JP2022183232A - Rotary mechanism - Google Patents

Abstract

PROBLEM TO BE SOLVED: To provide a rotary machinery with a simple structure and a small space occupation and capable of efficiently controlling an oil circulation rate.

SOLUTION: A rotary mechanism according to the present invention, comprises: a housing 11; a rotary member 110; and a discharge member 130. An oil and gas mixture is contained in the housing 11. The rotary member 110 is provided in the housing 11 and is rotatable about a rotation axis to drive the oil and gas mixture to form a cyclone flow, whereby under a centrifugal force, an oil content in the oil and gas mixture is smaller as it approaches the rotary member 110. The discharge member 130 is provided on the housing 11 and extends radially inwardly from the housing 11 to a position where the oil content is equal to or less than a preset amount.

SELECTED DRAWING: Figure 1

COPYRIGHT: (C)2023,JPO&INPIT

Description

This disclosure is based on Chinese Patent Application No. 201710701301.0 entitled "ROTARY MACHINERY" filed on August 16, 2017 with the State Intellectual Property Office of China, the disclosure of which is incorporated herein by reference; No. 201721025170.0 claims priority.

The present disclosure relates to rotary machinery.

The content of this section merely provides background information related to the present disclosure and may not necessarily constitute prior art.

Compressors (eg, scroll compressors, rotor compressors, etc.) typically include a compression mechanism, a drive shaft, and a motor. The drive shaft is supported by bearings in the bearing housing and driven to rotate by the motor. Rotation of the drive shaft also drives moving components of the compression mechanism (eg, the orbiting scroll of a scroll compressor, the rotor of a rotor compressor, etc.) to compress the working fluid (eg, refrigerant). Each moving component of the compressor (e.g. orbiting scroll in a scroll compressor, rotor in a rotor compressor, bearings, etc.) should be lubricated with oil to maintain the stability and reliability of the moving components and overall compressor operation. It is necessary to be lubricated by A lubricating oil circulation system for the compressor is therefore an important part of the compressor.

When the compressor operates, the lubricating oil flows from an oil pool to each moving component of the compressor, under differential pressure or oil, e.g., to lubricate each moving component to maintain normal operation of each moving component. It is carried by the pumping mechanism and finally returns to the oil pool. In addition, during lubricating oil circulation, it may also remove impurities between the contact surfaces of the components to reduce wear, as well as heat generated by each component due to friction and electrical currents.

During lubricating oil circulation, some of the lubricating oil leaves the compressor with the working fluid. If the amount of lubricating oil coming out of the compressor is too large, after the compressor has been running for a period of time, the amount of lubricating oil in the oil pool will gradually decrease, that is, the oil level will drop and the moving components will work normally. There is insufficient lubricating oil in the compressor to maintain , thus resulting in erratic operation of the compressor. Therefore, maintaining the oil pool level in the compressor is very important. Moreover, on the other hand, the lubricating oil discharged from the compressor with the working fluid adheres, for example, to the condenser and evaporator coils, thereby affecting the heat exchange efficiency of the working fluid with ambient air. Therefore, it is necessary for the compressor to properly control the lubricating oil circulation rate (also called oil circulation rate). Here, the oil circulation rate can be understood as the (mass) ratio of the lubricating oil contained in the unit working fluid discharged from the compressor.

An oil-gas separation device may be placed in the compressor to control the oil circulation rate. However, since the internal space of the compressor casing is limited, it is desirable to provide a compressor that has a simple structure, occupies a small space, and can effectively control the oil circulation rate.

SUMMARY OF THE INVENTION An object of the present disclosure is to provide a rotary machine that has a simple structure, occupies a small space, and can effectively control the oil circulation rate.

Another object of the present disclosure is to provide a compressor that is simple to manufacture and assemble, is low in cost, and allows reasonable control of the oil circulation rate of the compressor.

According to one aspect of the present disclosure, a rotary mechanical device is provided that includes a casing, a rotating member, and an ejection member. The casing contains the oil-gas mixture inside. A rotating member is disposed within the casing and is rotatable about an axis of rotation to drive the oil-gas mixture to form a cyclonic flow, thereby, under centrifugal force, the oil in the oil-gas mixture. The content decreases as it approaches the rotating member. The discharge member is disposed in the casing and extends radially inward from the casing to a location where the oil content is below a predetermined content. A rotary machine according to the present disclosure may provide good control of the lubricating oil circulation rate.

