Gas flow regulator and reciprocating compressor

Abstract

To provide a gas flow regulator which can inhibit oil loss in a reciprocating compressor, and to provide the reciprocating compressor.SOLUTION: A gas flow regulator is used for a reciprocating compressor having a suction chamber and a crank chamber located below the suction chamber. The gas flow regulator includes a plate spring attached to a partition wall which partitions a first chamber, which is one of the crank chamber and a first space capable of communicating with the crank chamber, from a second chamber, which is one of the suction chamber and a second space capable of communicating with the suction chamber, the plate spring configured to close an oil return hole provided on the partition wall from the first chamber side by a pressure difference between the first chamber and the second chamber. The plate spring has a spring hole having a diameter smaller than that of the oil return hole.SELECTED DRAWING: Figure 3

Description

Technical Field

[0005] , ,

[0001] The present disclosure relates to a gas flow regulator and a reciprocating compressor.

Background Art

[0002] A reciprocating compressor is applied, for example, to a refrigeration cycle and is used for compressing a refrigerant gas. As described in, for example, Patent Document 1, an intake chamber, a discharge chamber, a cylinder, and a crank chamber are partitioned in the housing of the reciprocating compressor, and the lower part of the crank chamber is used as an oil storage chamber for storing lubricating oil. A piston is disposed in the cylinder so as to be reciprocable, and a crankshaft is disposed in the crank chamber so as to be rotatable via a bearing. The piston is connected to the crankshaft via a connecting rod, and the rotational motion of the crankshaft is converted into the reciprocating motion of the piston. The cylinder, the intake chamber, and the discharge chamber can communicate with each other via an intake valve and a discharge valve. During operation of the reciprocating compressor, when power is externally supplied to the crankshaft and the piston reciprocates, the refrigerant gas to be compressed is sucked into the cylinder through the intake valve from the intake chamber, compressed, and then discharged into the discharge chamber through the discharge valve.

[0003] During compression of the refrigerant gas in the cylinder, the refrigerant gas to be compressed leaks from the gap between the inner wall surface of the cylinder and the piston ring and flows into the crank chamber. In order to prevent the pressure in the crank chamber from increasing due to this refrigerant gas, a pressure equalizing passage that communicates the crank chamber and the intake chamber is provided. Therefore, during normal operation (load operation) of the compressor, the refrigerant gas in the crank chamber is returned to the intake chamber through the pressure equalizing passage.

Prior Art Documents

Patent Documents

[0004]

Patent Document 1

Summary of the Invention

Problems to be Solved by the Invention

[0005] The above-described reciprocating compressor may experience at least one of the following problems: For example, the pressure in the intake chamber may decrease, such as when the reciprocating compressor is started or when the evaporation pressure of the refrigerant gas decreases. In this case, the pressure difference between the crankcase and the intake chamber increases, the amount of refrigerant gas flowing from the crankcase to the intake chamber increases, and there is a risk of a rapid decrease in pressure in the crankcase. As a result, the refrigerant dissolved in the lubricating oil in the oil reservoir chamber may gasify, causing oil foaming, and the atomized lubricating oil may flow into the intake chamber along with the refrigerant gas, potentially causing oil burning in the reciprocating compressor. Furthermore, during the operation of the reciprocating compressor, lubricating oil from each bearing is scattered as oil droplets within the crankcase. These scattered oil droplets flow into the intake chamber through the pressure equalization passage and oil return hole along with the flow of refrigerant gas. The lubricating oil accumulated in the intake chamber is drawn into the cylinder and then discharged. The amount of lubricating oil flowing into the intake chamber increases in proportion to the return rate of the refrigerant gas to the intake chamber. If the return rate is high, the amount of lubricating oil discharged from the reciprocating compressor increases, which can reduce the amount of lubricating oil inside the compressor and potentially cause oil leakage.

[0006] The purpose of this disclosure is to provide a gas flow regulator and a reciprocating compressor that can suppress oil leakage in a reciprocating compressor. [Means for solving the problem]

[0007] A gas flow regulator according to at least one embodiment of the present disclosure is A gas flow regulator for a reciprocating compressor having an intake chamber and a crank chamber located below the intake chamber, The device comprises a leaf spring attached to a partition wall separating a first chamber, which is either the crank chamber or a first space communicating with the crank chamber, and a second chamber, which is either the intake chamber or a second space communicating with the intake chamber, and configured to close an oil return hole provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber. The leaf spring has a spring hole that is smaller in diameter than the oil return hole.

