a strictly equal state, but also a state in which there is a difference to the extent that the same function can be obtained with a tolerance.

[0023] For example, expressions such as quadrangular shape, cylindrical shape, or the like indicating shape do not mean only a geometrically strict meaning quadrangular shape, cylindrical shape, or the like, but also a shape including a concave-convex portion, a chamfered portion, or the like within a range in which the same effect can be obtained.

[0024] On the other hand, expressions such as "provided with", "having", "possessing", "including", or "having" one constituent element are not exclusive expressions that exclude the presence of other constituent elements.

[0025] Reference Signs List Figures 1-6 Embodiments of the present application are described. Furthermore, the same reference signs are attached to the same elements throughout the drawings, and repeated description is omitted. For the dimensional proportions of the drawings, sometimes exaggeration is made for the convenience of explanation, and the actual proportions are different.

[0026] Figure 1 is a view showing a schematic longitudinal cross section of the reciprocating compressor 1 of the present embodiment together with a refrigeration cycle. Figure 2 is a view showing a schematic transverse cross section of the reciprocating compressor 1 of the present embodiment. Figure 3 is a perspective cross-sectional view showing the reciprocating compressor 1 of the present embodiment. Figure 4 is a view of the bearing housing 60 and the partition 70 as viewed from the inside of the crank chamber 34 toward the outside. Figure 5 is a view of the bearing housing 60 as viewed from the inside of the crank chamber 34 toward the outside.​Figure 6 is a view schematically showing a VI-VI cross-sectional view of Figure 5 . Further, in Figure 5 , the opening portion 71 of the partition 70 and the lubricating oil discharge hole 74 are indicated by a double-dot chain line for easy understanding.

[0027] First, the structure of the refrigeration cycle will be described with reference to Figure 1 .

[0028] The refrigeration cycle has a ring-shaped refrigerant circulation path 10 in which a reciprocating compressor 1, a condenser (high-pressure side heat exchanger) 12, an expansion valve (expander) 14, and an evaporator (low-pressure side heat exchanger) 16 are connected in this order in the circulation direction of the refrigerant. Further, in the present embodiment, an oil separator 18 and a reservoir 20 are also provided in the refrigerant circulation path 10.

[0029] In the refrigeration cycle, the reciprocating compressor 1 is configured to, for example, suck in refrigerant at a pressure (suction pressure) of 0.1 MPa to 0.3 MPa and compress it to discharge refrigerant at a pressure (discharge pressure) of 1.5 MPa to 2 MPa, but the range of the suction pressure and the discharge pressure of the refrigerant is not limited thereto. The refrigerant is, for example, various alternative refrigerants to freon such as R32, or ammonia, carbon dioxide, or the like.

[0030] Next, the structure of the reciprocating compressor 1 of the present embodiment will be described with reference to Figures 1-6 .

[0031] In summary, the reciprocating compressor 1 has: a housing 22; a piston 36 disposed in a cylinder 32 so as to be able to reciprocate; a crankshaft 40 disposed in a crank chamber 34 so as to be able to rotate; a bearing portion 50A on the oil pump 90 side and a bearing portion 50B on the one end side (right side in Figure 1 ) of the crankshaft 40, which shaft-support the crankshaft 40; a bearing housing 60 in which the bearing portion 50A on the oil pump 90 side is disposed; a partition 70 provided between the bearing housing 60 and the crank chamber 34, which forms a closed space V together with the bearing housing 60; and a pressure equalizing path 80 which communicates the closed space V and the suction chamber 28. Hereinafter, each structure will be described. Further, for ease of description, a circumferential direction centered on a rotation center axis AX of the crankshaft 40 will be referred to as a circumferential direction C, an extending direction of the rotation center axis AX will be referred to as an axial direction X, and a radial direction centered on the rotation center axis AX will be referred to as a radial direction R. In addition, the vertical direction coincides with the up-down direction of the paper in each drawing.

[0032] As shown in Figure 1As shown, the housing 22 is provided with an intake port 24 and an exhaust port 26. The intake port 24 is connected to the outlet of the evaporator 16 via a pipe, and the exhaust port 26 is connected to the inlet of the oil separator 18 via a pipe.

