WO2019033894A1 - Rotary mechanism - Google Patents

Abstract

A rotary mechanism, comprising 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, the oil content in the oil and gas mixture is smaller as it approaches the rotary member (110); and 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.

Description

Rotating machinery

The present application claims priority to Chinese Patent Application No. PCT Application No. No. No. No. No. No. No. No. No. No. No. No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No No

Technical field

The invention relates to a rotating machine.

Background technique

The content of this section merely provides background information related to the present disclosure, which may not 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 within the bearing housing and is rotated by the motor. The rotation of the drive shaft in turn drives the movable member of the compression mechanism (for example, the orbiting scroll of the scroll compressor, the rotor of the rotor compressor, etc.) to compress the working fluid (for example, the refrigerant). Each movable part of the compressor (for example, the scroll of the scroll compressor, the rotor of the rotor compressor, the bearing, etc.) requires lubrication of the lubricating oil to maintain the stability and reliability of the operation of the respective movable parts and the entire compressor. Sex. Therefore, the lubricating oil circulation system of the compressor is an important part of the compressor.

During operation of the compressor, the lubricating oil is delivered from the oil sump to the respective movable parts of the compressor under the action of a pressure difference or under the action of a pumping mechanism to lubricate the various components to maintain the normal movement of the movable parts. Run and finally return to the oil pool. In addition, during the circulation of the lubricating oil, it can also carry away impurities between the contact surfaces of the various components to reduce wear and the tropical travel of the various components due to friction or current.

During the circulation of the lubricating oil, some of the lubricating oil leaves the compressor with the working fluid. If the amount of lubricating oil leaving the compressor is too large, the amount of lubricating oil in the oil pool gradually decreases after the compressor is operated for a period of time, that is, the oil level drops, resulting in insufficient amount of lubricating oil in the compressor to maintain the movable parts. Normal operation, resulting in the compressor not working properly. Therefore, it is very important to maintain the oil level in the oil pool in the compressor. On the other hand, as the working fluid exits the compressor, the lubricating oil also adheres to the coils such as the condenser and the evaporator, thereby affecting the heat exchange efficiency of the working fluid with the surrounding air. Therefore, the compressor needs to properly control its lubricating oil circulation rate (also referred to as oil circulation rate). Here, the oil circulation rate can be understood as the (mass) ratio of the lubricating oil contained in each unit of the working fluid discharged from the compressor.

In order to control the oil circulation rate, an oil and gas separation device can be provided in the compressor. However, since the internal space of the casing of the compressor is limited, a compressor which is simple in structure, small in space, and highly efficient in controlling the oil circulation rate is desired.

Summary of the invention

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

Another object of the present invention is to provide a compressor which is simple in manufacture and assembly, low in cost, and capable of properly controlling the oil circulation rate of the compressor.

According to an aspect of the invention, there is provided a rotary machine comprising a housing, a rotating member and a discharge member. An oil and gas mixture is contained in the housing. The rotating member is disposed within the housing and rotatable about a rotational axis to drive the oil and gas mixture to form a cyclonic flow, whereby the content of oil in the oil and gas mixture is closer to the rotating member under centrifugal force The smaller. The discharge member is disposed 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 amount. The rotary machine according to the present invention can well control the lubricating oil circulation rate.

In some embodiments, a distance between an end of the discharge member located in the housing and an outer peripheral surface of the rotating member is a predetermined distance from a diameter of a circular discharge passage of the discharge member The ratio between them is less than 1.5.

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

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

In some embodiments, the rotating member has a first axial end surface and a second axial end surface in an axial direction, and the discharge member is positioned between the first axial position and the second axial position, wherein a radial side of the discharge passage of the discharge member in the first axial position is located axially outward of the first axial end surface and an opposite radial other side of the discharge passage is opposite to the first An axial end face is aligned; in the second axial position, the radially other side of the discharge passage is located axially outside of the second axial end face and the radial one of the discharge passage The side is aligned with the second axial end face.

In some embodiments, the discharge member is positioned to be substantially aligned with an axially central portion of the rotating member.