[0008] A reciprocating compressor according to at least one embodiment of the present disclosure is Inhalation room and A crank chamber located below the intake chamber, A gas flow regulator for adjusting the flow of oil in the crankcase into the intake chamber, A partition wall separates a first chamber, which is either the crank chamber or a first space communicating with the crank chamber, from a second chamber, which is either the intake chamber or a second space communicating with the intake chamber. Equipped with, The aforementioned gas flow regulator is The leaf spring is attached to the partition wall and is configured to close the oil return hole provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber, The leaf spring has a spring hole that is smaller in diameter than the oil return hole. [Effects of the Invention]

[0009] According to this disclosure, it is possible to provide a gas flow regulator that can suppress oil leakage in a reciprocating compressor, and a reciprocating compressor. [Brief explanation of the drawing]

[0010] [Figure 1] This is a schematic longitudinal cross-sectional view of a reciprocating compressor according to one embodiment of the present disclosure. [Figure 2] This is a schematic diagram of a reciprocating compressor according to the first embodiment. [Figure 3] This is a schematic diagram of a gas flow regulator according to the first embodiment. [Figure 4] This is a schematic diagram showing the structure of a leaf spring. [Figure 5] This is another schematic diagram of the gas flow regulator according to the first embodiment. [Figure 6] This is a schematic diagram of a gas flow regulator according to the second embodiment. [Figure 7] This is a schematic diagram showing a part of a reciprocating compressor according to the third embodiment. [Figure 8]It is a schematic diagram of a gas flow regulator according to the third embodiment. [Figure 9] It is a schematic diagram showing a reciprocating compressor according to the fourth embodiment.

Modes for Carrying Out the Invention

[0011] 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 the components described as embodiments or shown in the drawings are not intended to limit the scope of the present disclosure, but are merely illustrative examples. For example, expressions representing relative or absolute arrangements such as "in a certain direction", "along a certain direction", "parallel", "orthogonal", "center", "concentric", or "coaxial" not only strictly represent such arrangements, but also represent a state in which there are tolerances or relative displacements with angles and distances such that the same function can be obtained. For example, expressions representing that things such as "identical", "equal", and "homogeneous" are in an equal state not only strictly represent an equal state, but also represent a state in which there are tolerances or differences such that the same function can be obtained. For example, expressions representing shapes such as a rectangular shape or a cylindrical shape not only represent shapes such as a rectangular shape or a cylindrical shape in a geometrically strict sense, but also represent shapes including concave and convex portions, chamfered portions, etc. within a range where the same effect can be obtained. On the other hand, the expression "comprising", "including", or "having" a component is not an exclusive expression excluding the existence of other components. Note that the same reference numerals may be assigned to the same configurations and the description may be omitted.

[0012] <1. Outline of the reciprocating compressor 1> FIG. 1 is a schematic longitudinal sectional view of a reciprocating compressor 1 according to an embodiment of the present disclosure. The reciprocating compressor 1 is incorporated into a refrigeration cycle (not shown) and is configured to compress a refrigerant gas G. The refrigerant gas G may be, for example, a fluorocarbon, ammonia, or carbon dioxide, but is not particularly limited. The refrigeration cycle is composed of, for example, a primary refrigerant circuit and a secondary refrigerant circuit, and the reciprocating compressor 1 may be incorporated into the primary refrigerant circuit. As another example, the refrigeration cycle may be composed of a high-stage refrigeration cycle and a low-stage refrigeration cycle, and the reciprocating compressor 1 may be incorporated into each of the two cycles. Hereinafter, although the reciprocating compressor 1 is exemplified as a multi-cylinder reciprocating compressor having a plurality of pistons 36 and a plurality of cylinders 32, the reciprocating compressor 1 of the present disclosure may be a single-cylinder reciprocating compressor.

[0013] The reciprocating compressor 1 includes a housing 22, and a suction port 24 and a discharge port 26 for the refrigerant gas G are provided in the housing 22. Further, inside the housing 22, a suction chamber 28 communicating with the suction port 24, a discharge chamber 30 communicating with the discharge port 26, a cylinder 32 provided with a suction valve and a discharge valve, and a crank chamber 34 located below the cylinder 32 are provided. A piston 36 is disposed in the cylinder 32 so as to be reciprocable, and a compression chamber is defined by the inner wall surface of the cylinder 32 and the piston 36. The compression chamber can communicate with the suction chamber 28 via the suction valve and can communicate with the discharge chamber 30 via the discharge valve.

[0014] One end of the cylinder 32 communicates with the crank chamber 34, and a connecting rod 38 connected to the piston 36 extends into the crank chamber 34. The crank chamber 34 is located below the suction chamber 28, and the two chambers are separated from each other by a partition wall 29 that forms a part of the housing 22. A crankshaft 40 is rotatably disposed in the crank chamber 34, and the connecting rod 38 is connected to the crankshaft 40. More specifically, the crankshaft 40 is rotatably supported by the housing 22 via a sliding bearing as a radial bearing. Also, a sliding bearing as a radial bearing is interposed between the connecting rod 38, the piston 36, and the crankshaft 40.

[0015] One end of the crankshaft 40 airtightly penetrates the housing 22 and is connected to a drive source located outside the housing 22. When the crankshaft 40 rotates due to the power supplied by the drive source, the piston 36 reciprocates within the cylinder 32. This causes the intake stroke, compression stroke, and discharge stroke of the refrigerant gas G to be repeatedly performed in sequence.