In some embodiments, there is a predetermined distance between the end portion of the discharge member disposed inside the casing and the outer peripheral surface of the rotating member, and the ratio of the predetermined distance to the diameter of the circular discharge passage of the discharge member is: less than 1.5.

In some embodiments, the ratio of the predetermined distance to the diameter of the circular discharge passage of the discharge member is greater than 0.25.

In some embodiments, the ratio of predetermined distance to diameter of the circular discharge passage is between 0.4 and 0.5.

In some embodiments, the rotating member has a first axial end face and a second axial end face in the axial direction, and the ejection member has a first axial position and a second axial position. positioned between When the discharge member is in the first axial position, one radial side of the discharge passage of the discharge member is located axially outward of the first axial end surface and extends along one radial side of the discharge passage. The other radial side opposite the is aligned with the first axial end face. When the discharge member is in the second axial position, the other radial side of the discharge passage is located axially outside the second axial end surface and the one radial side of the discharge passage is located at the second axial position. 2 axial end faces.

In some examples, the ejection member is positioned to substantially align with the axially central portion of the rotating member.

In some embodiments, the end portion of the ejection member adjacent the rotating member extends linearly in a horizontal direction perpendicular to the axis of rotation, and the end surface of the end portion faces the outer peripheral surface of the rotating member. Oriented diagonally.

In some embodiments, the end portion of the ejection member adjacent the rotating member is bent in a circumferential direction of the rotating member and/or in a vertical direction parallel to the axis of rotation.

In some embodiments, the discharge opening of the discharge member is oriented to face downstream in the direction of rotation of the rotating member, and the oil-gas mixture in the casing enters the discharge member through the discharge opening. .

In some embodiments, the rotating member has a first axial end face and a second axial end face in the axial direction, and the ejection member is located at the first axial end face or the second axial end face. An end portion of the discharge member positioned axially outwardly and located within the casing faces inwardly so as to be flush with the outer peripheral surface of the rotating member or radially within the outer peripheral surface of the rotating member. extend towards.

In some embodiments, the rotating member is in the form of a cam, eccentric or counterweight and the ejection member is in the form of an ejection pipe or passageway.

In some examples, the rotary mechanical device further includes a compression mechanism, a drive shaft, and a motor. A compression mechanism is located within the casing and is configured to compress the working fluid. A drive shaft is adapted to drive the compression mechanism. The motor includes a stator and a rotor rotatable relative to the stator and is configured to drive the drive shaft to rotate. The rotating member is arranged on the drive shaft or arranged on the rotor.

In some examples, the rotating member is located between the compression mechanism and the motor or between the motor and the oil sump.

In some examples, the rotary machine is a high side scroll compressor.

In the above construction, the rotating member in the rotating mechanical device can drive the oil-gas mixture around it to form a cyclonic flow when the rotating member rotates, so that the lubricating oil increases the lubricating oil circulation rate. For better control, the oil-gas mixture can be separated from the oil-gas mixture under centrifugal force before it exits the compressor. On the one hand, the oil level of the oil pool in the compressor can be maintained at a desired level. On the other hand, the amount of lubricating oil leaving the compressor and entering the compressor system may be reduced, for example, the amount of lubricating oil entering the heat exchanger may be reduced, thereby improving the overall operation of the compressor system. Improve efficiency.

The features and advantages of one or more embodiments of the disclosure may become more readily apparent from the following description, taken in conjunction with the accompanying drawings.

1 is a longitudinal cross-sectional view of a compressor including an oil-gas separation device according to embodiments of the disclosure; FIG. Figure 2 is a schematic cross-sectional view of an oil-gas separation device of the compressor of Figure 1; 2 is a schematic view of the oil-gas separation device of FIG. 1 showing different radial positions of the discharge pipe relative to the counterweight; FIG. 2 is a schematic diagram of the oil-gas separation device of FIG. 1 showing different axial positions of the discharge pipe relative to the counterweight; FIG. FIG. 2 is a schematic diagram of a compressor with oil-gas separation devices located at different positions; FIG. 2 is a schematic diagram of a compressor with oil-gas separation devices located at different positions; Fig. 3 is a graph showing the distance between the discharge pipe and the counterweight and the circulation rate; FIG. 4 is a cross-sectional view showing the oil-gas distribution of an oil-gas separation device according to the present disclosure; FIG. 4 is a cross-sectional view showing the oil-gas distribution of an oil-gas separation device in a comparative example; FIG. 3 is a schematic diagram similar to FIG. 2 showing one modification of the discharge pipe; FIG. 4 is a schematic longitudinal section through the oil-gas separation device of the compressor showing another modification of the discharge pipe;

The following description of preferred embodiments is merely exemplary and is in no way intended to limit the disclosure and its application or use. Like reference numerals are used throughout the drawings to refer to like components, and descriptions of the structures of like components will not be repeated.