In some embodiments, an end of the discharge member adjacent to the rotating member linearly extends in a horizontal direction perpendicular to the rotation axis, and an end surface of the end portion is inclined with respect to an outer circumferential surface of the rotating member Orientation.

In some embodiments, an end of the discharge 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 port of the discharge member is oriented to face the downstream side of the rotational direction of the rotating member, and the oil and gas mixture within the housing enters the discharge member via the discharge port.

In some embodiments, the rotating member has a first axial end surface and a second axial end surface in an axial direction, and the discharge member is positioned at the first axial end surface or the second axial end surface The axially outer side, and an end of the discharge member located inside the housing extends inwardly to be flush with the outer peripheral surface of the rotating member or to extend radially inward of the outer peripheral surface of the rotating member.

In some embodiments, the rotating member is in the form of a cam, an eccentric or a weight, the discharge member being in the form of an exhaust pipe or a discharge passage.

In some embodiments, the rotary machine further includes 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 configured to drive the drive shaft to rotate. The rotating member is disposed on the drive shaft or on the rotor.

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

In some embodiments, the rotating 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 and gas mixture to form a cyclone flow when rotating, the lubricating oil can be separated from the oil and gas mixture under the centrifugal force before the oil and gas mixture leaves the compressor, so as to well control the lubrication. Oil circulation rate. On the one hand, the oil level in the oil sump in the compressor can be maintained at a desired level. On the other hand, the amount of lubricating oil exiting the compressor into the compressor system can be reduced, for example, by reducing the amount of lubricating oil entering the heat exchanger, thereby increasing 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 <RTIgt;

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

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

Figure 3 is a schematic view of the oil and gas separation device of Figure 1 showing different radial positions of the exhaust pipe relative to the weight;

Figure 4 is a schematic view of the oil and gas separation device of Figure 1 showing different axial positions of the exhaust pipe relative to the weight;

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

Figure 7 is a graph showing the distance between the exhaust pipe and the weight and the circulation rate;

Figure 8a is an oil and gas distribution diagram of a cross section of an oil and gas separation device according to the present invention;

Figure 8b is a cross-sectional oil and gas distribution diagram of the oil and gas separation device of the comparative example;

Figure 9 is a schematic view similar to Figure 2 showing a variation of the exhaust pipe;

Figure 10 is a longitudinal cross-sectional view of the oil and gas separation device of the compressor showing another variation of the exhaust pipe.

Detailed ways

The following description of the preferred embodiments is merely exemplary and is in no way limiting The same reference numerals are used in the respective drawings to refer to the same components, and thus the construction of the same components will not be repeatedly described.

For ease of description, where a component is capable of rotating about an axis of rotation, the "longitudinal direction" or "axial direction" referred to herein for the component refers to the direction parallel to the axis of rotation, and the "radial direction". It refers to the direction perpendicular to the axis of rotation. The terms "first", "second", and the like, as used herein, are used to distinguish different components and are not intended to represent a sequence or other meaning.

An oil-gas separation device and a compressor including the oil-gas separation device according to the present invention will be described below with reference to the accompanying drawings. Shown in the drawings is a high pressure side vertical 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. Wait.

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 casing 11, and a rotor 13a positioned inside the stator 13b and fixed to the drive shaft 14. When the motor 13 is activated, the rotor 13a rotates and drives 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 the working fluid (typically gaseous) as the drive shaft 14 rotates. In the scroll compressor 10 shown in the drawing, the eccentric crank pin 14b of the drive shaft 14 is fitted in the movable scroll 12b of the compression mechanism 12 to drive the movable scroll 12b to rotate.

The compressor 10 also includes a main bearing housing 15 that is fixed to the housing 11. The main bearing housing 15 rotatably supports the drive shaft 14 via the main bearing 15a, and supports the compression mechanism 12, particularly the movable scroll member 12b.

