CN109404289B

CN109404289B - Rotary machine

Info

Publication number: CN109404289B
Application number: CN201710701301.0A
Authority: CN
Inventors: 赵跟辉; 王石; 周启明; 毛安兵
Original assignee: Gulun Environmental Technology Suzhou Co ltd
Current assignee: Gulun Environmental Technology Suzhou Co ltd
Priority date: 2017-08-16
Filing date: 2017-08-16
Publication date: 2024-05-14
Anticipated expiration: 2037-08-16
Also published as: CN109404289A

Abstract

The present invention relates to a rotary machine including a housing, a rotary member, and a discharge member. The housing contains an oil-gas mixture therein. The rotating member is disposed within the housing and is rotatable about an axis of rotation to cause the mixture of oil and gas to form a cyclone flow whereby the oil content of the mixture of oil and gas under centrifugal force decreases as the rotating member is positioned closer. The discharge member is provided on the housing and extends radially inward from the housing to a position where the content of the oil is equal to or less than a predetermined content. The rotary machine according to the present invention can control the circulation rate of lubricating oil well.

Description

Rotary machine

Technical Field

The present invention relates to a rotary machine.

Background

The statements in this section merely provide background information related to the present disclosure and may not constitute prior art.

Compressors (e.g., scroll compressors, rotor compressors, etc.) typically include a compression mechanism, a drive shaft, and a motor. The drive shaft is supported by bearings within the bearing housing and is driven to rotate by the motor. The rotation of the drive shaft in turn moves movable components of the compression mechanism (e.g., the orbiting scroll of the scroll compressor, the rotor of the rotor compressor, etc.) to compress a working fluid (e.g., refrigerant). Each movable component of the compressor (e.g., the orbiting scroll of the scroll compressor, the rotor of the rotor compressor, bearings, etc.) requires lubrication with a lubricating oil to maintain the operational stability and reliability of each movable component as well as the overall compressor. Therefore, the lubrication oil circulation system of the compressor is an important component of the compressor.

During operation of the compressor, lubricating oil is delivered from the sump to the various movable components of the compressor, for example under the influence of a pressure differential or under the influence of an oil pumping mechanism, in order to lubricate the various components in order to maintain the normal operation of the movable components, and finally also to return to the sump. In addition, during the circulation of the lubricating oil, it can also carry away impurities between the contact surfaces of the individual components to reduce wear and carry away the heat of the individual components due to friction or current.

During the circulation of the lubricating oil, some of the lubricating oil may leave the compressor with the working fluid. If the amount of lubrication oil leaving the compressor is too large, the amount of lubrication oil in the sump gradually decreases, i.e., the oil level drops, after a period of operation of the compressor, resulting in an insufficient amount of lubrication oil in the compressor to maintain normal operation of the movable components, and thus, resulting in a failure of the compressor to operate normally. Therefore, it is very important to maintain the oil level of the oil sump in the compressor. On the other hand, the lubricating oil discharged from the compressor with the working fluid also adheres to coils such as condensers and evaporators, thereby affecting the heat exchange efficiency of the working fluid with the surrounding air. Therefore, the compressor needs to reasonably control its oil circulation rate (also referred to as oil circulation rate). Here, the oil circulation rate may be understood as a (mass) ratio of the lubricating oil contained in each unit of working fluid discharged from the compressor.

To control the oil circulation rate, an oil-gas separation device may be provided in the compressor. However, since the internal space of the casing of the compressor is limited, a compressor having a simple structure, small occupied space, but high efficiency in controlling the oil circulation rate is desired.

Disclosure of Invention

An object of the present invention is to provide a rotary machine which is simple in structure, occupies a small space, and can efficiently control oil circulation efficiency.

Another object of the present invention is to provide a compressor which is simplified in its manufacture and assembly, is low in cost, and can reasonably control the oil circulation rate of the compressor.

According to one aspect of the present invention, there is provided a rotary machine including a housing, a rotary member, and a discharge member. The housing contains an oil-gas mixture therein. The rotating member is disposed within the housing and is rotatable about an axis of rotation to cause the mixture of oil and gas to form a cyclone flow whereby the oil content of the mixture of oil and gas under centrifugal force decreases as the rotating member is positioned closer. The discharge member is provided on the housing and extends radially inward from the housing to a position where the content of the oil is equal to or less than a predetermined content. The rotary machine according to the present invention can control the circulation rate of lubricating oil well.