[0033] like Figures 1-3 As shown, the housing 22 contains an intake chamber 28, an exhaust chamber 30, a cylinder 32, a crankshaft chamber 34, and an oil reservoir 35. A piston 36 is arranged reciprocatingly within the cylinder 32, dividing the cylinder 32 into a compression chamber W. The intake chamber 28 communicates with the intake port 24 and is also connected to the compression chamber W via an intake valve. The exhaust chamber 30 communicates with the exhaust port 26 and is also connected to the compression chamber W via an exhaust valve.

[0034] The lower end of cylinder 32 communicates with crankshaft chamber 34, and connecting rod 38, which is connected to piston 36, extends into crankshaft chamber 34. Crankshaft 40 is rotatably disposed in crankshaft chamber 34, and connecting rod 38 is connected to crankshaft 40.

[0035] like Figure 1 As shown, an oil reservoir 35 is formed at the bottom of the crankshaft chamber 34. The oil stored in the oil reservoir 35 is supplied as lubricating oil to each sliding part during the operation of the reciprocating compressor 1. In this embodiment, oil filters 46 and 48 for purifying the lubricating oil are respectively provided inside the oil reservoir 35 and outside the housing 22.

[0036] One end of crankshaft 40 ( Figure 1 The crankshaft 40 (right side) is hermetically connected to the housing 22 via the shaft seal 43, and a drive source (not shown) is connected to the outer end of the crankshaft 40. When the crankshaft 40 is rotated by the drive source, the piston 36 reciprocates within the cylinder 32, thereby repeatedly performing the refrigerant intake stroke, compression stroke, and discharge stroke.

[0037] like Figure 3 As shown, the bearing section 50A is configured to provide shaft support for the crankshaft 40 on the side opposite to the drive source, the oil pump 90. Figure 3 As shown, a groove 51 is formed on the inner circumference of the bearing portion 50A to allow lubricating oil from the oil reservoir 35 to contact the outer circumference of the crankshaft 40. One end side of the bearing portion 50A ( Figure 3 The near-front side has a flange shape, configured to abut against the bearing housing 60.

[0038] like Figure 3 As shown, a bearing portion 50A is disposed in the bearing housing 60. The bearing housing 60 is fixed to the housing 22 by a fixing part (not shown). The fixing part is not particularly limited, and may be, for example, a bolt.

[0039] In the reciprocating compressor 1 of this embodiment, the housing 22 and the bearing housing 60 are included in the outer casing 2 of the reciprocating compressor 1, and the outer casing 2 forms the crankshaft chamber 34 and the oil reservoir 35. That is, the housing 22 and the bearing housing 60 are components constituting the outer casing 2 of the reciprocating compressor 1 of this embodiment.

[0040] like Figure 3 As shown, an oil passage 61 for lubricating oil is formed on the radially outer side of the bearing housing 60. Additionally, on one end side of the bearing housing 60 ( Figure 3 A recess 62 is formed on the near-front side of the bearing housing 60, axially recessed towards the crankshaft 40. Fixed to the bearing housing 60 by a partition 70, the recess 62 forms a closed space V. The closed space V includes a first closed space V1 connected to the pressure equalization circuit 80 and a second closed space V2 connected to the oil passage 61. Lubricating oil supplied from the oil reservoir 35 to the bearing housing 60 flows through the oil passage 61 to the second closed space V2.

[0041] The recess 62 extends circumferentially C in the region radially outer of the bearing portion 50A, surrounding the bearing portion 50A in a circumferential direction C. The recess 62 includes a first recess 621 forming a first enclosed space V1 and a second recess 622 forming a second enclosed space V2. The first recess 621 and the second recess 622 are separated by wall portions 623 and 624. That is, if the partition 70 is fixed to the bearing housing 60, the first enclosed space V1 is separated from the second enclosed space V2.

[0042] When viewed from the inside of the crankshaft chamber 34 toward the outside along the axial direction X, the first recess 621 and the second recess 622 each have a partially annular shape.

[0043] The second recess 622 is located below the first recess 621.

[0044] Multiple protrusions are formed in the recess 62 as ribs 66 to strengthen the bearing housing 60. The protrusions extend radially R in the recess 62 and protrude axially X from the outside of the crankshaft chamber 34 toward the inside, i.e. toward the partition 70 described later.