The compression mechanism 12 includes a fixed scroll member 12a fixed to the housing 11 or the main bearing housing 15 and an orbiting scroll member 12b movable relative to the fixed scroll member 12a. Driven by the drive shaft 14, the orbiting scroll member 12b moves about the fixed scroll member 12a (i.e., the central axis of the orbiting scroll member moves around the central axis of the scroll member, but the orbiting scroll member itself does not Will rotate around its own central axis). A series of compression chambers whose volume gradually decreases from the radially outer side to the radially inner side are formed between the spiral blade of the fixed scroll member 12a and the spiral blade of the movable scroll member 12b. The working fluid is compressed in these compression chambers and then discharged through the exhaust port 17 of the compression mechanism 12. The exhaust port 17 of the compression mechanism 12 is generally disposed at substantially the center of the end plate of the fixed scroll member 12a.

During the operation of the scroll compressor, centrifugal force or centrifugal moment generated by the rotation of the eccentric member may cause vibration of the compressor. Typically, a counterweight is placed over the rotating component to provide a counter-centrifugal force or centrifugal moment to balance the amount of imbalance created by the eccentric component. In the compressor 10 shown in FIG. 1, the weight 110 is fixed to the outer peripheral surface of the drive shaft 14 and adjacent to the main bearing housing 15, and the weight 210 is disposed on the end surface of the rotor 13a of the motor 13 facing the compression mechanism 12. The weight 310 is disposed on an end face of the rotor 13a of the motor 13 facing away from the compression mechanism 12. Although the compressor in the Figure includes three balance weights, it should be understood that the number of balance weights can vary depending on the particular application needs.

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, through which the lubricating oil in the oil reservoir 20 is supplied to the respective bearings of the compressor, between the main bearing housing 15 and the movable scroll member 12b. Support surface, as well as components such as compression mechanisms. After lubricating the various components of the compressor, the lubricating oil is returned to the sump 20.

As shown in Fig. 1, the compressor 10 is a high pressure side scroll compressor. An exhaust pipe (discharge member) 130 is provided on the casing 11. The low pressure working fluid is directly supplied to the suction 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 exhausted from the compression mechanism 12. 17 is discharged into the space surrounded by the casing 11 of the compressor. In the illustrated example, the exhaust pipe 130 is sealingly mounted in the housing 11 to discharge compressed gas from the compressor 10. During the operation of the compressor, the working fluid discharged from the exhaust port 17 is mixed with lubricating oil, and the movement of the components of the movable scroll member 12b, the rotor 13a of the motor 13, and the like is also supplied from the passage 14a of the drive shaft 14. The lubricating oil is distributed in the space inside the compressor housing 11 in the form of an oil mist. Therefore, the high-pressure working fluid to be discharged from the exhaust pipe 130 to the compressor often contains lubricating oil, and therefore it is necessary to control the amount of lubricating oil in the working fluid discharged from the compressor via the exhaust pipe 130 to control the oil circulation rate of the entire compressor ( OCR).

In order to well control the oil circulation rate (OCR) of the compressor, an oil and 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 assembly process. Especially in the case where the internal space of the compressor is limited, it is not suitable to additionally provide an oil and gas separation device.

In order to overcome the above problems, the inventors of the present application conceived a solution which can utilize the existing components in the compressor and separate the high-pressure working fluid by centrifugal force only by rationally arranging the relative positional relationship between the respective members. The lubricating oil is discharged and the working fluid containing reduced or even no lubricating oil is discharged to properly control the oil circulation rate (OCR) of the compressor. Such a solution can significantly reduce the number of parts, save installation space, and simplify the assembly process, which can greatly reduce costs.

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

The weight block 110 has an outer peripheral surface 111 adjacent to and facing the exhaust pipe 130, a first axial end surface 115 and a second axial end surface 117 opposed to each other. Referring to FIGS. 1, 2, and 3, the weight may have a radially protruding portion 112 that protrudes outward in the radial direction, and an axial protrusion 114 that extends axially from the second axial end surface 117. It should be understood that the structure of the weight (especially the position, size and number of the protrusions, etc.) may vary depending on the particular application. For example, the weight may have only any of a radial projection and an axial projection. Additionally or alternatively, the weight may have an axial projection extending axially from the first axial end surface.

