Flange structure, pump body and compressor

Abstract

The present application relates to a flange structure, a pump body and a compressor, specifically including a flange body and a flow guide member. The flange body has a central shaft hole and an exhaust hole that penetrate through in the thickness direction of the flange body itself. The central shaft hole and the exhaust hole are arranged at intervals along the radial direction of the flange body. The flow guide member is arranged in the exhaust hole to guide the gas in the exhaust hole to flow in a circumferential shape. Among them, the flange body is further provided with an oil return channel, and a flow guide groove is provided on the wall of the exhaust hole. The flow guide groove is communicated with the central shaft hole through the oil return channel. In this way, the present application forms an oil return loop between the exhaust passage and the central shaft hole to supplement oil for the crankshaft in the central shaft hole, avoiding a large amount of oil being carried out of the compressor by the exhaust of the exhaust passage, thereby improving the rotational lubrication degree of the compressor crankshaft and reducing wear, and further improving the reliability of the compressor.

Description

Technical Field

[0001] The present application relates to the technical field of compressors, and particularly to a flange structure, a pump body and a compressor. Background Art

[0002] In the fields of refrigeration and gas compression, rotary vane compressors are widely used due to their simple structure and high reliability. There are contacts and relative movements between the parts of a rotary vane compressor, and the working chamber of the compressor adopts clearance sealing. Therefore, lubricating oil is usually required in the compressor cylinder to achieve lubrication and sealing effects.

[0003] However, with the increase in the displacement of the compressor, the lubricating oil will be discharged together with the gas, which reduces the lubricating oil in the compressor oil sump, resulting in poor lubrication of the friction pairs of the compressor shafting, and further leading to poor reliability of the rotary vane compressor. Summary of the Invention

[0004] Based on this, in view of the problem that the compressor is prone to oil spitting and the reliability of the compressor becomes poor, the present application provides a flange structure, a pump body and a compressor, and the flange structure, the pump body and the compressor have the technical effect of being able to return oil and replenish oil.

[0005] In a first aspect, the present application provides a flange structure, including a flange body and a flow guiding member. The flange body has a central shaft hole and an exhaust hole that penetrate through in the thickness direction of the flange body itself. The central shaft hole and the exhaust hole are arranged at a radial interval along the flange body. The flow guiding member is arranged in the exhaust hole for guiding the gas in the exhaust hole to flow in a circular shape. Among them, the flange body further has an oil return channel. A flow guiding groove is provided on the wall of the exhaust hole. The flow guiding member is communicated with the flow guiding groove, and the flow guiding groove is communicated with the central shaft hole through the oil return channel.

[0006] In one embodiment, the flow guiding member has a flow guiding surface extending in a spiral shape, and one end of the flow guiding surface is communicated with the flow guiding groove.

[0007] In one embodiment, micro-textures are provided on the wall of the central shaft hole.

[0008] In one embodiment, the micro-textures include a plurality of micro-concave textures formed by concave in the wall of the central shaft hole and arranged in a matrix. An oil inlet hole communicated with the oil return channel is further provided on the wall of the central shaft hole, and the oil inlet hole is located between all the micro-concave textures.

[0009] In one embodiment, the cross-sectional area of the central shaft hole is S1, and the cross-sectional area of a single micro-concave texture is S2, and (S2 / S1)*100% ≤ 5%.

[0010] In one embodiment, along the opening direction of the exhaust hole, the diversion groove extends spirally on the wall of the exhaust hole.

[0011] In one embodiment, the flange body is further provided with an oil-gathering hole, which is arranged between the diversion groove and the oil return channel, and the diversion groove is communicated with the oil return channel through the oil-gathering hole.

[0012] In one embodiment, the oil-gathering hole is arranged along the thickness direction of the flange body.

[0013] In one embodiment, the oil return channel is linear or arc-shaped.

[0014] In a second aspect, a pump body of a compressor is provided, including a crankshaft of the compressor and the flange structure of any one of the above, and the crankshaft is rotatably arranged in the central shaft hole; the pump body has an exhaust passage, and the exhaust hole is a part of the exhaust passage.