[0045] Furthermore, the rib 66 protrudes less from the bottom surface 62a of the recess 62 toward the axial X than the wall portions 623 and 624. Therefore, if the partition 70, described later, is fixed to the bearing housing 60, the partition 70 is in close contact with the top surfaces 623a and 624a of the wall portions 623 and 624 toward the axial X, but is separated from the top surface 66a of the rib 66 toward the axial X in the axial X direction.

[0046] like Figure 3As shown in FIG. 1, the partition plate 70 is provided between the bearing housing 60 and the crank chamber 34. In addition, the partition plate 70 is fixed to the bearing housing 60 in a manner of covering the recessed portion 62 of the bearing housing 60. The method of fixing the partition plate 70 to the bearing housing 60 is not particularly limited, and is, for example, fastening with a bolt. That is, the partition plate 70 is disposed on the inner side of the crank chamber 34 with respect to the recessed portion 62 along the axial direction X.

[0047] As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2. Figure 3 Figure 4 As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2.

[0048] As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2. Figure 3 Figure 4 As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2.

[0049] As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2. Figure 3 Figure 3 As shown in FIG. 1, the partition plate 70 has an opening portion 71 that communicates the crank chamber 34 and the first closed space V1. In addition, the partition plate 70 has a lubricating oil discharge hole 74 that communicates the crank chamber 34 and the second closed space V2.

[0050] The mesh portion 72 is provided at each opening portion 71. The mesh portion 72 is a mesh member provided in a manner of covering each opening portion 71. The mesh portion 72 is preferably provided with a mesh size through which blow-by gas can pass, and through which oil droplets of lubricating oil cannot pass or are difficult to pass.

[0051] The partition plate 70 has a non-opening region 73 in which no opening portion 71 is provided between two adjacent opening portions 71 in the circumferential direction C. In the reciprocating compressor 1 of the present embodiment, the partition plate 70 has a plurality of non-opening regions 73. At least any one of the plurality of non-opening regions 73 is provided at a position that opposes the rib 66 in the axial direction X when the partition plate 70 is mounted to the bearing housing 60.

[0052] The equalizing passage 80 is provided in order to suppress an increase in the pressure of the crank chamber 34 due to blow-by gas leaking from the gap between the piston 36 and the wall surface of the cylinder 32 in the operation of the reciprocating compressor 1.

[0053] The equalizing passage 80 has an opening end (an inlet end) 81 that opens to the first closed space V1 and an opening end (an outlet end) 82 that opens to the suction chamber 28 (see FIG. 1). Figure 3

[0054] ​​​​That is, in the reciprocating compressor 1 of the present embodiment, the equalizing flow path 100 for returning blow-by gas of the reciprocating compressor 1 to the intake side (specifically, the suction chamber 28) is formed by the recess 62, the partition 70, and the equalizing passage 80 that form the first closed space V1.

[0055] Next, the effects of the reciprocating compressor 1 of the present embodiment will be described.

[0056] For example, in the case of a reciprocating compressor in which the partition 70 is not provided, oil droplets of lubricating oil that has been lubricated to bearings and the like scatters from the crankshaft and the bearings during operation of the reciprocating compressor, and the lubricating oil is entrained by blow-by gas that flows into the suction chamber through the equalizing passage, and the oil amount of the oil reservoir decreases, and blow-by can occur.

[0057] In contrast, in the reciprocating compressor 1 of the present embodiment, since the partition 70 is provided between the bearing housing 60 and the crank chamber 34, lubricating oil that is entrained by blow-by gas through the mesh portions 72 that cover the respective opening portions 71 is difficult to pass through the mesh portions 72, and thus returns to the oil reservoir 35. Furthermore, even if the lubricating oil that is entrained by blow-by gas slightly passes through the mesh portions 72, the entrained oil droplets become large during passage through the first closed space V1, and are separated from the blow-by gas by gravity. The oil droplets that are separated from the blow-by gas return to the oil reservoir 35 from the lower portion of the first closed space V1 via the opening portions 71 and the mesh portions 72. On the other hand, the blow-by gas from which the oil droplets are separated moves from the first closed space V1 to the suction chamber 28 via the equalizing passage 80. Thus, the amount of lubricating oil that flows into the suction chamber 28 through the equalizing passage 80 decreases, and blow-by of the reciprocating compressor 1 can be prevented.