When the weight 110 rotates with the drive shaft 14, the radial projection 112 and the axial projection 114 of the weight 110 can agitate the surrounding oil and gas mixture discharged from the exhaust port 17 and force the surrounding oil and gas mixture to form. Cyclone flow. Under the action of the centrifugal force, the lubricating oil in the oil and gas mixture is slid radially outward to the casing 11 and flows downwardly along the casing 11 into the sump 20 under the force of gravity. Thus, the amount of lubricating oil in the oil and gas mixture near the weight block 110 is small, and the amount of lubricating oil in the oil and gas mixture near the casing 11 is higher. The lubricating oil content in the oil and gas mixture increases in the direction from the weight block 110 to the casing 11. The lubricating oil content in the radially inner hydrocarbon mixture of the cyclone flow is less than the lubricating oil content in the radially outer oil and gas mixture of the cyclonic flow. Therefore, the inventors propose to position the end of the exhaust pipe located inside the casing within the range of the cyclone flow caused by the rotation of the weight, in particular in the radially inner portion of the cyclone flow. The desired content of the lubricating oil in the oil and gas mixture to be discharged may be predetermined in accordance with the desired oil circulation rate. The position of the exhaust pipe can then be determined based on a predetermined desired content (also referred to as a "predetermined content"). That is, the exhaust pipe may be extended radially inward from the casing to a position where the content of the lubricating oil in the oil and gas mixture is less than or equal to the predetermined content.

It should be understood that the inventive concept of the present invention is based on the principle that the swirl flow caused by the rotation of the weight 110 causes the gradient of the lubricating oil content between the weight 110 and the casing 11 to change and the relative relationship between the exhaust pipe 130 and the weight 110 is passed. The positional relationship is to obtain a desired reduction in oil circulation rate. In some existing compressors, due to installation requirements, the exhaust pipe will also extend into the compressor casing for a certain length, but in this case, the extension length of the exhaust pipe can be as long as the installation requirements are met, so the exhaust The projecting end of the tube tends to be closer to the compressor housing. Further, in some existing compressors, since the lubricating oil flows along the inner surface of the compressor casing, the exhaust pipe also extends into the compressor casing for a length to prevent the lubricating oil from flowing into the exhaust pipe. However, the setting of the extension length of the exhaust pipe in the conventional compressor is independent of the rotation of the balance block, the cyclone flow generated by the rotation of the balance block, and the like.

In one embodiment, the exhaust pipe 130 may be positioned closer to the weight 110 between the housing 11 and the weight 110 in accordance with the inventive concepts of the present invention. Preferably, the exhaust pipe 130 is disposed adjacent to the weight 110, that is, at a predetermined distance from the outer circumferential surface of the weight 110 to discharge a working fluid containing a reduced amount of lubricating oil or even no lubricating oil that satisfies the need. .

Referring to Figures 2 and 3, the exhaust pipe 130 is a circular tubular member and has a circular discharge passage 133. The exhaust pipe 130 also has an end face 131 adjacent to the weight 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 the vicinity of the weight 110. The end surface 131 of the exhaust pipe 130 has a certain distance L from the outer peripheral surface 111 of the weight 110. It is desirable that the distance L can both facilitate the discharge of the working fluid via the exhaust pipe 130 and ensure that the discharged working fluid contains a lower level of lubricating oil. The distance L may be determined according to operating conditions, for example, the rotational speed of the weight 110, the ambient pressure, the distance of the weight 110 to the housing 11, the amount of lubricating oil in the working fluid discharged through the exhaust port 17, via the exhaust pipe. 130 The desired amount of lubricating oil in the working fluid discharged, and the like. The distance L may be predetermined or may vary depending on the operation of the compressor. Preferably, it is desirable that the end surface 131 of the exhaust pipe 130 is as close as possible to the outer circumferential surface 111 of the weight 110 to provide a better oil and gas separation effect, but at the same time, it is desirable that the end surface 131 of the exhaust pipe 130 and the outer circumferential surface 111 of the weight 110 The distance between them is not too small and the flow area of the exhaust pipe 130 is reduced.