[0015] In one embodiment, the pump body includes a lower flange, a lower cylinder, a sliding vane, a partition plate, an upper cylinder and an upper flange which are sequentially assembled and connected, the flange structure is the upper flange and / or the lower flange, and the pump body has an exhaust passage;

[0016] The exhaust passage extends through the lower flange to the upper flange, and the exhaust hole of the lower flange forms the inlet end of the exhaust passage, and the exhaust hole of the upper flange forms the outlet end of the exhaust passage.

[0017] In a third aspect, a compressor is further provided, including a housing, a motor and the pump body of any one of the above embodiments, the pump body and the motor are both assembled in the housing, and an oil storage cavity is formed between the pump body and the housing.

[0018] The above flange structure forms an oil return circuit. The gas entering the exhaust hole is first diverted by the diversion member and then changes its flow direction, flowing in a circular shape so that the exhaust gas has centrifugal force. The oil thrown out by the centrifugal force enters the diversion groove communicated with the diversion member, and then flows through the oil return channel into the central shaft hole to supplement oil for the rotating shaft in the central shaft hole, ensuring the oil supply of the rotating shaft. For example, when the rotating shaft is the crankshaft of the compressor, the oil in the oil return circuit enters the central shaft hole to complete the establishment of the oil film. It improves the rotational lubricity of the compressor crankshaft and reduces wear, thereby improving the reliability of the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0019] Figure 1 It is a schematic cross-sectional structure diagram of a compressor provided by an embodiment of the present application;

[0020] Figure 2Schematic cross-sectional structure diagram of the pump body of a compressor provided by an embodiment of the present application;

[0021] Figure 3 Schematic cross-sectional structure diagram of a flange structure provided by an embodiment of the present application;

[0022] Figure 4 is Figure 3 Schematic three-dimensional structure diagram of the flange structure provided in;

[0023] Figure 5 is Figure 3 Schematic cross-sectional structure diagram of another perspective of the flange body in the flange structure provided in;

[0024] Figure 6 is Figure 3 Schematic plan structure diagram of the flange body in the flange structure provided in;

[0025] Figure 7 is Figure 3 Schematic structure diagram of the flow guide member in the flange structure provided in.

[0026] Reference numerals: 1000, compressor; 100, flange structure; 10, flange body; 11, central shaft hole; 111, oil inlet hole; 12, exhaust hole; 121, flow guide groove; 13, oil return channel; 14, oil collecting hole; 20, flow guide member; 21, flow guide surface; 30, micro-texture; 200, housing; 300, motor; 310, stator; 320, rotor; 400, pump body; 410, silencer; 420, lower flange; 430, lower cylinder; 440, sliding vane; 450, partition; 460, upper cylinder; 470, upper flange; 480, exhaust passage; 500, crankshaft; 700, oil storage cavity; 710, upper cavity; 720, middle cavity; L1, thickness direction; L2, radial direction. Detailed Description of the Invention

[0027] In order to make the above objects, features, and advantages of the present application more obvious and understandable, the following detailed description of the specific embodiments of the present application will be given with reference to the accompanying drawings. Many specific details are set forth in the following description in order to fully understand the present application. However, the present application can be implemented in many other ways different from those described herein, and those skilled in the art can make similar improvements without departing from the connotation of the present application. Therefore, the present application is not limited by the specific embodiments disclosed below.

[0028] In the description of the present application, it should be understood that the orientation or positional relationships indicated by the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. are based on the orientation or positional relationships shown in the drawings. These are only for the convenience of describing the present application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and thus should not be construed as a limitation on the present application.

[0029] In addition, the terms "first" and "second" are used only for descriptive purposes and should not be construed as indicating or implying relative importance or implicitly specifying the quantity of the indicated technical features. Thus, features defined with "first" and "second" may explicitly or implicitly include at least one such feature. In the description of the present application, the meaning of "a plurality" is at least two, such as two, three, etc., unless otherwise specifically and clearly defined.