[0058] In the reciprocating compressor 1 of the present embodiment, by providing the mesh portions 72 at the opening portions 71, the area of the opening portions 71 can be made relatively large, the flow rate of blow-by gas that invades the first recess 621 can be reduced, and the oil droplet entrainment force of the blow-by gas can be reduced, and thus the amount of oil droplets that invade the first recess 621 can be reduced. Furthermore, in the reciprocating compressor 1 of the present embodiment, since the mesh portions 72 can be used to hinder the invasion of oil droplets into the first recess 621, the amount of oil droplets that invade the first recess 621 can be reduced. Thus, blow-by can be reduced.

[0059] In the reciprocating compressor 1 of the present embodiment, the first recess 621 that forms the first closed space V1 is formed in a ring shape, and the end portion 621a on one side and the end portion 621b on the other side in the circumferential direction C are disposed so as to face downward (at a position that is lower than other portions). The opening portion 71 is formed so as to include a position that is axially X opposite to at least either one of the end portion 621a on one side or the end portion 621b on the other side. Figure 5 In the example shown in FIG. 6, the opening portion 71 is formed so as to include a position that is axially X opposite to both the end portion 621a on one side and the end portion 621b on the other side.

[0060] For example, Figure 6 As shown, in at least one end 621a, 621b, the wall surface 621c of the first recess 621 facing circumferential direction C is inclined downwards as it extends from the bottom surface 62a of the first recess 621 toward the partition 70. Furthermore, in Figure 6 The image shows the vicinity of one end 621a.

[0061] Therefore, the lubricating oil accumulated in the first recess 621 along the wall 621c can easily return to the crankshaft chamber 34 through the opening 71 and the mesh 72, thus reducing oil leakage.

[0062] In the reciprocating compressor 1 of this embodiment, when the partition plate 70 is installed on the outer casing 2 (bearing housing 60), a plurality of openings 71 are provided at intervals along the circumferential direction C at positions opposite to the annular recess 62 in the axial direction X.

[0063] By dividing the openings 71 along the circumferential direction C, the length of the circumferential direction C of each opening 71 is shortened. As a result, the circumferential extension length of the mesh portion 72 is shortened, and the rigidity of the mesh portion 72 is increased. Therefore, even if external force is applied to the mesh portion 72 through the mesh portion 72 when air flows into the first recess 621, deformation of the mesh portion 72 can be suppressed.

[0064] Within the bearing housing 60, the first enclosed space V1 is shaped with a relatively large flow path cross-sectional area, reducing the return velocity of the blow-by gas to the suction chamber 28, thereby promoting the gravity settling of oil droplets. Furthermore, a plurality of the aforementioned ribs 66 are provided within the space formed by the recess 62 within the bearing housing 60. At least one of the non-opening regions 73 is positioned opposite the ribs 66 in the axial direction X when the partition 70 is mounted on the housing 2 (bearing housing 60).

[0065] By arranging the ribs 66 in this way, the blow-by gas passes through a complex flow path, thereby further promoting oil separation. Specifically, when the blow-by gas and oil droplets flow circumferentially (C) within the recess 62, the ribs 66 and the non-opening region 73 act as a throttling section, generating pressure loss. This reduces the flow velocity of the blow-by gas and oil droplets within the recess 62, thus reducing the amount of oil droplets carried away from the recess 62 along with the blow-by gas. Furthermore, by forming vortices downstream of the throttling section on the downstream side of the throttling section between the ribs 66 and the non-opening region 73, it is expected that the oil droplets will coalesce and become larger. This throttling section is formed by the ribs 66 and the non-opening region 73, which is axially opposite the ribs 66 (X). Therefore, it is expected that the amount of oil droplets carried away from the recess 62 along with the blow-by gas will be reduced.