For ease of description, when a particular component can rotate about an axis of rotation, "longitudinal" or "axial" references to components herein refer to directions parallel to the axis of rotation. and "radial" as referred to herein for a component refers to the direction perpendicular to the axis of rotation. The terms "first," "second," and other terms referred to herein are used merely to distinguish different components and are not used to indicate order or other meaning. .

In the following, an oil-gas separation device according to the present disclosure and a compressor including this oil-gas separation device will be described with reference to the accompanying drawings. In the drawing a high side vertical scroll compressor is shown. However, it should be understood that the present disclosure is also applicable to other types of compressors such as horizontal scroll compressors, rotor compressors, and piston compressors.

Referring to FIG. 1, the compressor 10 includes a casing 11 and includes a compression mechanism 12 disposed within the casing 11 , a motor 13 and a drive shaft (also referred to as a rotating shaft or crankshaft) 14 .

The motor 13 includes a stator 13 b fixed to the casing 11 and a rotor 13 a positioned inside the stator 13 b and fixed to the drive shaft 14 . When the motor 13 is started, the rotor 13a rotates, driving the drive shaft 14 to rotate therewith.

Drive shaft 14 is attached to compression mechanism 12 so as to drive compression mechanism 12 to compress a working fluid (usually a gas) as drive shaft 14 rotates. In the scroll compressor 10 illustrated in the drawings, an eccentric crank pin 14b of the drive shaft 14 fits into an orbiting scroll 12b of the compression mechanism 12 to drive the orbiting scroll 12b into rotation.

Compressor 10 further includes a main bearing housing 15 secured to casing 11 . Main bearing housing 15 rotatably supports drive shaft 14 via main bearing 15a and supports compression mechanism 12, particularly orbiting scroll component 12b.

Compression mechanism 12 includes a non-orbiting orbiting scroll component 12a fixed to casing 11 or main bearing housing 15 and an orbiting orbiting scroll component 12b movable relative to non-orbiting orbiting scroll component 12a. Driven by the drive shaft 14, the orbiting scroll component 12b orbits relative to the non-orbiting scroll component 12a (i.e., the central axis of the orbiting scroll component is the same as the non-orbiting scroll component). It moves about a central axis, but the orbiting scroll component itself does not rotate about its own central axis). A series of compression chambers whose volume gradually decreases from radially outward to radially inward are formed between the helical vanes of the non-orbiting orbiting scroll component 12a and the orbiting orbiting scroll component 12b. be done. The working fluid is compressed in these compression chambers and then discharged through the discharge holes 17 of the compression mechanism 12 . The discharge hole 17 of the compression mechanism 12 is generally located approximately centrally in the end plate of the non-orbiting scroll component 12a.

During operation of a scroll compressor, the centrifugal force or torque produced by the rotation of the eccentric component causes the compressor to vibrate. Generally, a counterweight is placed on the rotating component to provide an opposing centrifugal force or torque to offset the imbalance created by the eccentric component. In the compressor 10 illustrated in FIG. 1, a counterweight 110 is fixed to the outer peripheral surface of the drive shaft 14 and adjacent the main bearing housing 15, and a counterweight 210 is mounted on the rotor 13a of the motor 13 facing the compression mechanism 12. Arranged on the end face, the counterweight 310 is arranged on the end face of the rotor 13 a of the motor 13 facing away from the compression mechanism 12 . Although the compressor in the drawings includes three counterweights, it should be understood that the number of counterweights can vary depending on the requirements of a particular application.

In the compressor example shown in FIG. 1, an oil sump 20 for storing lubricating oil is arranged at the bottom of the compressor casing 11 . The drive shaft 14 may be formed therein with a passageway 14 a extending substantially along the axial direction of the drive shaft 14 . The lubricating oil in the oil sump 20 is supplied through this passage 14a to the bearings of the compressor, the bearing surfaces of the main bearing housing 15 and the orbiting scroll component 12b, the compression mechanism and the like. After lubricating the various components of the compressor, the lubricating oil returns to the oil sump 20 .