As used herein, "lower amount of lubricating oil" or "reduced amount of lubricating oil" or the like means that the amount of lubricating oil in the working fluid discharged through the exhaust pipe 130 is less than that in the compressor casing 11. The amount of lubricating oil in the fluid is within the range of a suitable lubricating oil circulation rate (OCR). For convenience of description, "working fluid in the compressor casing" is referred to herein as "working fluid before separation" or "oil and gas mixture", and "working fluid discharged through the exhaust pipe 130" is referred to as "separated after separation". Working fluid".

In the example of FIG. 3, assuming that the diameter of the circular discharge passage 133 is D, 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 distance L to diameter D can be greater than about 0.25. In some examples, the ratio L/D of distance L to diameter D can 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 Figure 7, there is shown a graph of the distance and circulation rate between the exhaust pipe and the counterweight when the compressor is operated at 5400 RPM (revolutions per minute). In Fig. 7, the abscissa indicates the radial distance L between the end surface of the exhaust pipe and the outermost circumferential surface of the weight, where D represents the inner diameter of the exhaust pipe; and the ordinate represents the oil circulation rate OCR of the compressor. As shown in Fig. 7, when L is about 1/2 D, the oil circulation rate of the compressor is the lowest, about 1.08%. For prior art compressors, the oil circulation rate exceeds 5% when the compressor is operated at 5400 RPM. In contrast, in the present invention, the compressor oil can be significantly reduced by arranging the exhaust pipe adjacent to the balance block, that is, by setting the distance between the exhaust pipe and the balance block within a certain range. The cycle rate has achieved significant unexpected technical effects.

The inventors tested the conventional compressor and the compressor according to the present invention, and listed the test results in the table below. The test is carried out for a set of conventional compressors (C1) and three sets of inventive compressors (T1, T2 and T3) under different operating conditions (different speeds of the balancing mass), wherein the distance L in the compressor of the invention The ratio to the diameter D is 0.4. The test result in the table is the amount of lubricating oil in the separated working fluid. In the conventional compressor C1, the exhaust pipe protrudes into the compressor casing only for the convenience of assembly, but is far from the balance block, that is, the distance from the balance pipe to the balance pipe is much larger than the inner diameter of the exhaust pipe.

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%

According to the above test and the test results in the table, the content of the lubricating oil in the working fluid discharged from the compressor according to the present invention is significantly lower than the content of the lubricating oil in the working fluid discharged from the conventional compressor. The test results show that the liquid-gas separation device of the present invention can efficiently separate the lubricating oil from the oil-gas mixture. Therefore, the compressor of the present invention significantly reduces the circulation rate (OCR) of the lubricating oil. This is an unexpected effect of conventional compressors in the art prior to the present invention.

Reference is also made to Figs. 8a and 8b, which is a cross-sectional oil and gas distribution diagram of the oil and gas separation apparatus according to the present invention; and Fig. 8b is a cross-sectional oil and gas distribution diagram of the oil and gas separation apparatus of the comparative example. It can be seen from Fig. 8b that there is a region with a high lubricating oil content near the outer peripheral surface of the balance block, and a region having a high lubricating oil content in the vicinity of the compressor casing, and a lubricating oil contained in the working fluid discharged from the exhaust pipe. The content is higher. In contrast, in Fig. 8a, the region with a higher lubricating oil content is concentrated near the casing, so that the working fluid discharged from the exhaust pipe disposed adjacent to the balancing block contains a smaller amount of lubricating oil, thereby lowering the compressor. Oil circulation rate.

In the compressor of the present invention, the balance weight acts as an active rotating member, and when it rotates, the surrounding oil and gas mixture is forced to form a cyclone flow, thereby pulling out the lubricating oil having a larger specific gravity radially outward by the centrifugal force. . Thereby, the working fluid near the balance block contains less lubricating oil and is easily discharged from the exhaust pipe provided near the balance block.