[0066] In the reciprocating compressor 1 of the present embodiment, the partition plate 70 can have at least one non-opening region 73 in which no opening portion 71 is provided between two opening portions 71 adjacent in the circumferential direction C. At least one of the non-opening regions 73 can be provided at a position facing the opening end 81 of the pressure-equalizing path 80 opening toward the first recessed portion 621 in the axial direction X when the partition plate 70 is installed to the casing 2 (the bearing housing 60). That is, at least one of the non-opening regions 73 can be provided at a position overlapping the opening end 81 in the circumferential direction C when viewed in the axial direction X.

[0067] Thus, compared to a case in which the opening portion 71 is provided at a position facing the opening end 81 of the first recessed portion 621 in the axial direction X, it is possible to reduce oil droplets taken away together with blow-by gas from the opening end 81 of the first recessed portion 621.

[0068] The present disclosure is not limited to the above-described embodiments, and includes modes in which the above-described embodiments are modified, and modes in which these modes are appropriately combined.

[0069] For example, in the above-described embodiments, the partition plate 70 has the lubricating oil discharge hole 74, but can not have the lubricating oil discharge hole 74.

[0070] In addition, in the above-described embodiments, the recessed portion 62 is provided to the bearing housing 60, but can be provided to the casing 22. That is, the recessed portion 62 can be provided to the casing 2. Also, the partition plate 70 can be fixed to the casing 2 in a manner covering the recessed portion 62.

[0071] The content described in each of the above-described embodiments can be grasped, for example, as follows.

[0072] (1) The blow-by gas plate (partition plate 70) of at least one embodiment of the present disclosure can be installed to the casing 2 facing the recessed portion 62 (first recessed portion 621) provided to the casing 2 of the reciprocating compressor 1 as a part of the pressure-equalizing flow path 100, to form the pressure-equalizing flow path 100 for returning blow-by gas of the reciprocating compressor 1 to the intake side. The blow-by gas plate (partition plate 70) of at least one embodiment of the present disclosure has: one or more opening portions 71 provided at a position facing the recessed portion 62; and a mesh portion 72 provided to the opening portion 71 through which blow-by gas can pass.

[0073] According to the structure of the above (1), by providing the mesh portion 72 at the opening portion 71, the area of the opening portion 71 can be made relatively large, the flow rate of blow-by gas that intrudes into the recess portion 62 (the equalizing flow path 100) can be reduced, and the oil droplet entrainment force of the blow-by gas can be reduced, so the amount of oil droplets that intrude into the recess portion 62 (the equalizing flow path 100) can be reduced. In addition, according to the structure of the above (1), the intrusion of oil droplets into the recess portion 62 (the equalizing flow path 100) can be hindered by the mesh portion 72, so the amount of oil droplets that intrude into the recess portion 62 (the equalizing flow path 100) can be reduced. Thus, blow-by oil can be reduced.

[0074] (2) In some embodiments, in the structure of the above (1), the opening portion 71 can be formed to include a position that opposes at least either one of an end portion 621a of one side of a circumferential direction C of the recess portion 62 or an end portion 621b of the other side when the blow-by gas plate (the partition plate 70) is attached to the housing 2, wherein the recess portion 62 is formed in a ring shape and is provided such that the end portion 621a of one side and the end portion 621b of the other side face downward. The mesh portion 72 can be provided at the opening portion 71 so as to cover at least either one of the end portions 621a, 621b when the blow-by gas plate (the partition plate 70) is attached to the housing 2.

[0075] According to the structure of the above (2), lubricating oil accumulated in the recess portion 62 (the equalizing flow path 100) is easily returned to the outside of the recess portion 62 (the equalizing flow path 100) via the opening portion 71 and the mesh portion 72, so blow-by oil can be reduced.

[0076] (3) In some embodiments, in the structure of the above (1) or (2), it can also be that a plurality of opening portions 71 are provided at intervals along the circumferential direction C at positions that oppose the recess portion 62 formed in a ring shape when the blow-by gas plate (the partition plate 70) is attached to the housing 2.

[0077] According to the structure of the above (3), by dividing the opening portion 71 along the circumferential direction C, the length of the circumferential direction C of each opening portion 71 is shortened. Thus, the extension length of the mesh portion 72 in the circumferential direction C is shortened, and the rigidity of the mesh portion 72 is increased. Therefore, even if an external force acts on the mesh portion 72 when blow-by gas flows into the recess portion 62 (the equalizing flow path 100) through the mesh portion 72, deformation of the mesh portion 72 and the like can be suppressed.