[0016] The reciprocating compressor 1 is configured to supply lubricating oil to sliding parts such as radial bearings and pistons 36 during operation. Specifically, a lubricating oil storage chamber is formed at the bottom of the crank chamber 34 (in Figures 1 and 2, the stored lubricating oil is indicated by the symbol L). The reciprocating compressor 1 is equipped with an oil pump 42 that operates in conjunction with the crankshaft 40, and the lubricating oil drawn up from the oil storage chamber by the oil pump 42 is supplied to each sliding part through oil passages provided inside or outside the housing 22. Oil passages are also formed inside the crankshaft 40, for example, as shown by the dotted line in Figure 1. In this embodiment, oil filters 46 and 48 for purifying the lubricating oil are installed inside the oil storage chamber and outside the housing 22, respectively.

[0017] <2. Inflow of oil particles into the intake chamber 28> During operation of the reciprocating compressor 1 illustrated in Figure 1, refrigerant gas G leaks out from between the piston 36 and the inner wall surface of the cylinder 32 and flows into the crank chamber 34. When the pressure in the crank chamber 34 becomes higher than the pressure in the intake chamber 28 due to the inflow of refrigerant gas G, the refrigerant gas G in the crank chamber 34 flows into the intake chamber 28 through the oil return hole 39 (see Figure 2). Since this refrigerant gas G contains oil particles of lubricating oil floating in the crank chamber 34, lubricating oil flows into the intake chamber 28. This lubricating oil returns to the crank chamber 34 through the oil return hole 39 and flows into the oil storage chamber. In other words, the oil return hole 39 in the present invention, by having the hole diameter characteristics described later, has the role of returning lubricating oil remaining in the intake chamber 28 to the crank chamber 34, and also has the role of a pressure equalizing hole that reduces the pressure difference between the intake chamber 28 and the crank chamber 34. By eliminating the conventional pressure equalization hole, which is provided at the top of the partition wall 29 (the area indicated by the dashed line M in Figure 2) solely for the purpose of equalizing the pressure in both chambers, and by having the oil return hole 39 perform that function, the structure of the housing 22 can be simplified. Furthermore, it is preferable that the oil return hole 39 be provided in a portion of the partition wall 29 that is below the top. As a more specific example, the oil return hole 39 is located at the bottom of the suction chamber 28. This disclosure does not exclude embodiments in which the oil return hole is provided at the top of the partition wall 29, along with the oil return hole 39.

[0018] <3. Overview of the gas flow regulator 50> When the reciprocating compressor 1, illustrated in Figure 1, starts up, or when the evaporation pressure of the refrigerant gas G decreases due to a decrease in the heat load of the refrigeration cycle, or when the capacity control of the reciprocating compressor is increased due to an increase in the heat load of the refrigeration cycle, the pressure in the intake chamber 28 becomes lower than the previous state. In this case, the flow of refrigerant gas G from the crank chamber 34 to the intake chamber 28 becomes rapid, resulting in more fine particles of lubricating oil suspended in the crank chamber 34 flowing into the intake chamber 28 along with the refrigerant gas G than during normal operation. Furthermore, a rapid decrease in pressure in the crank chamber 34 can also cause oil foaming under specified conditions. In this case, the lubricating oil that has foamed up on the oil surface of the oil storage chamber becomes fine particles and is more easily scattered as the flow of refrigerant gas G increases, resulting in even more atomized lubricating oil flowing into the intake chamber 28 than under normal conditions. The inventors conceived the gas flow regulator 50 of this disclosure based on the idea that slowing the flow of refrigerant gas G from the crank chamber 34 to the intake chamber 28 in these cases would suppress oil leakage due to oil particles. The gas flow regulator 50 partially blocks the oil return hole 39 when the pressure in the crank chamber 34 becomes somewhat higher than the pressure in the intake chamber 28, thereby slowing the flow of refrigerant gas G from the crank chamber 34 to the intake chamber 28. The gas flow regulator 50 then opens the oil return hole 39 when the pressure difference between the crank chamber pressure and the intake chamber pressure falls below a specified value. The number of gas flow regulators 50 installed in the reciprocating compressor 1 may be one or two or more.

[0019] The following describes, in order, the gas flow regulator 50A according to the first embodiment, the gas flow regulator 50B according to the second embodiment, the gas flow regulator 50C according to the third embodiment, and the gas flow regulator 50D according to the fourth embodiment.

[0020] <4. Gas flow regulator 50A(50) according to the first embodiment> Figure 2 is a schematic diagram of the reciprocating compressor 1A(1) according to the first embodiment. Figure 3 is a schematic diagram of the gas flow regulator 50A(50) according to the first embodiment. Figure 4 is a schematic diagram showing the configuration of the leaf spring 90. Note that in Figure 2, some components of the reciprocating compressor 1 exemplified in Figure 1, such as the connecting rod 38 and the oil filter 46, are not shown.

[0021] As illustrated in Figure 2, the gas flow regulator 50A(50), a component of the reciprocating compressor 1A(1), is provided on the first chamber 61A(61) side of the partition wall 99A(99) that separates the first chamber 61A(61) and the second chamber 62A(62). In the first embodiment, the first chamber 61A is the crank chamber 34, the second chamber 62A is the intake chamber 28, and the partition wall 99A constitutes part of the partition wall 29.