[0030] In the present application, unless otherwise clearly specified and limited, the terms "mounted", "connected", "coupled", "fixed", etc. shall be construed in a broad sense. For example, it may be a fixed connection, a detachable connection, or integrated; it may be a mechanical connection or an electrical connection; it may be directly connected or indirectly connected through an intermediate medium, and it may be the communication inside two elements or the interaction relationship between two elements, unless otherwise clearly limited. For those of ordinary skill in the art, the specific meanings of the above terms in the present application can be understood according to specific circumstances.

[0031] In the present application, unless otherwise clearly specified and limited, the first feature being "on" or "under" the second feature may be that the first and second features are in direct contact, or the first and second features are indirectly in contact through an intermediate medium. Moreover, the first feature being "above", "over" and "on top of" the second feature may be that the first feature is directly above or obliquely above the second feature, or merely indicates that the first feature has a higher horizontal height than the second feature. The first feature being "under", "beneath" and "underneath" the second feature may be that the first feature is directly below or obliquely below the second feature, or merely indicates that the first feature has a lower horizontal height than the second feature.

[0032] It should be noted that when an element is referred to as "fixed to" or "disposed on" another element, it can be directly on the other element or there may be an intermediate element. When an element is considered to be "connected" to another element, it can be directly connected to the other element or there may be an intermediate element at the same time. The terms "vertical", "horizontal", "upper", "lower", "left", "right" and similar expressions used herein are for illustrative purposes only and do not represent the only implementation.

[0033] The attached drawings are not drawn to a scale of 1:1, and the relative dimensions of each element are only drawn by way of example in the attached drawings and not necessarily to the actual scale.

[0034] Referring to Figures 1 to 2 , the present application provides a compressor 1000, which includes a housing 200, a motor 300 and a pump body 400. The pump body 400 and the motor 300 are both assembled in the housing 200, and an oil storage cavity 700 is formed between the pump body 400 and the housing 200, and a middle cavity 720 is formed between the pump body 400 and the motor 300, and an upper cavity 710 is formed between the motor 300 and the housing 200.

[0035] Specifically, referring to Figure 2 , the pump body 400 has a crankshaft 500. The crankshaft 500 extends along the axial direction of the housing 200 and is rotatably assembled inside the pump body 400. One end of the crankshaft 500 communicates with the oil storage cavity 700. Thus, when the compressor 1000 is operating, the oil storage cavity 700 can supply oil to the crankshaft 500 to ensure the normal rotation of the crankshaft 500.

[0036] However, as described in the background art, during the operation of the compressor 1000, the compressor 1000 will discharge high-pressure gas. At the same time as the compressor 1000 exhausts, the oil in the oil storage cavity 700 will be discharged together with the high-pressure gas. The larger the displacement of the compressor 1000, the more the lubricating oil in the oil storage cavity 700 of the compressor 1000 gradually decreases, which in turn leads to poor lubrication of the friction pair of the crankshaft 500 of the compressor 1000, and the compressor 1000 is prone to problems with poor reliability.

[0037] To solve the above problems, referring to Figures 3 to 6 , the present application provides a flange structure 100 for the pump body 400 of the compressor 1000. The flange structure 100 includes a flange body 10 and a flow guiding member 20. The flange body 10 has a central shaft hole 11 and an exhaust hole 12 that penetrate along its own thickness direction L1. The central shaft hole 11 and the exhaust hole 12 are arranged at intervals along the radial direction L2 of the flange body 10. The central shaft hole 11 is rotatably connected to a rotating shaft accommodated therein, that is, the rotating shaft can rotate relative to the flange body 10 in the central shaft hole 11. It can be understood that in the compressor 1000, the rotating shaft is the crankshaft 500 of the compressor 1000.

[0038] Further, a flow guiding member 20 is disposed in the exhaust hole 12 for guiding the gas in the exhaust hole 12 to flow in a circular shape. Wherein, the flange body 10 is further provided with an oil return flow channel 13, and a flow guiding groove 121 is provided on the hole wall of the exhaust hole 12. The flow guiding groove 121 is communicated with the central shaft hole 11 through the oil return flow channel 13.