As illustrated in FIG. 1, compressor 10 is a high side scroll compressor. A discharge pipe (discharge member) 130 is arranged in the casing 11 . The low pressure working fluid is fed directly into the suction chamber or low pressure chamber of the compression mechanism 12 through the inlet pipe (not shown) and suction holes (not shown) of the compression mechanism and then compressed and compressed into the compression mechanism 12 . It is discharged from the discharge hole 17 into the space enclosed by the casing 11 of the compressor. In the example shown, a discharge pipe 130 is hermetically installed within the casing 11 for discharging the compressed gas out of the compressor 10 . During operation of the compressor, the working fluid discharged through the discharge hole 17 is mixed with lubricating oil, which is supplied through the passage 14a of the drive shaft 14, and the orbiting scroll component 12b, the rotor 13a of the motor 13, etc. The motion distributes the space within the compressor casing 11 in the form of an oil mist. Therefore, the high pressure working fluid to be discharged out of the compressor through the discharge pipe 130 often contains lubricating oil, and therefore the amount of lubricating oil in the working fluid discharged out of the compressor through the discharge pipe 130 is and thereby control the overall compressor oil circulation rate (OCR).

An oil-gas separation device may be placed in the compressor 10 to better control the oil circulation rate (OCR) of the compressor. However, additional oil-gas separation devices require specific space and complicate the manufacturing and assembly process. Especially when the internal space of the compressor is limited, it is not suitable to additionally install an oil-gas separation device.

In order to overcome the above problems, the inventors of the present disclosure use the members already present in the compressor, and only by rationally configuring the relative positional relationship between the members, the centrifugal flow of lubricating oil from the high pressure working fluid. A solution that can be separated by force to discharge working fluid with reduced content of lubricating oil or even working fluid without lubricating oil, thereby rationally controlling the oil circulation rate (OCR) of the compressor. devised a strategy. Such a solution can significantly reduce the number of parts, save installation space, and simplify the assembly process, thereby greatly reducing costs.

In the following, an oil-gas separation device according to embodiments of the present disclosure will be described with reference to FIGS. 1 and 2. FIG. As illustrated in the drawings, the oil-gas separation device includes a counterweight 110 and an exhaust pipe 130. As shown in FIG. A counterweight 110 is fixed to the outer peripheral surface of the drive shaft 14 and can rotate with the drive shaft 14 . In this example, the axis of rotation of counterweight 110 is also the axis of rotation of drive shaft 14 , ie, the central longitudinal axis of drive shaft 14 . The discharge pipe 130 is located radially outside the counterweight 110 and is hermetically fixed to the casing 11 .

The counterweight 110 has an outer peripheral surface 111 adjacent to and facing the discharge pipe 130 and first and second axial end surfaces 115 and 117 in opposite directions. 1, 2 and 3, the counterweight has a radially outwardly projecting radial projection 112 and an axial projection 114 extending axially from a second axial end face 117. can have It should be understood that the construction of the counterweight (particularly the location, size, number of protrusions) may vary depending on the particular application. For example, the counterweight may have only one of the radial projection and the axial projection. Additionally or alternatively, the counterweight may have an axial projection extending axially from the first axial end face.

As the counterweight 110 rotates with the drive shaft 14, the radial projections 112 and axial projections 114 of the counterweight 110 may agitate the oil-gas mixture around them that is discharged from the discharge holes 17; The oil-gas mixture around them may be caused to form cyclonic flows. Under centrifugal force, the lubricating oil in the oil-gas mixture is discharged radially outward into the casing 11, flows down along the casing 11, and returns into the oil sump 20 by gravity. In this way, the oil-gas mixture near the counterweight 110 has a low lubricating oil content and the oil-gas mixture near the casing 11 has a high lubricating oil content. The content of lubricating oil in the oil-gas mixture increases in the direction from counterweight 110 to casing 11 . The content of lubricating oil in the oil-gas mixture radially inside the cyclonic flow is less than the content of lubricating oil in the oil-gas mixture radially outside the cyclonic flow. Therefore, the inventors prefer to position the end portion of the discharge pipe provided inside the casing within the area of the cyclonic flow generated by the rotation of the counterweight, in particular within the radially inner side of the cyclonic flow. suggest. The desired content of lubricating oil in the oil-gas mixture to be discharged can be predetermined according to the desired oil circulation rate. As such, the location of the discharge pipe can be determined according to a predetermined desired content (also referred to as "predetermined content"). That is, the discharge pipe may extend radially inward from the casing to a position where the content of lubricating oil in the oil-gas mixture is below a predetermined content.