[0022] As shown in Figures 3 and 4, the gas flow regulator 50A comprises a plurality of fastening members 98 and a leaf spring 90 attached to the partition wall 99A by the plurality of fastening members 98. The leaf spring 90 includes a mounting portion 91 attached to the partition wall 99A by a fastening member 98, which may be a screw, a curved portion 92 having one end connected to the mounting portion 91, and an opening / closing portion 93 extending from the other end of the curved portion 92 in a direction away from the mounting portion 91. The mounting portion 91 abuts against the wall surface on the first chamber 61A side that constitutes the partition wall 99A. The opening / closing portion 93 facing the oil return hole 39 has a spring hole 95 with a smaller diameter than the oil return hole 39.

[0023] Figure 5 is a schematic diagram showing the operating state of the gas flow regulator 50A according to the first embodiment. As the pressure in the intake chamber 28 decreases, the pressure difference between the first chamber 61A and the second chamber 62A increases, and the leaf spring 90 begins to elastically deform. The opening / closing part 93 gradually approaches the partition wall 99A and eventually contacts the partition wall 99A, blocking the oil return hole 39 from the first chamber 61A side. The refrigerant gas G containing oil particles in the first chamber 61A cannot reach the second chamber 62A unless it passes through the spring hole 95 and the oil return hole 39 in sequence. After a predetermined time has elapsed since the oil return hole 39 was blocked (for example, 30 minutes to 2 hours), the pressure in the first chamber 61A becomes sufficiently low, and the elastically deformed leaf spring 90 returns to its natural state (see Figure 3). As a result, the oil return hole 39 is opened.

[0024] With the above configuration, as the pressure in the intake chamber 28 decreases, the pressure difference between the first chamber 61A and the second chamber 62A increases, causing the leaf spring 90 to elastically deform and the oil return hole 39 to close. The refrigerant gas G in the crank chamber 34 cannot reach the intake chamber 28 without passing through the spring hole 95. Since the pressure loss in the flow of refrigerant gas G in the spring hole 95, which has a smaller diameter than the oil return hole 39, is large (i.e., the flow resistance in the spring hole 95 is large), the rapid flow of refrigerant gas G from the crank chamber 34 to the intake chamber 28 can be suppressed, and the rapid pressure reduction in the crank chamber 34 can be suppressed. As a result, oil leakage due to oil particles flowing out of the reciprocating compressor 1 can be suppressed. In addition, the leaf spring 90 according to other embodiments does not need to have a curved portion 92, in which case the opening / closing portion 93 may be connected to one end of the mounting portion 91. Even in this case, the advantage of suppressing oil leakage in the reciprocating compressor 1 can be obtained.

[0025] In one embodiment of the present disclosure, the spring hole 95 has an inner diameter of 1.4 mm or less. The spring hole 95 is preferably circular, but may also be polygonal. If the spring hole 95 is polygonal, the maximum inner diameter is 1.4 mm or less. With the above configuration, the flow of refrigerant gas G into the intake chamber 28 is further suppressed by having a spring hole 95 of 1.4 mm or less. This further suppresses oil leakage.

[0026] In one embodiment of the present disclosure, the spring hole 95 has an inner diameter of 0.6 mm or more. The spring hole 95 is preferably a circular hole, but may also be polygonal. If the spring hole 95 is polygonal, the maximum inner diameter is 0.6 mm or more. With the above configuration, when refrigerant gas G flows from the crank chamber 34 to the intake chamber 28, a certain amount of refrigerant gas G can be ensured to flow through the spring hole 95. This shortens the time required for the pressure in the crank chamber 34 to approach the pressure in the intake chamber 28.

[0027] In one embodiment of this disclosure, the inner diameter of the oil return hole 39 is 15 mm or more. The oil return hole 39 is, for example, circular in shape. With the above configuration, it is easier to ensure an inner diameter of the oil return hole 39 that is greater than or equal to the Taylor instability wavelength (Taylor critical wavelength) at the boundary between the refrigerant gas G and the lubricating oil, so that both the flow of refrigerant gas G toward the intake chamber 28 and the flow of lubricating oil toward the crank chamber 34 in the oil return hole 39 can occur simultaneously. Therefore, it is possible to suppress the problem of lubricating oil blocking the oil return hole 39 and preventing the flow of refrigerant gas G. Furthermore, because the inner diameter of the oil return hole 39 is 15 mm or more, when the gas flow regulator 50A does not block the oil return hole 39, the oil return hole 39 can fully function as a pressure equalization hole that equalizes the pressure in the intake chamber and the pressure in the crank chamber. Therefore, in this disclosure, it is not necessary to provide a pressure equalization hole at the top of the partition wall 29 as disclosed in Patent Document 1, and the structure of the partition wall 29 can be simplified. It should be noted that the pressure equalization hole is understood to be a hole through which refrigerant gas G containing oil particles can flow from the crank chamber 34 to the intake chamber 28, but lubricating oil cannot flow toward the crank chamber 34.