In some embodiments, the end of the discharge member within the housing and the outer circumferential surface of the rotary member have a predetermined distance therebetween, and a ratio between the predetermined distance and a diameter of the circular discharge passage of the discharge member is less than 1.5.

In some embodiments, a ratio between the predetermined distance and a diameter of the circular discharge channel of the discharge member is greater than 0.25.

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

In some embodiments, the rotary member has a first axial end face and a second axial end face in an axial direction, the discharge member being positioned between a first axial position in which a radial side of a discharge passage of the discharge member is located axially outward of the first axial end face and an opposite radial side of the discharge passage is aligned with the first axial end face; the other radial side of the discharge passage in the second axial position is located axially outward of the second axial end face while the one radial side of the discharge passage is aligned with the second axial end face.

In some embodiments, the discharge member is positioned in substantial alignment with an axially central portion of the rotary member.

In some embodiments, an end of the discharge member adjacent to the rotation member extends linearly in a horizontal direction perpendicular to the rotation axis, and an end face of the end is oriented obliquely with respect to an outer peripheral surface of the rotation member.

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

In some embodiments, the discharge port of the discharge member is oriented to face a downstream side of the rotation direction of the rotation member, and the oil-gas mixture within the housing enters the discharge member via the discharge port.

In some embodiments, the rotary member has a first axial end face and a second axial end face in an axial direction, the discharge member is positioned axially outward of the first axial end face or the second axial end face, and an end of the discharge member located within the housing extends inward to be flush with or to extend radially inward of an outer peripheral face of the rotary member.

In some embodiments, the rotary member is in the form of a cam, eccentric or counterweight and the exhaust member is in the form of an exhaust pipe or exhaust passage.

In some embodiments, the rotary machine further comprises a compression mechanism, a drive shaft, and a motor. The compression mechanism is located within the housing and is configured to compress a working fluid. The 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 rotation of the drive shaft. The rotating member is provided on the drive shaft or on the rotor.

In some embodiments, the rotary member is located between the compression mechanism and the motor or between the motor and an oil reservoir.

In some embodiments, the rotary machine is a high-pressure side scroll compressor.

In the above structure, since the rotating member in the rotating machine can drive the surrounding oil-gas mixture to form a cyclone flow when rotating, the lubricating oil can be separated from the oil-gas mixture under the centrifugal force before the oil-gas mixture leaves the compressor, so that the lubricating oil circulation rate can be well controlled. In one aspect, the oil level of an oil sump within a compressor may be maintained at a desired level. On the other hand, the amount of lubrication exiting the compressor into the compressor system may be reduced, for example, the amount of lubrication entering the heat exchanger, thereby improving the overall operating efficiency of the compressor system.

Drawings

The features and advantages of one or more embodiments of the present invention will become more readily appreciated from the following description, taken in conjunction with the accompanying drawings, in which:

FIG. 1 is a longitudinal cross-sectional view of a compressor including an oil and gas separation device according to an embodiment of the present invention;

FIG. 2 is a schematic cross-sectional view of a gas-oil separation device of the compressor of FIG. 1;

FIG. 3 is a schematic illustration of the oil and gas separation device of FIG. 1 illustrating different radial positions of the exhaust pipe relative to the balance weight;

FIG. 4 is a schematic illustration of the oil and gas separation device of FIG. 1 illustrating different axial positions of the exhaust pipe relative to the balance weight;

FIGS. 5 and 6 are schematic views of a compressor having oil and gas separation devices located at different locations;

FIG. 7 is a graph showing the distance between the exhaust pipe and the balance weight and the circulation rate;

FIG. 8a is a cross-sectional oil and gas distribution diagram of an oil and gas separation device according to the present invention;

FIG. 8b is a graph of a hydrocarbon distribution of a cross-sectional view of a hydrocarbon separation device of a comparative example;

FIG. 9 is a schematic view similar to FIG. 2 showing a variation of the exhaust pipe; and

FIG. 10 is a schematic longitudinal section of an oil and gas separation device of a compressor, illustrating another variation of an exhaust pipe.