The inventive concept of the present disclosure is that the cyclonic flow generated by the rotation of the counterweight 110 creates a gradient change in the lubricating oil content between the counterweight 110 and the casing 11, and the discharge pipe 130 and the counterweight. It should be understood that the relative positional relationship between 110 is based on the principle that it is determined to obtain the desired reduced oil circulation rate. In some conventional compressors, due to installation requirements, a length of discharge pipe may extend into the compressor casing. In this case, the length of the discharge pipe extension need only meet the installation requirements, so the end of the discharge pipe extension tends to be closer to the compressor casing. Additionally, in some conventional compressors, the lubricating oil flows along the inside surface of the compressor casing, so the length of the discharge pipe is - can be extended into the casing; However, setting the length of the discharge pipe extension in a conventional compressor has nothing to do with the rotation of the counterweight, the cyclonic flow generated by the rotation of the counterweight, and so on.

In one embodiment, between the casing 11 and the counterweight 110, the exhaust pipe 130 may be positioned closer to the counterweight 110, according to the inventive concepts of the present disclosure. Preferably, a discharge pipe 130 is positioned adjacent to the counterweight 110 for discharging working fluid with a reduced content of lubricating oil, or even working fluid without lubricating oil, as desired. , that is, positioned at a predetermined distance from the outer peripheral surface of the counterweight 110 .

2 and 3, the discharge pipe 130 is a circular tubular member and has a circular discharge passage 133. As shown in FIG. Discharge pipe 130 also has an end face 131 adjacent counterweight 110 . In other words, the end face 131 of the discharge pipe 130 located inside the casing extends inwardly from the wall of the casing to the vicinity of the counterweight 110 . A distance L exists between the end surface 131 of the discharge pipe 130 and the outer peripheral surface 111 of the counterweight 110 . Distance L may be able to both facilitate the discharge of working fluid through discharge pipe 130 and ensure that the discharged working fluid contains a lower content of lubricating oil. desirable. The distance L depends on operating conditions such as the rotational speed of the counterweight 110, the ambient pressure, the distance from the counterweight 110 to the casing 11, the content of lubricating oil in the working fluid discharged through the discharge hole 17 and the discharge pipe. It may be determined according to the desired content of lubricating oil in the working fluid to be discharged via 130, or the like. The distance L may be predetermined or may vary depending on the operating conditions of the compressor. Preferably, the end surface 131 of the discharge pipe 130 is as close as possible to the outer peripheral surface 111 of the counterweight 110 in order to provide a better oil-gas separation effect, and the end surface 131 of the discharge pipe 130 and the counterweight 110 It is also desirable that the distance between the outer peripheral surface 111 of the discharge pipe 130 should not be so small as to disadvantageously reduce the flow area of the discharge pipe 130 .

"Lower content lubricating oil" or "reduced content lubricating oil" or the like referred to herein means that the content of lubricating oil in the working fluid discharged via discharge pipe 130 is・It means that the content of lubricating oil in the working fluid in the casing 11 is less than the appropriate range of the lubricating oil circulation rate (OCR). For convenience of explanation, the "working fluid in the compressor casing" is referred to herein as the "working fluid before separation" or "oil-gas mixture" and is referred to as "discharge via discharge pipe 130. The "separated working fluid" is referred to as the "separated working fluid".

In the example of FIG. 3, assuming the diameter of circular discharge passage 133 is D, the ratio L/D of distance L to diameter D may be less than about 1.5. In some instances, the ratio L/D of distance L to diameter D can be greater than about 0.25. In some instances, the ratio L/D of distance L to diameter D is between about 0.25 and 1.25, between about 0.4 and 1, between about 0.4 and 0.75, preferably , may be between about 0.4 and 0.5. More preferably, the ratio of distance L to diameter D may be about 0.5. Referring to FIG. 7, there is shown a graph showing the distance between the discharge pipe and the counterweight versus the circulation rate when the compressor is operated at 5400 RPM (revolutions per minute). In FIG. 7, the horizontal axis represents the radial distance L between the end face of the discharge pipe and the outermost peripheral surface of the counterweight, and D represents the inner diameter of the discharge pipe. The vertical axis represents the oil circulation rate OCR of the compressor. As shown in FIG. 7, when L is about 1/2D, the compressor has the lowest oil circulation rate, which is about 1.08%. In prior art compressors, the oil circulation rate exceeds 5% when the compressor operates at 5400 RPM. In contrast, in the present disclosure, by locating the discharge pipe close to the counterweight, i.e., by setting the distance between the discharge pipe and the counterweight within a certain range, the oil circulation rate of the compressor can be significantly reduced, which achieves a significantly unexpected technical effect.