[0028] <5. Gas flow regulator 50B(50) according to the second embodiment> Figure 6 is a schematic diagram of the gas flow regulator 50B(50) according to the second embodiment. The gas flow regulator 50B(50), which is a component of the reciprocating compressor 1B(1), is installed in the partition wall 99B(99) separating the first chamber 61B(61) and the second chamber 62B(62). In the second embodiment, the first chamber 61B is the first space 11B(11), which will be described later and can communicate with the crank chamber 34, and the second chamber 62B is the intake chamber 28. In this example, the partition wall 99B also constitutes part of the partition wall 29.

[0029] The gas flow regulator 50B of the reciprocating compressor 1B includes a cover 70 in addition to the components of the gas flow regulator 50A. The cover 70 is attached to the outer surface of the partition wall 99B to accommodate a leaf spring 90. The inner space of the cover 70 is a first space 11B(11) that accommodates the leaf spring 90 attached to the outer surface of the partition wall 99B and is able to communicate with the crank chamber 34. The cover 70 includes an opening 74 that allows the first space 11B to communicate with the crank chamber 34, which is the outer space of the cover 70. In this paper, "able to communicate" is a concept that includes both constant communication between the two spaces and communication between the two spaces depending on the operating state of equipment such as valves (for example, if the two spaces become able to communicate as a valve moves from a closed state to an open state, then these two spaces are understood to be able to communicate). The opening 74 has a larger inner diameter than the oil return hole 39. More specifically, as an example, the opening 74 has an inner diameter that is 1.5 times or more and 2.0 times or less than that of the oil return hole 39. The number of openings 74 may be one or two or more.

[0030] Figure 6 shows the gas flow regulator 50B in operation. Due to the pressure difference between the first chamber 61B and the second chamber 62B, the leaf spring 90 elastically deforms, and when the opening / closing part 93 closes the oil return hole 39, the refrigerant gas G in the crank chamber 34 cannot reach the second chamber 62B without passing through the opening hole 74, the first chamber 61B, and the spring hole 95 in that order. The refrigerant gas G flowing near the spring hole 95 is accelerated by the throttling action of the spring hole 95 and is drawn into the spring hole 95. In this respect, with the above configuration, the flow of refrigerant gas G is slower in the opening hole 74, which is larger than the spring hole 95, so it becomes difficult for oil particles to reach the first chamber 61B (first space 11B) inside the cover 70. This suppresses the drawing of oil particles of lubricating oil floating in the crank chamber 34 into the spring hole 95 along with the refrigerant gas G. In this example, the flow of refrigerant gas G caused by the pressure difference between the crank chamber 34 and the intake chamber 28 can also be sufficiently suppressed by the pressure loss at the spring hole 95. This further suppresses oil leakage.

[0031] The cover 70 includes a cover body 72, which is a wall portion in which an opening 74 is provided. The cover body 72 is positioned to be aligned with the oil return hole 39 in the axial direction of the oil return hole 39 (the direction of the opening of the oil return hole 39). In other words, the opening 74 is positioned offset from the oil return hole 39 in the axial direction. With this configuration, the cover body 72 prevents the refrigerant gas G in the crank chamber 34 from moving toward the spring hole 95. This also suppresses oil particles mixed in with the refrigerant gas G from reaching the spring hole 95. Therefore, oil leakage can be further suppressed.

[0032] <6. Gas flow regulator 50C(50) according to the third embodiment> Figure 7 is a schematic diagram showing a part of the reciprocating compressor 1C(1) according to the third embodiment. Figure 8 is a schematic diagram of the gas flow regulator 50C(50) according to the third embodiment. The gas flow regulator 50C(50), which is a component of the reciprocating compressor 1C(1), is provided on the outer surface of the housing 22. The leaf spring 90 of the gas flow regulator 50C is provided on the partition wall 99C(99) separating the first chamber 61C(61) and the second chamber 62C(62). The first chamber 61C is the first space 11C(11), which will be described later and communicates with the crank chamber 34, and the second chamber 62C is the intake chamber 28. In this example, the partition wall 99C constitutes a part of the housing 22 and is a different wall from the partition wall 29.

[0033] The gas flow regulator 50C includes an outer cover 110 provided on the bulkhead 99C to accommodate a leaf spring 90 attached to the outer surface of the bulkhead 99C. The space in which the leaf spring 90 is housed by the outer cover 110 is a first space 11C(11) that can communicate with the crank chamber 34. The first space 11C is the space for housing the leaf spring 90 defined by the outer cover 110 and the bulkhead 99C. In this example, the first space 11C can communicate with the crank chamber 34 through a through hole 21 provided in the bulkhead 99C. The lower end of the inner circumferential surface of the bulkhead 99C that defines the through hole 21 is positioned at the same height as the lower end of the inner circumferential surface of the outer cover 110, or lower than the lower end of the inner circumferential surface of the outer cover 110. Furthermore, the partition wall 99C in this example separates the first space 11C not only from the crankcase 34 but also from the intake chamber 28, and an oil return hole 39 is provided in the partition wall 99C, configured to allow lubricating oil to flow from the intake chamber 28 towards the crankcase 34. The first space 11C can communicate with the intake chamber 28 through this oil return hole 39. The through hole 21 is larger than the oil return hole 39.