[0039] In this way, the flange structure 100 of the present application forms an oil return circuit (flow guiding member 20 - flow guiding groove 121 - oil return flow channel 13). When the compressor 1000 exhausts, the high-temperature and high-pressure gas first enters the exhaust hole 12 and is redirected after being guided by the flow guiding member 20, flowing in a circular shape so that the exhaust gas has a centrifugal force. The oil thrown out by the centrifugal force enters the flow guiding groove 121 communicated with the flow guiding member 20, and then flows into the central shaft hole 11 through the oil return flow channel 13 to supplement oil for the rotating shaft in the central shaft hole 11, ensuring the oil supply of the rotating shaft, and the gas continues to rise and is discharged outwards.

[0040] For example, when the rotating shaft is the crankshaft 500 of the compressor 1000, the oil in the oil return circuit enters the central shaft hole 11 to establish an oil film on the hole wall of the central shaft hole 11, avoiding a large amount of oil being carried out of the compressor 1000 due to the exhaust of the exhaust hole 12, and also avoiding the complex structure caused by the need to provide an oil guiding groove inside the central shaft hole 11, thereby improving the rotational lubrication degree of the crankshaft 500 of the compressor 1000 and reducing wear, and further improving the reliability of the compressor 1000.

[0041] In other embodiments, the flange structure 100 can also be applied to other settings where a rotating shaft needs to be provided to provide an oil return function to ensure the lubrication of the rotating shaft.

[0042] In one embodiment, the flange body 10 is also called a flange flange or a collar. A flange is a part for connecting between shafts, used for connecting between pipe ends. The central shaft hole 11 of the flange is generally located at the geometric center of the flange body 10. The exhaust hole 12 is provided on the outer periphery of the central shaft hole 11. The exhaust hole 12 can be provided as one or more according to requirements. One or more oil return flow channels 13 are provided between each exhaust hole 12 and the central shaft hole 11 to control the oil return efficiency through the number of exhaust holes 12 and the number of oil return flow channels 13.

[0043] In one embodiment, micro-textures 30 are provided on the wall of the central shaft hole 11. The micro-textures 30 refer to patterns with certain dimensions, geometric morphologies, and arrangement modes prepared on the wall of the central shaft hole 11 by using specific microfabrication processes to improve the tribological properties of the surface. The special structure of the micro-textures 30 can ensure excellent surface friction performance, with a small friction coefficient, small frictional force, and small material wear on the friction surface. Thus, the micro-textures 30 are provided on the central shaft hole 11 facing the rotating shaft, further improving the lubrication effect on the rotating shaft and enhancing the reliability and overall performance of the compressor 1000.

[0044] Specifically, the micro-textures 30 include a plurality of micro-recessed textures formed by concave recesses on the wall of the central shaft hole 11 arranged in a matrix. Its structure is specifically a pit or a groove, and the shape of each is preferably set to be circular, or oval, triangular, rectangular, or various shapes that are combinations thereof. The micro-recessed textures have the ability to store liquid by capillarity. After the oil in the exhaust hole 12 flows back into the central shaft hole 11 in the oil return circuit, some oil is stored inside each micro-recessed texture, thereby further improving the lubrication effect on the rotating shaft.

[0045] Furthermore, an oil inlet hole 111 communicating with the oil return channel 13 is also provided on the wall of the central shaft hole 11. The oil inlet hole 111 is located between all the micro-recessed textures, which is equivalent to a divergent uniform matrix distribution of the micro-recessed textures around the oil inlet hole 111. At this time, the oil entering through the oil inlet hole 111 can evenly fill the surrounding micro-recessed textures.

[0046] Preferably, all the micro-recessed textures can be evenly opened on the wall of the central shaft hole 11 along the axial direction of the central shaft hole 11, i.e., the thickness direction L1 of the flange body 10. An oil inlet hole 111 can be provided in the area between any adjacent four micro-recessed textures. Four oil return channels 13 are provided at a single exhaust hole 12, and the oil inlet holes 111 of the four oil return channels 13 are respectively located between regularly distributed micro-textures 30, so that the oil replenishing holes intersect with the micro-textures 30, maximizing the oil replenishing area.