Detailed Description

The following description of the preferred embodiment(s) is merely exemplary in nature and is in no way intended to limit the invention, its application, or uses. The same reference numerals are used to denote the same parts throughout the various drawings, and thus the construction of the same parts will not be repeated.

For ease of description, where a component is capable of rotation about an axis of rotation, references herein to "longitudinal direction" or "axial direction" for that component refer to a direction parallel to the axis of rotation, and "radial direction" refers to a direction perpendicular to the axis of rotation. The terms "first," "second," and the like herein are used merely to distinguish between different components and are not used to indicate a sequence or other meaning.

The oil and gas separation device and the compressor including the same according to the present invention will be described below with reference to the accompanying drawings. The figures show a high pressure side-elevation scroll compressor, however, it should be understood that the present invention is also applicable to other types of compressors, such as horizontal scroll compressors, rotor compressors, piston compressors, and the like.

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

The motor 13 includes a stator 13b fixed to the housing 11 and a rotor 13a located inside the stator 13b and fixed to the drive shaft 14. When the motor 13 is started, the rotor 13a rotates and brings the drive shaft 14 to rotate together.

The drive shaft 14 is fitted with the compression mechanism 12 to drive the compression mechanism 12 to compress a working fluid (typically gaseous) as the drive shaft 14 rotates. In the scroll compressor 10 shown in the drawings, an eccentric crank pin 14b of a drive shaft 14 is fitted in an orbiting scroll 12b of a compression mechanism 12 to drive the orbiting scroll 12b to rotate.

Compressor 10 also includes a main bearing housing 15 secured to housing 11. The main bearing housing 15 rotatably supports the drive shaft 14 via a main bearing 15a, and supports the compression mechanism 12, particularly the orbiting scroll member 12 b.

The compression mechanism 12 includes a non-orbiting scroll member 12a fixed to the housing 11 or main bearing housing 15 and an orbiting scroll member 12b movable relative to the non-orbiting scroll member 12 a. The orbiting scroll member 12b orbits (i.e., the central axis of the orbiting scroll member orbits the central axis of the non-orbiting scroll member, but the orbiting scroll member itself does not orbit the central axis itself) with respect to the non-orbiting scroll member 12a under the drive of the drive shaft 14. A series of compression chambers whose volumes gradually decrease from the radially outer side to the radially inner side are formed between the spiral vane of the fixed scroll member 12a and the spiral vane of the movable scroll member 12b. The working fluid is compressed in these compression chambers and then discharged through the discharge port 17 of the compression mechanism 12. The discharge port 17 of the compression mechanism 12 is disposed generally at the approximate center of the end plate of the non-orbiting scroll member 12 a.

During operation of the scroll compressor, centrifugal forces or moments generated by the rotation of the eccentric member may cause vibration of the compressor. Generally, a balance weight is provided on the rotating member to provide a counter centrifugal force or centrifugal moment to balance the amount of unbalance generated by the eccentric member. In the compressor 10 shown in fig. 1, the weight 110 is fixed to the outer peripheral surface of the drive shaft 14 and is adjacent to the main bearing housing 15, the weight 210 is provided on the end surface of the rotor 13a of the motor 13 facing the compression mechanism 12, and the weight 310 is provided on the end surface of the rotor 13a of the motor 13 facing away from the compression mechanism 12. While the compressor in the figures includes three weights, it should be understood that the number of weights may vary depending on the particular application requirements.

In the example of the compressor shown in fig. 1, an oil reservoir 20 for storing lubricating oil is provided at the bottom of the compressor housing 11. A passage 14a extending substantially in the axial direction thereof may be formed in the drive shaft 14, and the lubricating oil in the oil reservoir 20 is supplied to the respective bearings of the compressor, the bearing surface between the main bearing housing 15 and the orbiting scroll member 12b, and the compression mechanism, etc. through the passage 14 a. After lubricating the various components of the compressor, the lubricating oil is returned to the oil reservoir 20.