A conventional compressor and a compressor according to the present disclosure were tested by the inventors and the test results are listed in the table below. Tests were conducted under different operating conditions (different counterweight rotation speeds) for a set of conventional compressors (C1) and three sets of compressors of the present disclosure (T1, T2 and T3), and the test , the ratio of distance L to diameter D in the disclosed compressor is 0.4. The test results in the table are the content of lubricating oil in the separated working fluid. In a conventional compressor C1, the discharge pipe extends into the compressor casing merely for assembly convenience, but is far away from the counterweight, i.e. the distance between the discharge pipe and the counterweight is much larger than the inner diameter of the discharge pipe.

From the above tests and the test results in the table, it can be seen that the content of lubricating oil in the working fluid discharged from the compressor according to the present disclosure is significantly lower than the content of lubricating oil in the working fluid discharged from the conventional compressor. . Test results show that the liquid-gas separation device of the present disclosure can effectively separate lubricating oil from an oil-gas mixture. Accordingly, the compressor of the present disclosure significantly reduces the lubricating oil circulation rate (OCR). Such results could not have been expected from conventional compressors in the art prior to the invention.

Reference may also be made to Figures 8a and 8b. FIG. 8a is a cross-sectional view showing the oil-gas distribution of an oil-gas separation device according to the present disclosure, and FIG. 8b is a cross-sectional view showing the oil-gas distribution of an oil-gas separation device in a comparative example. As can be seen from FIG. 8b, there is a region with a higher lubricating oil content near the outer peripheral surface of the counterweight, and also a region with a higher lubricating oil content near the compressor casing, and the discharge The working fluid discharged from the pipe has a higher content of lubricating oil. By contrast, in FIG. 8a the regions with higher lubricating oil content are concentrated near the casing. Therefore, the working fluid discharged from the discharge pipe adjacent to the counterweight contains less lubricating oil, thereby reducing the oil circulation rate of the compressor.

In the compressor of the present disclosure, the counterweight is used as an active rotating member, and as it rotates, the oil-gas mixture around it is forced to form a cyclonic flow, thereby creating a greater Lubricating oil is discharged radially outward due to its specific gravity. Therefore, the working fluid near the counterweight has less lubricating oil in it and is easily discharged from the discharge pipe located near the counterweight.

In another embodiment, the end surface 131 of the discharge pipe 130 may face the counterweight 110 not parallel to the outer peripheral surface 111 of the counterweight 110 in the direction of the rotation axis of the counterweight 110, and the outer peripheral surface of the counterweight 110 It is oblique to 111 . In an alternative embodiment, the discharge opening of the discharge pipe 130 may be oriented to face downstream in the direction of rotation of the counterweight, and the oil-gas mixture inside the compressor casing is discharged through the discharge opening. It enters the pipe and is discharged from the compressor via the discharge pipe. By doing so, the amount of lubricating oil entering the discharge pipe 130 can be reduced and a better oil-gas separation effect can be achieved.

In some instances, the discharge pipe 130 may extend straight from the compressor casing in a horizontal direction perpendicular to the direction of rotation of the counterweight 110 . The end face 131 of the discharge pipe 130 is directed toward the outer peripheral surface 111 of the counterweight 110 and is oblique to the outer peripheral surface 111 of the counterweight 110 . In this case, the angle between the end face 131 of the discharge pipe 130 and the central longitudinal axis of the discharge pipe 130 is greater than 0 degrees but less than 90 degrees.

In other examples, the end portion of the discharge pipe 130 adjacent the counterweight 110 may be bent in the circumferential direction of the counterweight 110 and/or in the vertical direction parallel to the counterweight 110 axis of rotation. That is, the discharge pipe 130 may include a bent end portion located within the casing. The bent end portion may be a curved arc or may be bent at an angle.