[0047] In one embodiment, the cross-sectional area of the central shaft hole 11 is denoted as S1, that is, the opening area of the central shaft hole 11 is S1, and the cross-sectional area of a single groove is S2. (S2 / S1)*100% ≤ 5%. In this range, the effect of the micro-textures 30 can be optimized.

[0048] Specifically, for example, if a single micro-recessed texture is set as a semi-spherical shape, the range of the single radius r1 of the semi-spherical shape is 5 μm - 10 μm, and S2 = πr². At this time, it is only necessary to control the area of a single micro-recessed texture to be less than 5% of the area of the central shaft hole 11.

[0049] In one embodiment, along the opening direction of the exhaust hole 12, the diversion groove 121 extends spirally on the wall of the exhaust hole 12, that is, the diversion groove 121 forms a spiral groove structure. The air flow entering the exhaust hole 12, after changing the flow direction through the diversion member 20, rotates circumferentially and has a certain centrifugal force. Under the action of the centrifugal force, the oil carried in the air flow can be thrown onto the wall of the exhaust hole 12 and into the diversion groove 121 communicating with the diversion member 20. Under the action of the diversion groove 121, the oil thrown out by the centrifugal force is further strengthened in convergence, and finally the oil carried in the gas is returned to the central shaft hole 11 through the oil return channel 13 to provide lubrication for the rotating shaft.

[0050] In one embodiment, the flange body 10 is further provided with an oil collecting hole 14. The oil collecting hole 14 is arranged between the return diversion groove 121 and the oil return channel 13, and the diversion groove 121 is communicated with the oil return channel 13 through the oil collecting hole 14. The oil converged in the diversion groove 121 first flows into the oil collecting hole 14 uniformly, and then flows from the oil collecting hole 14 to the oil return channel 13.

[0051] Further, the oil collecting hole 14 is opened along the thickness direction L1 of the flange body 10. The connection position of the oil collecting hole 14 and the diversion groove 121 is tangent to the maximum diameter of the diversion groove 121 to ensure that the oil in the diversion groove 121 can be introduced into the oil collecting hole 14. Due to a certain pressure of the exhaust air flow for oil collection, most of the air flow will continue to flow along the extension direction of the exhaust hole 12 at this time, avoiding the phenomenon that a large amount of air flow enters the oil collecting hole 14 and causes the oil to flow back into the diversion groove 121.

[0052] Specifically, the oil collecting hole 14 only needs to communicate the diversion groove 121 and the oil return channel 13. Its set length and set size are not limited, and it may not need to penetrate the flange body 10 completely. Preferably, the diameter of the oil collecting hole 14 can be the same as the grooving diameter of the diversion groove 121 to avoid the phenomenon that a large amount of air flow enters the oil collecting hole 14 due to the over-large oil collecting hole 14 and causes the oil to flow back into the diversion groove 121.

[0053] In one embodiment, the oil return channel 13 is in a straight line or an arc shape, avoiding bends in the oil return channel 13, so as to ensure the oil return rate and the oil return amount in the oil return channel 13. Specifically, when the oil return channel 13 is in a curved shape, the cross-sectional area of the oil return channel 13 at this time is denoted as S3, and the area relationship (S3 / S1)*100% ≤ 2% is defined. The curvature K of the oil return channel 13 is:

[0054]

[0055] The X value is the abscissa corresponding to each position of the oil return channel 13 with the plane passing through the center of the flange inner hole and the center plane of the exhaust hole 12 as the reference plane, the center of the flange inner hole as the coordinate origin, and the right and upward directions as the positive directions to establish a coordinate system.

[0056] Under the above area and curvature, the oil return effect and oil return rate generated by the oil return channel 13 are optimal.

[0057] Specifically, when the oil return channel 13 is linear, the cross-sectional area of the oil return channel 13 at this time is denoted as S3, and the area relationship (S3 / S1)*100% ≤ 1% is defined, and the inclination angle relative to the horizontal plane is set to 30°. At this time, the oil return effect and oil return rate generated by the oil return channel 13 are optimal.