As shown in fig. 1, the compressor 10 is a high-pressure side scroll compressor. An exhaust pipe (exhaust member) 130 is provided in the housing 11. The low-pressure working fluid is directly supplied into the suction chamber or low-pressure chamber of the compression mechanism 12 through an intake pipe (not shown) and an intake port (not shown) of the compression mechanism, and then compressed and discharged from the discharge port 17 of the compression mechanism 12 into a space surrounded by the housing 11 of the compressor. In the illustrated example, a discharge tube 130 is sealingly mounted in the housing 11 for discharging compressed gas from the compressor 10. During operation of the compressor, the working fluid discharged from the discharge port 17 is mixed with the lubricating oil, and the lubricating oil supplied from the passage 14a of the drive shaft 14 is distributed in the space within the compressor housing 11 in the form of oil mist due to the movement of the movable scroll 12b, the rotor 13a of the motor 13, and the like. Therefore, the high-pressure working fluid to be discharged from the discharge pipe 130 of the compressor often contains lubricating oil, and thus it is necessary to control the amount of lubricating oil in the working fluid discharged from the compressor through the discharge pipe 130 to control the Oil Circulation Rate (OCR) of the entire compressor.

In order to well control the Oil Circulation Rate (OCR) of the compressor, an oil-gas separation device may be provided in the compressor 10. However, the additionally provided oil and gas separation device needs to occupy a certain space and complicate the manufacturing and assembling processes. In particular, in the case of a limited internal space of the compressor, it is not suitable to additionally provide the oil and gas separation device.

To overcome the above problems, the present inventors have conceived a solution that can reasonably control an Oil Circulation Rate (OCR) of a compressor by separating lubricating oil from a high-pressure working fluid using centrifugal force and discharging the working fluid having a reduced content or even no lubricating oil using existing components in the compressor and merely by reasonably configuring a relative positional relationship between the respective components. Such a solution allows a significant reduction in the number of components, a saving in installation space and a simplification of the assembly process, which results in a considerable reduction in costs.

An oil and gas separation apparatus according to an embodiment of the present invention will be described below with reference to fig. 1 and 2. As shown, the oil and gas separation device includes a balance weight 110 and an exhaust pipe 130. The weight 110 is fixed to the outer peripheral surface of the drive shaft 14 and is rotatable with the drive shaft 14. In this example, the axis of rotation of the counterbalance 110 is also the axis of rotation of the drive shaft 14, i.e., the longitudinal central axis of the drive shaft 14. The exhaust pipe 130 is located outside the balance weight 110 in the radial direction and is sealingly fixed to the housing 11.

The balance weight 110 has a first axial end face 115 and a second axial end face 117 that are adjacent to and face the outer peripheral surface 111 of the exhaust pipe 130, opposite to each other. Referring to fig. 1,2 and 3, the weight may have a radial protrusion 112 protruding radially outward, and an axial protrusion 114 extending axially from a second axial end surface 117. It will be appreciated that the configuration of the weights (particularly the location, size, number of protrusions, etc.) may vary depending on the particular application. For example, the weight may have only any one of the radial protrusion and the axial protrusion. Additionally or alternatively, the weight may have an axial projection extending axially from the first axial end face.

As the weight 110 rotates with the drive shaft 14, the radial protrusions 112 and axial protrusions 114 of the weight 110 may agitate and force the surrounding mixture of air and fuel discharged from the exhaust port 17 into a swirling flow. Under the influence of centrifugal force, the lubricating oil in the oil-gas mixture is thrown radially outwards to the housing 11 and flows back down the housing 11 into the oil reservoir 20 under the influence of gravity. Thus, the oil and gas mixture near the balance weight 110 has a lower oil content, while the oil and gas mixture near the housing 11 has a higher oil content. The lubricating oil content in the oil-gas mixture increases in the direction from the balance weight 110 to the housing 11. The oil and gas mixture radially inward of the cyclone flow has a lower lubricant content than the oil and gas mixture radially outward of the cyclone flow. Therefore, the inventors propose to position the end of the exhaust pipe located inside the housing within the range of the cyclone flow caused by the rotation of the counterweight, in particular in the radially inner part of the cyclone flow. The desired content of lubricating oil in the oil-gas mixture to be discharged may be predetermined according to the desired oil circulation rate. Then, the position of the exhaust pipe may be determined according to a predetermined desired content (also referred to as "predetermined content"). That is, the exhaust pipe may be extended radially inward from the housing to a position where the content of the lubricating oil in the oil-gas mixture is equal to or less than the predetermined content.