As illustrated in FIG. 9, the bent end portion 230 of the discharge pipe 130 is bent in the circumferential direction of the counterweight 110 . In one example, the discharge opening at the end face 231 of the bent end portion 230 may face downstream in the direction of rotation of the counterweight 110 . Therefore, a better oil-gas separation effect can be achieved.

As illustrated in FIG. 10, the bent end portion 330 of the discharge pipe 130 is bent in a vertical direction parallel to the axis of rotation of the counterweight 110 . In the example shown, the end face 331 of the bent end portion 330 can be oriented downward. In alternative instances, the end face 331 of the bent end portion 330 may be oriented downwards or any other shape capable of reducing the amount of lubricating oil entering the discharge pipe. It may be oriented in any suitable direction.

In the compressor axial direction shown, the discharge pipe 130 may be positioned within the cyclonic flow created by the rotation of the counterweight 110 . In the example shown in FIG. 4, the discharge pipe 130 may be positioned between a first axial position P1 and a second axial position P2. At the first axial position P 1 , the discharge pipe 130 is axially outboard of and substantially aligned with the first axial end face 115 of the counterweight 110 . In other words, at the first axial position P1, one radial side portion of the discharge passage 133 of the discharge pipe 130 is located axially outside the first axial end face 115 and is located at one side of the discharge passage 133. The other radial side opposite the radial side is substantially aligned with the first axial end face 115 . According to the orientation in FIG. 4, in the first axial position P1, the discharge pipe 130 lies axially below the first axial end face 115 of the counterweight 110 and axially of the discharge passage of the discharge pipe 130. is substantially aligned with the first axial end face 115 . At the second axial position P 2 , the discharge pipe 130 is axially outward of and substantially aligned with the second axial end face 117 of the counterweight 110 . In other words, at the second axial position P2, the other radial side portion of the discharge passage of the discharge pipe 130 is located axially outside of the second axial end surface 117, and is aligned with the one side of the discharge passage. The radial side is substantially aligned with the second axial end face 117 . According to the orientation in FIG. 4, in the second axial position P2, the discharge pipe 130 lies axially above the second axial end face 117 of the counterweight 110 and axially of the discharge passage of the discharge pipe 130. is substantially aligned with the second axial end face 117 .

According to the principles of the present disclosure, the discharge pipe 130 is axially outward of the first axial position P1 or axially outward of the second axial position P2 (i.e., more than the first axial position P1). or above the second axial position P2) and radially inward, e.g. flush with the outer peripheral surface 111 of the counterweight 110, or It may also extend further radially inward of the outer peripheral surface 111 of 110 . Due to the cyclonic flow created by the rotation of the counterweight 110, the working fluid discharged from the discharge pipe 130 may still maintain a lower oil circulation rate (OCR).

In the embodiment shown in FIGS. 1-4, counterweight 110 is positioned on the outer circumference of drive shaft 14 . However, it should be understood that the oil-gas separation device may include a counterweight and discharge pipe located on any other suitable rotating member. For example, as shown in Figure 5, the oil-gas separation device may include a counterweight 210 positioned on the end face 1301 of the rotor 13a of the motor 13 facing the compression mechanism. Referring to FIG. 6, the oil-gas separation device may include a counterweight 310 positioned on the end face 1302 of the rotor 13a of the motor 13 facing away from the compression mechanism. The mutual positional relationship and dimensional relationship between the discharge pipe 130 and the counterweight can be appropriately set with reference to the above description.

In the embodiment shown in FIGS. 1-4, the oil-gas separation device is arranged between the main bearing housing 15 and the motor 13 . However, it should be understood that the oil-gas separation device may be located at any suitable location within the interior space defined by compressor casing 11 . For example, as shown in FIG. 6, an oil-gas separation device may be located between motor 13 and oil sump 20 .

It will be appreciated that the counterweight may have any suitable construction so long as it can rotate and cause the oil-gas mixture around it to form a cyclonic flow. For example, the counterweight may have a constant or variable radial dimension and/or may have a constant or variable axial dimension. The counterweight may have a cylindrical outer surface, a tapered outer surface, or any other outer surface having a suitable shape capable of achieving the above effects. Depending on the particular application, the counterweights shown in the drawings may be replaced by cams, eccentrics, or any other suitable member capable of achieving the above effects.