[0058] In one embodiment, referring to Figure 3 and Figure 7 , the flow guide member 20 can be fixed on the inner wall of the central axis hole 11, and it has a flow guide surface 21 extending in a spiral shape. One end of the flow guide surface 21 is communicated with the flow guide groove 121. In the initial state, the air flow generally enters along the axial direction of the exhaust hole 12. After entering, it encounters the flow guide surface 21, and the flow guide surface 21 guides the air flow to rotate and rise in a spiral shape, thereby generating a centrifugal force to separate the liquid in the gas.

[0059] Specifically, the flow guide member 20 can be a flow guide piece formed by twisting in a twist shape along the extension direction of the exhaust hole 12, such as Figure 2 and Figure 3 , the extension height H2 of the flow guide piece is less than or equal to the thickness H of the flange body 10 to avoid the flow guide piece being too high and affecting the diversion effect. The diameter of the flow guide piece after twisting can just match the inner diameter of the exhaust hole 12, so that all the air flow entering the exhaust hole 12 is redirected by the flow guide member 20.

[0060] Furthermore, the flow guide piece has a certain spiral angle, and its angle range is within 0°-90°. The preferred angle is 60 degrees. At this angle, the gas-liquid separation effect generated by guiding the exhaust air flow is the best.

[0061] According to another aspect of the present application, a pump body 400 of a compressor 1000 is further provided. The pump body 400 includes a muffler 410, a lower flange 420, a lower cylinder 430, a sliding vane 440, a partition 450, an upper cylinder 460, and an upper flange 470 that are assembled and connected in sequence. The flange structure 100 of the oil return channel 13 is the upper flange 470 of the oil return channel 13 and / or the lower flange 420 of the oil return channel 13. The pump body 400 has an exhaust passage 480, and the exhaust passage 480 extends through from the lower flange 420 to the upper flange 470, and the exhaust hole 12 of the lower flange 420 forms the inlet end of the exhaust passage 480, and the exhaust hole 12 of the upper flange forms the outlet end of the exhaust passage 480.

[0062] Specifically, the flange structure 100 provided in the present application can be assembled as the upper flange 470 above the pump body 400 (with the compressor 1000 placed upright), or can be assembled as the lower flange 420 below the pump body 400, so as to effect the return of oil in the exhaust gas at the inlet end of the exhaust passage 480 of the pump body 400, or can also effect the return of oil in the exhaust gas at the outlet end of the exhaust passage 480 of the pump body 400. Thereby, the oil is returned to different positions of the crankshaft 500, improving the lubrication degree of the crankshaft 500.

[0063] Further, since one end of the crankshaft 500 close to the lower flange 420 is closer to the oil storage cavity 700, and one end of the crankshaft 500 close to the upper flange 470 is farther from the oil storage cavity 700, during the rotation of the crankshaft 500, the end of the crankshaft 500 close to the upper flange 470 is more prone to oil shortage. In practical applications, the number of oil return channels 13 of the upper flange can be appropriately increased to improve the oil replenishment amount and oil replenishment efficiency for the end of the crankshaft 500 far from the lower flange 420.

[0064] It can be understood that the exhaust passage 480 provided on the pump body 400 extends from the lower flange 420 to the upper flange. Then, in addition to the exhaust holes 12 formed by the upper flange and the lower flange 420, communication through holes communicating with the exhaust holes 12 on the upper flange 470 and the lower flange 420 are provided on the lower cylinder 430, the sliding vane 440, the partition plate 450, and the upper cylinder 460, so as to enable the pump body 400 to form a complete exhaust passage 480 to discharge high-temperature and high-pressure gas during the operation of the compressor 1000.

[0065] In one embodiment, the crankshaft 500 of the compressor 1000 is rotatably disposed in the central shaft holes 11 of the upper flange 470 and the lower flange 420. Then, the crankshaft 500 of the compressor 1000 penetrates through from the lower flange 420 to the upper flange, and communication shaft holes communicating with the central shaft holes 11 on the upper flange 470 and the lower flange 420 are provided on the lower cylinder 430, the sliding vane 440, the partition plate 450, and the upper cylinder 460 passed through in the middle. Moreover, the formation of the oil return circuit, the setting of the micro-texture 30, and the setting of the diversion groove 121 provided in the present application are equally applicable to the lower cylinder 430, the sliding vane 440, the partition plate 450, the upper cylinder 460, and their communication shaft holes, so as to effect oil return to each position of the crankshaft 500 during the exhaust process of the entire exhaust passage 480.