It should be understood that the inventive concept of the present invention is based on the principle that the cyclone flow caused by the rotation of the balance weight 110 causes the gradient of the lubricant oil content between the balance weight 110 and the housing 11 and obtains a desired reduced oil circulation rate through the relative positional relationship between the exhaust pipe 130 and the balance weight 110. In some existing compressors, the exhaust pipe also extends into the compressor housing for a certain length due to the installation requirement, but in this case, the extending length of the exhaust pipe only needs to meet the installation requirement, so the extending end of the exhaust pipe is often closer to the compressor housing. Furthermore, in some existing compressors, the discharge tube also extends into the compressor housing for a length to avoid the flow of lubricant into the discharge tube, as the lubricant flows along the inner surface of the compressor housing. However, the extension length of the exhaust pipe in the conventional compressor is set irrespective of the rotation of the weight, the cyclone flow generated by the rotation of the weight, and the like.

In one embodiment, the exhaust pipe 130 may be positioned closer to the balance weight 110 between the housing 11 and the balance weight 110 according to the inventive concept of the present invention. Preferably, the exhaust pipe 130 is disposed adjacent to the balance weight 110, i.e., positioned at a predetermined distance from the outer circumferential surface of the balance weight 110, so as to discharge the working fluid containing a reduced amount of lubricating oil, or even no lubricating oil, as needed.

Referring to fig. 2 and 3, the exhaust pipe 130 is a circular tubular member and has a circular exhaust passage 133. The exhaust pipe 130 also has an end face 131 adjacent the counterweight 110. In other words, the end face 131 of the exhaust pipe 130 located within the housing extends inwardly from the wall of the housing to near the weight 110. The end surface 131 of the exhaust pipe 130 is spaced apart from the outer peripheral surface 111 of the weight 110 by a distance L. Desirably, the distance L can both facilitate the evacuation of the working fluid via the exhaust pipe 130 and ensure that the evacuated working fluid contains a relatively low level of lubricating oil. The distance L may be determined according to the operating conditions, such as the rotational speed of the balance weight 110, the ambient pressure, the distance of the balance weight 110 to the housing 11, the content of the lubricating oil in the working fluid discharged through the exhaust port 17, the desired content of the lubricating oil in the working fluid discharged through the exhaust pipe 130, and the like. The distance L may be predetermined or may vary depending on the operation of the compressor. Preferably, the end face 131 of the exhaust pipe 130 is desirably as close to the outer peripheral surface 111 of the balance weight 110 as possible to provide a better oil-gas separation effect, but at the same time, it is desirable that the distance between the end face 131 of the exhaust pipe 130 and the outer peripheral surface 111 of the balance weight 110 is not so small as to disadvantageously reduce the flow area of the exhaust pipe 130.

Reference herein to "lower content lubricating oil" or "reduced content lubricating oil" or the like means that the content of lubricating oil in the working fluid discharged via the discharge pipe 130 is less than the content of lubricating oil in the working fluid in the compressor housing 11 and is within a range of suitable lubricating Oil Circulation Rate (OCR). For convenience of description, the "working fluid in the compressor housing" is referred to herein as the "working fluid before separation" or the "oil-gas mixture", and the "working fluid discharged through the discharge pipe 130" is referred to herein as the "working fluid after separation".