[0034] The oil return function of the reciprocating compressor 1C illustrated in Figure 8 is the same as that of the reciprocating compressor 1A illustrated in Figure 5. That is, when the pressure in the crank chamber 34 shown in Figure 8 is higher than the pressure in the intake chamber 28, the refrigerant gas G containing oil particles in the crank chamber 34 flows into the intake chamber 28 by passing through the through hole 21, the first space 11C, and the oil return hole 39 in that order. Because the through hole 21 is larger than the oil return hole 39, the flow velocity of the refrigerant gas G from the crank chamber 34 toward the first space 11C does not increase easily. Therefore, the amount of lubricating oil flowing into the intake chamber 28 can be reduced. The lubricating oil in the intake chamber 28 returns to the crankcase 34 by passing through the oil return hole 39, the first space 11C, and the through hole 21 in that order. Since the lower end of the inner circumferential surface of the partition wall 99C that defines the through hole 21 is positioned at the same height as, or lower than, the lower end of the inner circumferential surface of the outer cover 110, the lubricating oil can return to the crankcase 34 without accumulating in the outer cover 110.

[0035] Furthermore, the operating principle of the gas flow regulator 50C is the same as that of the gas flow regulator 50A. That is, as the pressure in the intake chamber 28 decreases, the pressure difference between the first chamber 61C (first space 11C) and the second chamber 62C (intake chamber 28) increases, and the leaf spring 90 undergoes elastic deformation. As a result, the opening / closing part 93 contacts the partition wall 99C and closes the oil return hole 39 from the first chamber 61C side. This prevents the refrigerant gas G containing oil particles in the first chamber 61C from reaching the crank chamber 34 without passing through the spring hole 95 and the oil return hole 39 in sequence, thus slowing the flow of refrigerant gas G from the first chamber 61C to the second chamber 62C. With the above configuration, the gas flow regulator 50C can be provided on the outside of the housing 22, which improves the design freedom of the shape or arrangement of the gas flow regulator 50C.

[0036] <6. Gas flow regulator 50D(50) according to the fourth embodiment> Figure 9 is a schematic diagram showing a reciprocating compressor 1D(1) according to the fourth embodiment. The gas flow regulator 50D(50), which is a component of the reciprocating compressor 1D(1), is equipped with a partition wall 99D(99), which separates the first chamber 61D(61) and the second chamber 62D(62). The first chamber 61D is a first space 11D(11) described later that can communicate with the crank chamber 34, and the second chamber 62D is a second space 12 described later that can communicate with the intake chamber 28.

[0037] The gas flow regulator 50D comprises a bulkhead cover 150, a first connecting pipe 131, and a second connecting pipe 132. The bulkhead cover 150 is provided to accommodate a leaf spring 90 attached to the bulkhead 99D, and in cooperation with the bulkhead 99D, defines a first space 11D that can communicate with the crank chamber 34. The first connecting pipe 131 is provided between the crank chamber 34 and the bulkhead 99D. Communication hole 94 It is a horizontal pipe connected to the intake chamber 28 and the partition wall 99D. Oil return hole 39 It is a horizontal pipe connected to bulkhead 99D. Communication hole 94 The first chamber 61D, which is the first space 11D, and the first connecting pipe 131 are connected, and the partition wall 99D Oil return hole 39 This allows the second chamber 62D, which is the second space 12, to communicate with the first space 11D (first chamber 61D). The lower end of the inner surface of the partition wall 99D that defines the communication hole 94 is positioned at the same height as the lower end of the inner surface of the partition wall cover 150, or lower than the lower end of the inner surface of the outer cover 110. Also, the communication hole 94 is larger than the oil return hole 39. Since both the first communication pipe 131 and the second communication pipe 132 are horizontal pipes, trapping (stagnation) of lubricating oil can be suppressed. Furthermore, the gas flow regulator 50D in this example includes a first valve 121 provided in the first connecting pipe 131 and a second valve 122 provided in the second connecting pipe 132. When both the first valve 121 and the second valve 122 are open, the crank chamber 34 and the intake chamber 28 are connected via the gas flow regulator 50D, and the gas flow regulator 50D becomes operational. In this example, ball valves (more preferably full-bore type ball valves) are used for both the first valve 121 and the second valve 122. This simplifies the internal structure of the first valve 121 and the second valve 122, thereby suppressing the trapping of lubricating oil.

[0038] The oil return function of the reciprocating compressor 1D is the same as that of the reciprocating compressor 1C, and the operating principle of the gas flow regulator 50D is the same as that of the gas flow regulator 50C, so a detailed explanation will be omitted. With the above configuration, the leaf spring 90 and the partition wall 99D can be placed away from the housing 22 in which the intake chamber 28 and crank chamber 34 are formed on the inside, thereby improving the design flexibility of the shape or placement of the gas flow regulator 50D.