[0078] (4) In some embodiments, in the structure of the above (3), the blow-by gas plate (the partition plate 70) can have at least one non-opening region 73 that is a region in which no opening portion 71 is provided between two opening portions 71 adjacent in the circumferential direction C. At least one of the non-opening regions 73 can be provided at a position that opposes a protrusion (a rib 66) provided in the recess portion 62 and protruding toward the blow-by gas plate (the partition plate 70) when the blow-by gas plate (the partition plate 70) is attached to the housing 2.

[0079] According to the structure of the above (4), when blow-by gas and oil droplets flow in the circumferential direction C in the recess 62 (the equalizing flow path 100), the protrusions (ribs 66) and the non-opening regions 73 can function as a throttle portion to generate pressure loss, and can reduce the flow rate of the blow-by gas and the oil droplets in the recess 62 (the equalizing flow path 100) to reduce the oil droplets that are taken out from the recess 62 (the equalizing flow path 100) together with the blow-by gas. In addition, by forming a vortex of the blow-by gas and the oil droplets flowing in the circumferential direction C between the protrusions (ribs 66) and the non-opening regions 73 on the downstream side of the throttle portion formed by the protrusions (ribs 66) and the non-opening regions 73 opposite thereto, it is possible to expect to promote the merging of the oil droplets, and the oil droplets become large. Thus, it is possible to expect to reduce the oil droplets that are taken out from the recess 62 (the equalizing flow path 100) together with the blow-by gas.

[0080] (5) In some embodiments, in the structure of the above (3) or (4), the blow-by gas plate (the partition plate 70) can have at least one non-opening region 73 that is a region in which no opening portion 71 is provided between two adjacent opening portions 71 in the circumferential direction C. When the blow-by gas plate (the partition plate 70) is installed in the housing 2, at least one of the non-opening regions 73 can be provided at a position opposite to the opening end 81 that opens to the recess 62 in the axial direction X.

[0081] According to the structure of the above (5), compared to a case in which the opening portion 71 is provided at a position opposite to the opening end 81 that opens to the recess 62 in the axial direction X, it is possible to reduce the oil droplets that are taken out from the opening end 81 that opens to the recess 62 together with the blow-by gas.

[0082] (6) The reciprocating compressor 1 of at least one embodiment of the present disclosure has the blow-by gas plate (the partition plate 70) of any one of the above (1) to (5). The reciprocating compressor 1 of at least one embodiment of the present disclosure has a housing 22 provided with a suction chamber 28, a discharge chamber 30, a cylinder 32, and a crank chamber 34, and a lower portion of the crank chamber 34 is configured as an oil reservoir 35 that stores lubricating oil. The reciprocating compressor 1 of at least one embodiment of the present disclosure has a piston 36 that is disposed in the cylinder 32 so as to be able to reciprocate, a crankshaft 40 that is disposed in the crank chamber 34 so as to be able to rotate and is linked to the piston 36 via a connecting rod 38, and a bearing housing 60 in which a bearing portion 50A that supports the crankshaft 40 in a shaft direction is disposed. The recess 62 is formed in the bearing housing 60.

[0083] According to the structure of the above (6), by providing the mesh portion 72 at the opening portion 71, the area of the opening portion 71 can be made relatively large, the flow rate of blowby gas that intrudes into the recess portion 62 (the pressure equalization flow path 100) can be reduced, and the oil droplet entrainment force of the blowby gas can be reduced, so the amount of oil droplets that intrude into the recess portion 62 (the pressure equalization flow path 100) can be reduced. In addition, according to the structure of the above (6), the intrusion of oil droplets into the recess portion 62 (the pressure equalization flow path 100) can be hindered by the mesh portion 72, so the amount of oil droplets that intrude into the recess portion 62 (the pressure equalization flow path 100) can be reduced. Thus, blowby oil can be reduced.