In the example of fig. 3, assuming a diameter D of the circular exhaust channel 133, the ratio L/D of the distance L to the diameter D may be less than about 1.5. In some examples, the ratio L/D of the distance L to the diameter D may be greater than about 0.25. In some examples, the ratio L/D of the distance L to the diameter D may be between about 0.25 and 1.25, between about 0.4 and 1, between about 0.4 and 0.75, preferably between about 0.4 and 0.5. More preferably, the ratio of the distance L to the diameter D may be about 0.5. Referring to fig. 7, a graph showing the distance between the discharge pipe and the balance weight and the circulation rate when the compressor is operated at 5400RPM (revolutions per minute) is shown. In fig. 7, the abscissa represents the radial distance L between the end face of the exhaust pipe and the outermost circumferential surface of the weight, where D represents the inner diameter of the exhaust pipe; the ordinate indicates the oil circulation rate OCR of the compressor. As shown in fig. 7, the oil circulation rate of the compressor is lowest, about 1.08%, when L is about 1/2D. For the prior art compressors, the oil circulation rate exceeded 5% when the compressor was operated at 5400 RPM. In contrast, in the present invention, by disposing the exhaust pipe adjacent to the weight, that is, by setting the distance between the exhaust pipe and the weight within a certain range, the oil circulation rate of the compressor can be significantly reduced, with a remarkable unexpected technical effect.

The inventors tested conventional compressors and compressors according to the present invention and the test results are listed in the following table. The tests were carried out on a set of conventional compressors (C1) and on three inventive compressors (T1, T2 and T3) with a ratio of distance L to diameter D of 0.4 in the inventive compressors, under different conditions (different speeds of rotation of the counterweight). The test results in the table are the lubricating oil content in the separated working fluid. In the conventional compressor C1, the discharge pipe is extended into the compressor housing only for convenience of assembly, but is far away from the weight, i.e., the distance of the discharge pipe from the weight is much larger than the inner diameter of the discharge pipe.

Rotating speed (RPM)	T1	T2	T3	C1
					3600	0.42％	0.41％	0.37％	1.29％
5400	0.96％	1.13％	0.57％	5.54％
					6000	1.77％	1.77％	1.24％	7.56％

From the above-described tests and the test results in the table, it is apparent that the content of the lubricating oil in the working fluid discharged from the compressor according to the present invention is significantly lower than that in the working fluid discharged from the conventional compressor. The test result shows that the liquid-gas separation device can efficiently separate lubricating oil from an oil-gas mixture. Therefore, the compressor of the present invention significantly reduces the circulation rate (OCR) of the lubricating oil. This is an effect not expected by conventional compressors in the art before the present invention was made.

Referring also to FIGS. 8a and 8b, FIG. 8a is a cross-sectional oil and gas distribution diagram of an oil and gas separation device according to the present invention; FIG. 8b is a graph of a hydrocarbon distribution of a cross-sectional view of a hydrocarbon separation device of a comparative example. As can be seen from fig. 8b, there is a region of higher lubricant content near the outer peripheral surface of the weight, and there is a region of higher lubricant content near the compressor housing, and the content of lubricant contained in the working fluid discharged from the discharge pipe is higher. In contrast, in fig. 8a, the region where the lubricant content is high is concentrated near the housing, and thus, the working fluid discharged from the discharge pipe provided adjacent to the weight contains a smaller amount of lubricant, thereby reducing the oil circulation rate of the compressor.

In the compressor of the present invention, the balance weight acts as an active rotating member and forces the surrounding oil-gas mixture to form a cyclone flow when it rotates, thereby throwing out the lubricating oil having a relatively high specific gravity radially outward under the action of centrifugal force. Thus, the working fluid near the weight contains less lubricating oil, and is easily discharged from the exhaust pipe provided near the weight.

In another embodiment, the end face 131 of the exhaust pipe 130 may not be parallel to the outer peripheral surface 111 of the balance weight 110 in the rotation axis direction of the balance weight 110, but may face the balance weight 110 and be inclined with respect to the outer peripheral surface 111 of the balance weight 110. In an alternative embodiment, the discharge port of the discharge tube 130 may be oriented to face the downstream side of the direction of rotation of the counterweight, wherein the oil-gas mixture within the compressor housing enters the discharge tube via the discharge port and exits the compressor through the discharge tube. In this way, the amount of lubricating oil that enters the exhaust pipe 130 can be reduced, so that a better oil-gas separation effect can be achieved.