Similarly, the discharge pipes may have any suitable structure and/or be provided in any suitable number as long as they can facilitate the discharge of the working fluid. For example, the discharge pipe may include an open end portion. The discharge pipe may include an end portion oriented obliquely with respect to the outer peripheral surface of the counterweight. For example, the end portion of the discharge pipe adjacent to the counterweight is slanted downward, which may facilitate the outflow of lubricating oil on the inner wall of the discharge pipe. Although the compressor in the drawings includes one discharge pipe, the number of discharge pipes may be multiple. Depending on the particular application, the discharge pipes shown in the drawings can also be replaced by discharge passages arranged in a fixed structure.

Although several embodiments and variations of the disclosure have been described in detail, the disclosure is not limited to the embodiments and variations described above and shown in the drawings, but various other possible variations. It should be understood by those skilled in the art that variations and combinations may be included. For example, the oil-gas separation device may not have a bottom portion, so lubricating oil can drop directly into the oil sump along the wall. Other variations and modifications can be implemented by those skilled in the art without departing from the spirit and scope of this disclosure. All variations and modifications are within the scope of this disclosure. Moreover, all elements described in this specification may be replaced by other technically equivalent elements.

Claims (12)

a casing containing an oil-gas mixture;
A rotating member (110) disposed within said casing and rotatable about an axis of rotation to drive said oil-gas mixture to form a cyclonic flow, whereby under centrifugal force, said a rotating member (110), wherein the oil content of the oil-gas mixture decreases toward the rotating member;
a discharge member (130) configured to discharge said oil-gas mixture of said casing and arranged in said casing, from said casing to a position where said oil content is below a predetermined content; a radially inwardly extending ejection member (130), comprising:
Said rotating member has a first axial end face (115) and a second axial end face (117) in the direction of said axis of rotation, said ejection member having a first axial position (P1) and a positioned between a second axial position (P2) and when said ejection member is in said first axial position (P1), one radial side of said ejection passage of said ejection member: a radial side of the discharge passage located axially outwardly of the first axial end face and opposite the one radial side of the discharge passage aligned with the first axial end face; Further, when the discharge member is at the second axial position (P2), the other radial side portion of the discharge passage is positioned axially outside of the second axial end surface, A rotary mechanical device, wherein said one radial side of the passage is aligned with said second axial end face. A predetermined horizontal distance (L) perpendicular to the rotation axis exists between an end portion of the ejection member located inside the casing and the outer peripheral surface of the rotary member, and the ejection member (130) A rotary machine according to claim 1, wherein the ratio of the predetermined distance (L) to the diameter (D) of the circular discharge passage (133) is less than 1.5. A rotary machine according to claim 2, wherein said ratio of said predetermined distance (L) to said diameter (D) of said circular discharge passage (133) of said discharge member (130) is greater than 0.25. 4. The rotary machine of claim 3, wherein said ratio of said predetermined distance (L) to said diameter (D) of said circular discharge passage is between 0.4 and 0.5. The rotating member has a protrusion projecting radially outward or a protrusion extending axially from an axial end face of the rotating member, and the ejecting member is attached to the rotating member on which the protrusion is arranged. 2. The rotary mechanical device of claim 1, positioned to substantially align with the axial center portion of the portion. An end portion of the discharging member adjacent to the rotating member extends linearly in a horizontal direction perpendicular to the rotating shaft, and an end surface of the end portion extends obliquely to the outer peripheral surface of the rotating member. A rotary mechanical device according to claim 1, attached. 2. The rotary machine of claim 1, wherein an end portion of said ejector member adjacent said rotating member is bent in a circumferential direction of said rotating member and/or in a vertical direction parallel to said axis of rotation. The discharge opening of the discharge member is oriented to face downstream in the direction of rotation of the rotating member, and the oil-gas mixture in the casing enters the discharge member through the discharge opening. Item 1. The rotary machine device according to item 1. 2. The rotary mechanical device of claim 1, wherein the rotating member is in the form of an eccentric or counterweight and the ejection member is in the form of an ejection pipe or passageway. a compression mechanism (12) located within the casing and configured to compress a working fluid;
a drive shaft (14) adapted to drive said compression mechanism;
a motor (13) having a stator and a rotor rotatable relative to the stator, the motor (13) being configured to drive the drive shaft to rotate;
10. A rotary machine according to any preceding claim, wherein the rotating member is arranged on the drive shaft or arranged on the rotor. 11. The rotary machine device of claim 10, wherein the rotating member is positioned between the compression mechanism and the motor or between the motor and an oil sump. 11. The rotary machine of claim 10, wherein said rotary machine is a high side scroll compressor.

Images