[0039] Furthermore, the first connecting pipe 131 and the second connecting pipe 132 are not limited to being horizontal pipes. For example, if the first chamber 61D, which is the first space 11D, is positioned higher than the through hole 21 and lower than the oil return hole 39 formed in the housing 22, then even if the first connecting pipe 131 and the second connecting pipe 132 are bent, the lubricating oil can flow smoothly into the crankcase 34 by its own weight. The first valve 121 and the second valve 122 may be reduced-bore ball valves.

[0040] <7. Summary> The contents described in some of the embodiments above can be understood, for example, as follows:

[0041] 1) A gas flow regulator (50) according to one embodiment of the present disclosure is A gas flow regulator for a reciprocating compressor (1) having an intake chamber (28) and a crank chamber (34) located below the intake chamber, A leaf spring (90) is attached to a partition wall (99) separating a first chamber (61), which is either the crank chamber or a first space (11) that can communicate with the crank chamber, and a second chamber (62), which is either the intake chamber or a second space (12) that can communicate with the intake chamber, and is configured to close an oil return hole (39) provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber. The leaf spring has a spring hole (95) that is smaller in diameter than the oil return hole.

[0042] According to the configuration described in 1) above, as the pressure in the intake chamber decreases and the pressure difference between the first chamber and the second chamber increases, the leaf spring undergoes elastic deformation and the oil return hole is blocked. Refrigerant gas in the crankcase ( G The refrigerant gas cannot reach the intake chamber without passing through the spring hole. Since the pressure loss in the flow of refrigerant gas through the spring hole, which has a smaller diameter than the oil return hole, is large, the rapid flow of refrigerant gas from the crankcase to the intake chamber can be suppressed, and the rapid pressure reduction in the crankcase can be suppressed. This can suppress oil leakage caused by oil particles flowing out in the reciprocating compressor.

[0043] 2) In some embodiments, the gas flow regulator described in 1) above, The leaf spring is attached to the partition wall separating the first chamber, which is the crank chamber, and the second chamber, which is the intake chamber. The partition wall is provided with a cover (70) that includes an opening that allows the first space, which is the space for housing the leaf spring, to communicate with the crank chamber.

[0044] According to the configuration described in 2) above, the refrigerant gas containing oil particles cannot reach the spring hole without passing through the opening and the first space in sequence. Since the refrigerant gas flow is slow in the opening, it becomes difficult for the oil particles to reach the first space inside the cover. This further suppresses oil leakage.

[0045] 3) In some embodiments, the gas flow regulator described in 2) above, The cover includes a cover body (72) in which the opening hole is provided, The cover body is positioned so as to be aligned with the oil return hole in the axial direction of the oil return hole.

[0046] According to the configuration described in 3) above, the cover body prevents the refrigerant gas in the crankcase from moving towards the spring hole. This also prevents oil particles mixed in with the refrigerant gas from reaching the spring hole, thus further suppressing oil leakage.

[0047] 4) In some embodiments, the gas flow regulator described in 1) above, The partition wall constitutes part of the housing that accommodates the intake chamber and the crank chamber, and separates the first chamber, which is the first space, from the second chamber, which is the intake chamber. The gas flow regulator includes an outer cover (110) provided on the partition wall to house the leaf spring attached to the outer surface of the partition wall, The partition wall separates the first chamber, which is the first space defined by the partition wall and the outer cover, from the second chamber, which is the intake chamber.

[0048] According to the configuration described in 4) above, the gas flow regulator can be installed on the outside of the housing, thereby increasing the design flexibility regarding the shape or placement of the gas flow regulator.

[0049] 5) In some embodiments, the gas flow regulator described in 1) above, The partition wall is provided at a position away from the housing that houses the intake chamber and the crank chamber, A partition wall cover (150) is provided to accommodate the leaf spring attached to the partition wall and to cooperate with the partition wall to define the first space, A first connecting pipe (131) is connected to the crank chamber and the partition wall, A second connecting pipe (132) is connected to the intake chamber and the partition wall, and defines the second space on its inside, Equipped with, The partition wall includes an oil return hole that can communicate with the first space and the first connecting pipe, and a connecting hole (94) that can communicate with the second space, and separates the first chamber, which is the first space, from the second chamber, which is the second space.

[0050] According to the configuration in 5) above, the leaf spring and partition wall can be positioned away from the housing in which the intake chamber and crank chamber are formed on the inside, thereby improving the design flexibility, such as the shape or arrangement of the gas flow regulator.

[0051] 6) In some embodiments, a gas flow regulator according to any one of 1) to 5) above, The inner diameter of the oil return hole is 15 mm or more.

[0052] According to the configuration in 6) above, it becomes easier to secure an inner diameter of the oil return hole that is greater than or equal to the Taylor instability wavelength, so that both the flow of refrigerant gas toward the intake chamber and the flow of oil toward the crankcase can occur simultaneously in the oil return hole. Therefore, it is possible to suppress the problem of oil blocking the oil return hole and preventing refrigerant gas from flowing.