In some examples, the bleed tube 130 may extend linearly from the compressor housing in a horizontal direction perpendicular to the direction of the axis of rotation of the counterweight 110. The end face 131 of the exhaust pipe 130 is oriented toward the outer peripheral surface 111 of the balance weight 110 and is inclined with respect to the outer peripheral surface 111 of the balance weight 110. In this case, the angle between the end face 131 of the exhaust pipe 130 and the central longitudinal axis of the exhaust pipe 130 is greater than 0 degrees but less than 90 degrees.

In other examples, the end of the exhaust pipe 130 adjacent to the weight 110 may be bent in a circumferential direction of the weight 110 and/or in a vertical direction parallel to the rotational axis of the weight 110. That is, the exhaust pipe 130 may include a bent end portion located within the housing. The bent end may be curved in an arc shape or may be bent at a constant angle.

As shown in fig. 9, the bent end 230 of the exhaust pipe 130 is bent in the circumferential direction of the weight 110. In one example, the discharge outlet at the end face 231 of the bent end 230 may face downstream of the rotational direction of the balance weight 110. Thus, a better oil-gas separation effect can be achieved.

As shown in fig. 10, the bent end 330 of the exhaust pipe 130 is bent in a vertical direction parallel to the rotation axis of the balance weight 110. In the illustrated example, the end face 331 of the bent end 330 may be oriented downward. In alternative examples, end face 331 of bent end 330 may be oriented downward or may be oriented in any other suitable direction that reduces the amount of lubrication oil entering the exhaust pipe.

In the illustrated axial direction of the compressor, the discharge tube 130 may be positioned within the range of the cyclone flow caused by the rotation of the balance weight 110. In the example shown in fig. 4, the exhaust pipe 130 may be positioned between a first axial position P1 and a second axial position P2. In the first axial position P1, the exhaust pipe 130 is located axially outward of the first axial end surface 115 of the balance weight 110 and is substantially aligned with the first axial end surface 115. In other words, in the first axial position P1, one radial side of the discharge passage 133 of the exhaust pipe 130 is located axially outward of the first axial end face 115, while the opposite radial side of the discharge passage 133 is substantially aligned with the first axial end face 115. According to the orientation in fig. 4, at the first axial position P1, the exhaust pipe 130 is located below the first axial end face 115 of the weight 110 in the axial direction, and the axially uppermost portion of the exhaust passage of the exhaust pipe 130 is substantially aligned with the first axial end face 115. In the second axial position P2, the exhaust pipe 130 is located axially outward of the second axial end surface 117 of the weight 110 and is substantially aligned with the second axial end surface 117. In other words, in the second axial position P2, the other side of the exhaust passage of the exhaust pipe 130 in the radial direction is located axially outward of the second axial end surface 117, while the one side of the exhaust passage in the radial direction is substantially aligned with the second axial end surface 117. According to the orientation in fig. 4, in the second axial position P2, the exhaust pipe 130 is located above the second axial end surface 117 of the weight 110 in the axial direction, and the axially lowermost portion of the exhaust passage of the exhaust pipe 130 is substantially aligned with the second axial end surface 117.

It is contemplated by the present disclosure that the exhaust pipe 130 may also be positioned axially outward (i.e., lower than the first axial position P1 or higher than the second axial position P2) of each of the first axial position P1 and the second axial position P2 and may extend further inward in the radial direction, such as to be flush with the outer circumferential surface 111 of the balance weight 110 or even to extend radially inward of the outer circumferential surface 111 of the balance weight 110. The working fluid discharged from the exhaust pipe 130 can maintain a low Oil Circulation Rate (OCR) due to the cyclone flow caused by the rotation of the balance weight 110.

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

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

It will be appreciated that the counterweight may have any suitable configuration so long as the counterweight is capable of rotating and forcing the surrounding mixture of oil and gas into a cyclonic flow. For example, the weights may have a constant radial dimension or a varying radial dimension, and/or may have a constant axial dimension or a varying axial dimension. The weight may have a cylindrical outer peripheral surface, a tapered outer peripheral surface, or any other suitably shaped outer peripheral surface capable of achieving the above-described effects. The weights shown in the figures may be replaced by cams, eccentrics or any other suitable means capable of achieving the above-described effects, depending on the particular application.