In another embodiment, the end surface 131 of the exhaust pipe 130 may not be parallel to the outer circumferential surface 111 of the weight 110 in the direction of the rotation axis of the weight 110, but may face the weight 110 and be opposite to the weight 110 The outer peripheral surface 111 is inclined. In an alternative embodiment, the discharge port of the exhaust pipe 130 may be oriented to face the downstream side of the rotation direction of the balance block, wherein the oil and gas mixture in the compressor casing enters the exhaust pipe via the discharge port and is discharged through the exhaust pipe compressor. In this way, the amount of lubricating oil entering the exhaust pipe 130 can be reduced, so that a better oil and gas separation effect can be achieved.

In some examples, the exhaust pipe 130 may extend linearly from the compressor housing in a horizontal direction that is perpendicular to the direction of the axis of rotation of the weight 110. The end surface 131 of the exhaust pipe 130 is oriented toward the outer circumferential surface 111 of the weight 110 and is inclined with respect to the outer circumferential surface 111 of the weight 110. In this case, the angle between the end surface 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 that is parallel to the axis of rotation of the weight 110. That is, the exhaust pipe 130 can include a bent end located within the housing. The bent end may be a curved arc shape or may be bent at a constant angle.

As shown in FIG. 9, the bent end portion 230 of the exhaust pipe 130 is bent in the circumferential direction of the weight 110. In one example, the discharge port at the end surface 231 of the bent end portion 230 may face downstream of the rotational direction of the weight block 110. Thereby, a better oil and gas separation effect can be achieved.

As shown in FIG. 10, the bent end portion 330 of the exhaust pipe 130 is bent in a vertical direction parallel to the rotation axis of the weight 110. In the illustrated example, the end face 331 of the bent end 330 can be oriented downward. In an alternative example, the end face 331 of the bent end 330 can be oriented downward or can be oriented in any other suitable direction that can reduce the amount of lubricating oil entering the exhaust pipe.

In the axial direction of the illustrated compressor, the exhaust pipe 130 may be positioned within a range of cyclonic flow caused by the rotation of the weight 110. In the example shown in FIG. 4, the exhaust pipe 130 may be positioned between the first axial position P1 and the second axial position P2. At the first axial position P1, the exhaust pipe 130 is located axially outward of the first axial end surface 115 of the weight 110 and is substantially aligned with the first axial end surface 115. In other words, in the first axial position P1, the radial side of the discharge passage 133 of the exhaust pipe 130 is located axially outward of the first axial end surface 115, and the opposite radial side of the discharge passage 133 is the other side. An axial end face 115 is generally aligned. According to the orientation in FIG. 4, at the first axial position P1, the exhaust pipe 130 is located below the first axial end surface 115 of the weight 110 in the axial direction, and the axial direction of the discharge passage of the exhaust pipe 130 is the uppermost Portions are generally aligned with the first axial end face 115. At 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 radial side of the discharge passage of the exhaust pipe 130 is located axially outward of the second axial end surface 117, and the radial side of the discharge passage is the same The two axial end faces 117 are generally aligned. According to the orientation in FIG. 4, at 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 axial direction of the discharge passage of the exhaust pipe 130 is the most The lower portion is substantially aligned with the second axial end surface 117.

In accordance with the teachings of the present invention, the exhaust pipe 130 may also be positioned axially outward of each of the first axial position P1 and the second axial position P2 (ie, lower than the first axial position P1, or greater than the second axis It is higher toward the position P2 and may extend further inward in the radial direction, for example, to be flush with the outer peripheral surface 111 of the weight 110, or even to the radially inner side of the outer peripheral surface 111 of the weight 110. Due to the cyclonic flow caused by the rotation of the weight 110, the working fluid discharged from the exhaust pipe 130 is still capable of maintaining a low oil circulation rate (OCR).

In the embodiment shown in FIGS. 1 to 4, the weight 110 is disposed 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 balance block 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 disposed on an end surface 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 weight 310 disposed on an end surface 1302 of the rotor 13a of the motor 13 opposite to 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 FIGS. 1 to 4, the oil and gas separation device is disposed between the main bearing housing 15 and the motor 13. However, it should be understood 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 weight can have any suitable configuration as long as the weight can rotate and force the surrounding oil and gas mixture to form a cyclonic flow. For example, the weight can have a constant radial dimension or a varying radial dimension and/or can 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 suitable shape outer peripheral surface capable of achieving the above-described effects. Depending on the particular application, the weights shown in the figures can be replaced by cams, eccentrics or any other suitable means capable of achieving the above.