[0053] 7) A reciprocating compressor according to at least one embodiment of the present disclosure is Inhalation room and A crank chamber located below the intake chamber, A gas flow regulator for adjusting the flow of oil in the crankcase into the intake chamber, A partition wall separates a first chamber, which is either the crank chamber or a first space communicating with the crank chamber, from a second chamber, which is either the intake chamber or a second space communicating with the intake chamber. Equipped with, The aforementioned gas flow regulator is The leaf spring is attached to the partition wall and is configured to close the oil return hole provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber, The leaf spring has a spring hole that is smaller in diameter than the oil return hole.

[0054] According to the configuration in 7) above, a reciprocating compressor that can suppress oil leakage is realized for the same reasons as in 1) above.

[0055] 8) In some embodiments, a gas flow regulator according to any one of 1) to 7) above, The spring hole has an inner diameter of 1.4 mm or less.

[0056] According to the configuration described in 8) above, the spring hole being 1.4 mm or less further suppresses the flow of refrigerant gas into the intake chamber. This further suppresses oil leakage.

[0057] 9) In some embodiments, a gas flow regulator according to any one of 1) to 8) above, The spring hole has an inner diameter of 0.6 mm or more.

[0058] According to the configuration described in 9) above, a certain amount of refrigerant gas flow can be ensured when fluid flows from the crankcase to the intake chamber. This prevents the time required for the crankcase pressure to approach the intake chamber pressure from becoming too long. [Explanation of Symbols]

[0059] 1: Reciprocating compressor 11: 1st space 12:Second space 22: Housing 28: Suction chamber 34: Crank Room 39: Oil return hole 50: Gas flow regulator 61: First Chamber 62: Second Chamber 70: Cover 72: Cover body 74: Opening hole 90: Leaf spring 94:Communication hole 95: Spring hole 99: Bulkhead 110: Outer cover 131: 1st communication pipe 132:Second communication pipe 150: Bulkhead cover

Claims

1. A gas flow regulator for a reciprocating compressor having an intake chamber and a crank chamber located below the intake chamber, The device comprises a leaf spring attached to a partition wall separating a first chamber, which is either the crank chamber or a first space communicating with the crank chamber, and a second chamber, which is either the intake chamber or a second space communicating with the intake chamber, and configured to close an oil return hole provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber. The leaf spring has a spring hole that is smaller in diameter than the oil return hole. With the leaf spring blocking the oil return hole, the gas flowing from the first chamber to the second chamber is configured to pass sequentially through the spring hole and the oil return hole. Gas flow regulator.

2. The leaf spring is attached to the partition wall separating the first chamber, which is the crank chamber, and the second chamber, which is the intake chamber. The gas flow regulator according to claim 1, comprising a cover provided in the partition wall to accommodate the leaf spring, and including an opening that allows communication between the first space, which is a space for accommodating the leaf spring, and the crank chamber.

3. The cover includes a cover body in which the opening hole is provided, The cover body is positioned so as to be aligned with the oil return hole in the axial direction of the oil return hole. The gas flow regulator according to claim 2.

4. The partition wall constitutes part of the housing that accommodates the intake chamber and the crank chamber, and separates the first chamber, which is the first space, from the second chamber, which is the intake chamber. The gas flow regulator includes an outer cover provided on the partition wall to accommodate the leaf spring attached to the outer surface of the partition wall, The partition wall separates the first chamber, which is the first space defined by the partition wall and the outer cover, from the second chamber, which is the intake chamber. The gas flow regulator according to claim 1.

5. The partition wall is provided at a position away from the housing that houses the intake chamber and the crank chamber, A partition wall cover is provided to accommodate the leaf spring attached to the partition wall and to cooperate with the partition wall to define the first space, A first connecting pipe is connected to the crank chamber and the partition wall, A second communication pipe is connected to the intake chamber and the partition wall, and defines the second space on its inside, Equipped with, The partition wall includes a communication hole that can communicate with the first space and the first communication pipe, and an oil return hole that can communicate with the first space and the second space, separating the first chamber, which is the first space, and the second chamber, which is the second space. The gas flow regulator according to claim 1.

6. The inner diameter of the oil return hole is 15 mm or more. A gas flow regulator according to any one of claims 1 to 5.

7. Inhalation room and A crank chamber located below the intake chamber, A gas flow regulator for adjusting the flow of oil in the crankcase into the intake chamber, A partition wall separates a first chamber, which is either the crank chamber or a first space that can communicate with the crank chamber, from a second chamber, which is either the intake chamber or a second space that can communicate with the intake chamber. Equipped with, The aforementioned gas flow regulator is The partition wall includes a leaf spring that is attached to the partition wall and configured to close an oil return hole provided in the partition wall from the first chamber side by the pressure difference between the first chamber and the second chamber, The leaf spring has a spring hole that is smaller in diameter than the oil return hole. With the leaf spring blocking the oil return hole, the gas flowing from the first chamber to the second chamber is configured to pass sequentially through the spring hole and the oil return hole. Reciprocating compressor.

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