Similarly, the exhaust pipe may have any suitable structure and/or number as long as it can facilitate the evacuation of the working fluid. For example, the exhaust pipe may include a flared end. The exhaust pipe may include an end portion disposed obliquely with respect to the outer peripheral surface of the weight. For example, the end of the exhaust pipe adjacent to the counterweight is inclined downward, which may facilitate outflow of lubricating oil on the inner wall of the exhaust pipe. The compressor in the figure includes one discharge pipe, however, the number of discharge pipes may be plural. The exhaust pipe shown in the figures may also be replaced by an exhaust channel provided in the fixed structure, depending on the particular application.

While some embodiments and modifications of the present invention have been specifically described, it will be understood by those skilled in the art that the present invention is not limited to the embodiments and modifications described above and shown in the drawings, but may include other various possible modifications and combinations. For example, the oil and gas separation device may not have a bottom, whereby the lubricating oil may be allowed to fall directly along the wall into the oil reservoir. Other modifications and variations can be effected by those skilled in the art without departing from the spirit and scope of the invention. All such modifications and variations are intended to be within the scope of the present invention. Moreover, all the components described herein may be replaced by other technically equivalent elements.

Claims

1. A rotary machine, comprising:

A housing containing an oil-gas mixture therein,

A rotating member (110) disposed within the housing and rotatable about an axis of rotation to entrain the oil-gas mixture into a cyclone flow, whereby the content of oil in the oil-gas mixture under centrifugal force decreases as it approaches the rotating member; and

A discharge member (130) provided on the housing and extending radially inward from the housing to a position where the content of the oil is equal to or less than a predetermined content,

Wherein the rotary member has a first axial end face (115) and a second axial end face (117) in the direction of the rotation axis, the discharge member being positioned between a first axial position (P1) in which a radial side of a discharge passage of the discharge member is located axially outward of the first axial end face and an opposite radial side of the discharge passage is aligned with the first axial end face, and a second axial position (P2) in which the radial side of the discharge passage is located axially outward of the second axial end face and the radial side of the discharge passage is aligned with the second axial end face,

Wherein a predetermined distance (L) is provided between an end of the discharge member located within the housing and an outer circumferential surface of the rotary member, and a ratio between the predetermined distance (L) and a diameter (D) of a circular discharge passage (133) of the discharge member (130) is less than 1.5.

2. The rotary machine of claim 1, wherein a ratio between the predetermined distance (L) and a diameter (D) of the circular discharge channel (133) of the discharge member (130) is greater than 0.25.

3. The rotary machine according to claim 2, wherein the ratio between the predetermined distance (L) and the diameter (D) of the circular discharge channel is between 0.4 and 0.5.

4. The rotary machine of claim 1, wherein the discharge member is positioned in substantial alignment with an axially central portion of the rotary member.

5. The rotary machine according to claim 1, wherein an end portion of the discharge member adjacent to the rotary member extends linearly in a horizontal direction perpendicular to the rotation axis, and an end face of the end portion is oriented obliquely with respect to an outer peripheral surface of the rotary member.

6. The rotary machine of claim 1, wherein an end of the ejection member adjacent to the rotary member is bent in a circumferential direction of the rotary member and/or in a vertical direction parallel to the rotation axis.

7. The rotary machine according to claim 1, wherein the discharge port of the discharge member is oriented to face a downstream side of a rotation direction of the rotary member, the oil-gas mixture within the housing entering the discharge member via the discharge port.

8. The rotary machine of claim 1, wherein the rotary member is in the form of a cam, eccentric or counterweight and the exhaust member is in the form of an exhaust pipe or exhaust passage.

9. The rotary machine of any one of claims 1-8, further comprising:

A compression mechanism (12) located within the housing and configured to compress a working fluid;

-a drive shaft (14) adapted to drive the compression mechanism; and

A motor (13) comprising a stator and a rotor rotatable relative to the stator and configured to drive rotation of the drive shaft;

Wherein the rotating member is provided on the drive shaft or on the rotor.

10. The rotary machine of claim 9, wherein the rotary member is located between the compression mechanism and the motor or between the motor and an oil reservoir.

11. The rotary machine of claim 9, wherein the rotary machine is a high-pressure side scroll compressor.