[0084] (7) In some embodiments, in the structure of the above (6), the recess portion 62 can be formed in a ring shape, and the end portion 621a on one side of the circumferential direction C and the end portion 621b on the other side can be disposed so as to face downward. The opening portion 71 can be formed so as to include a position that opposes at least either one of the end portion 621a on one side or the end portion 621b on the other side of the recess portion 62. In at least either one of the end portions 621a, 621b, a wall surface 621c that defines the recess portion 62 in the circumferential direction C can be inclined so as to face downward as it moves away from the bottom surface 62a of the recess portion 62 toward the opening portion 71.

[0085] According to the structure of the above (7), lubricating oil that accumulates inside the recess portion 62 (the pressure equalization flow path 100) along the above wall surface 621c is easily returned to the crank chamber 34 via the opening portion 71 and the mesh portion 72, so blowby oil can be reduced.

[0086] Reference Signs 1: reciprocating compressor; 2: housing; 22: casing; 24: suction port; 26: discharge port; 28: suction chamber; 30: discharge chamber; 32: cylinder; 34: crank chamber; 35: oil reservoir; 36: piston; 38: connecting rod; 40: crankshaft; 50A: bearing portion; 60: bearing housing; 62: recess portion; 62a: bottom surface; 66: rib; 66a: top portion; 70: partition; 71: opening portion; 72: mesh portion; 73: non-opening region; 74: lubricating oil discharge hole 80: equalizing passage 81: open end (inlet end) 82: open end (outlet end) 100: equalizing passage 621: first recess 621a: end portion 621b: end portion 621c: wall surface 622: second recess 623: wall portion 623a: top portion 624: wall portion 624a: top portion

Claims

1. A gas bypass plate capable of being installed in a housing of a reciprocating compressor so as to face a recess provided in the housing as a part of a pressure equalization flow path, to form the pressure equalization flow path for returning gas bypass of the reciprocating compressor to an intake side, comprising: one or more opening portions provided at positions opposite to the recess; and a mesh portion provided at the opening portion and through which the gas bypass is able to pass.

2. The gas bypass plate according to claim 1, wherein the opening portion is formed to include a position opposite to at least either one of an end portion of one side or an end portion of the other side in a circumferential direction of the recess when the gas bypass plate is installed in the housing, wherein the recess is formed in a ring shape and is provided so that the end portion of the one side and the end portion of the other side face downward, and wherein the mesh portion is provided at the opening portion so as to cover at least either one of the end portions when the gas bypass plate is installed in the housing.

3. The gas bypass plate according to claim 1 or 2, wherein a plurality of the opening portions are provided at positions opposite to the recess formed in a ring shape and spaced apart in the circumferential direction when the gas bypass plate is installed in the housing.

4. The gas bypass plate according to claim 3, comprising at least one non-opening region that is a region in which the opening portion is not provided between two of the opening portions adjacent in the circumferential direction, and wherein at least one of the non-opening regions is provided at a position opposite to a protrusion provided in the recess and protruding toward the gas bypass plate when the gas bypass plate is installed in the housing.

5. The gas bypass plate according to claim 3, comprising at least one non-opening region that is a region in which the opening portion is not provided between two of the opening portions adjacent in the circumferential direction, and wherein at least one of the non-opening regions is provided at a position axially opposite to an opening end that is open to the recess when the gas bypass plate is installed in the housing.

6. A reciprocating compressor comprising: the gas bypass plate according to claim 1 or 2; a housing provided with a suction chamber, a discharge chamber, a cylinder, and a crank chamber, a lower portion of the crank chamber being configured as an oil reservoir chamber that stores lubricating oil; a piston configured to be able to reciprocate in the cylinder; a crankshaft configured to be able to rotate in the crank chamber and linked to the piston via a connecting rod; and a bearing housing configured with a bearing portion that axially supports the crankshaft, wherein the recess is formed in the bearing housing.

7. The reciprocating compressor according to claim 6, wherein the recess is formed in a ring shape and is provided so that an end portion of one side and an end portion of the other side in a circumferential direction face downward, wherein the opening portion is formed to include a position opposite to at least either one of the end portion of the one side or the end portion of the other side of the recess, and wherein, in at least either one of the end portions, a wall surface of the recess that faces the circumferential direction is inclined so as to face downward as it goes from a bottom surface of the recess toward the opening portion. ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​ ​

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