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

Although some embodiments and variations of the present invention have been specifically described, those skilled in the art will understand that the present invention is not limited to the embodiments and variations shown in the above description and the accompanying drawings but may include various other possible variations. And combination. For example, the oil and gas separation device may have no bottom, thereby allowing the lubricating oil to fall directly into the sump along the wall. Other variations and modifications can be made by those skilled in the art without departing from the spirit and scope of the invention. All such variations and modifications are intended to fall within the scope of the invention. Moreover, all of the components described herein can be replaced by other technically equivalent components.

Claims (14)

A rotating machine comprising: a housing in which the oil and gas mixture is contained, a rotating member (110) disposed in the housing and rotatable about an axis of rotation to drive the oil and gas mixture to form a cyclonic flow, whereby the content of oil in the oil and gas mixture is increased by centrifugal force Smaller near the rotating member; a discharge member (130) that is disposed 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 amount. The rotary machine according to claim 1, wherein a position of the discharge member located inside the housing and an outer peripheral surface of the rotary member has a predetermined distance (L), the predetermined distance (L) and The ratio between the diameters (D) of the circular discharge passages (133) of the discharge member (130) is less than 1.5. The rotary machine according to claim 2, wherein a ratio between the predetermined distance (L) and a diameter (D) of the circular discharge passage (133) of the discharge member (130) is greater than 0.25. The rotary machine according to claim 3, wherein a ratio between the predetermined distance (L) and a diameter (D) of the circular discharge passage is between 0.4 and 0.5. The rotary machine according to claim 1, wherein the rotating member has a first axial end surface (115) and a second axial end surface (117) in a rotation axis direction, and the discharge member is positioned in the first axial direction Between the position (P1) and the second axial position (P2), wherein a radial side of the discharge passage of the discharge member is located at the first axial end face in the first axial position (P1) An axially outer side and an opposite radial other side of the discharge passage aligned with the first axial end face, the radial other of the discharge passage in the second axial position (P2) The side 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. The rotary machine according to claim 5, wherein the discharge member is positioned to be substantially aligned with an axial central portion of the rotary member. The rotary machine according to claim 1, wherein an end portion of the discharge member adjacent to the rotation member linearly extends in a horizontal direction perpendicular to the rotation axis, and an end surface of the end portion is opposite to the The outer peripheral surface of the rotating member is oriented obliquely. The rotary machine according to claim 1, wherein an end of the discharge 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 . The rotary machine according to claim 1, wherein a discharge port of the discharge member is oriented to face a downstream side of a rotation direction of the rotary member, and an oil and gas mixture in the case enters the discharge member via the discharge port . The rotary machine according to claim 1, wherein the rotating member has a first axial end surface (115) and a second axial end surface (117) in an axial direction, and the discharge member is positioned at the first An axially outer side of the axial end surface (115) or the second axial end surface (117), and an end of the discharge member located inside the housing extends inwardly to be flush with an outer circumferential surface of the rotating member Or extending to the radially inner side of the outer peripheral surface of the rotating member. The rotary machine according to claim 1, wherein the rotating member is in the form of a cam, an eccentric or a weight, and the discharge member is in the form of an exhaust pipe or a discharge passage. The rotary machine according to any one of claims 1 to 11, further comprising: a compression mechanism (12), the compression mechanism being located within the housing and configured to compress a working fluid; a drive shaft (14) adapted to drive the compression mechanism; a motor (13), the motor including a stator and a rotor rotatable relative to the stator and configured to drive the drive shaft to rotate; Wherein the rotating member is disposed on the drive shaft or on the rotor. The rotary machine according to claim 12, wherein the rotating member is located between the compression mechanism and the motor or between the motor and the oil reservoir. The rotary machine according to claim 12, wherein the rotary machine is a high pressure side scroll compressor.

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