[0066] It can be understood that since the oil gathering holes 14 communicate with the exhaust holes 12 and the oil return channels 13, oil gathering holes 14 are provided not only on the upper flange and the lower flange 420, but also communication oil holes communicating with the oil gathering holes 14 on the upper flange 470 and the lower flange 420 are provided on the lower cylinder 430, the sliding vane 440, the partition plate 450, and the upper cylinder 460, so as to enable the pump body 400 to communicate and form an oil gathering channel.

[0067] Specifically, when the compressor 1000 is placed upright, that is, when the oil storage cavity 700 is at the bottom, refer to Figure 6 , define L1 as the distance from the connection position of the oil return channel 13 and the oil collecting hole 14 to the geometric center of the central shaft hole 11, L2 as the distance from the lowest oil inlet hole 111 opened on the flange to the lower end surface of the flange body 10, L3 as the distance from the lowest oil inlet hole 111 opened on the flange to the lower end surface of the flange body 10, R1 as the radius of the central shaft hole 11, R2 as the radius of the oil collecting hole 14, H3 as the height of the exhaust passage 480, and C1 and C as the angles between the upward view projection of the trajectory line of different oil return channels 13 and the end surface projection passing through the central axis of the central shaft hole 11 and the central axis of the exhaust hole 12.

[0068] Then tanC = R1 / L1, tanC1 ≤ tanC. Let the total height of the flange body 10 be H, then 0.25*H ≤ L2 ≤ 1 / 3*H, 0.5*H ≤ L3 ≤ 4 / 5*H. The relationship between the cross-sectional area S3 of the oil return channel 13 and the cross-sectional area S4 of the oil collecting hole 14 is 0.0001 ≤ S3 ≤ S4, and S3 = πR2²; the relationship between the height H3 of the exhaust passage 480 and the radius R2 of the oil collecting hole 14 is as follows: 0.0001 ≤ R2 ≤ 0.5*H3, and preferably R2 = 0.15*H3.

[0069] In this way, within the above range, it can be known that the theoretical oil return effect is better.

[0070] The flange structure 100, the pump body 400, and the compressor 1000 provided by this application can form an oil return circuit between the exhaust passage 480 and the central shaft hole 11 to supplement oil to the crankshaft 500 in the central shaft hole 11, avoiding a large amount of oil being taken out of the compressor 1000 due to the exhaust of the exhaust passage 480, thereby improving the rotational lubrication degree of the crankshaft 500 of the compressor 1000 and reducing wear, and further improving the reliability of the compressor 1000.

[0071] The technical features of the above embodiments can be combined arbitrarily. For the sake of brevity of description, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, it should be considered as the scope recorded in this specification.

[0072] The above embodiments only represent several implementation manners of this application, and their descriptions are relatively specific and detailed, but they should not be construed as limiting the scope of the patent application. It should be noted that for those of ordinary skill in the art, without departing from the concept of this application, several deformations and improvements can still be made, and these all belong to the protection scope of this application. Therefore, the protection scope of the patent of this application should be subject to the appended claims.

Claims

1. A flange structure, characterized in that, Comprising: A flange body (10) having a central shaft hole (11) and an exhaust hole (12) penetrating therethrough along its thickness direction (L1), the central shaft hole (11) and the exhaust hole (12) being arranged at a radial interval along the flange body (10); A flow guide member (20) disposed in the exhaust hole (12) for guiding the gas in the exhaust hole (12) to flow in a circumferential shape; Wherein, the flange body (10) is further provided with an oil return channel (13), a flow guide groove (121) is provided on the wall of the exhaust hole (12), the flow guide member (20) is communicated with the flow guide groove (121), and the flow guide groove (121) is communicated with the central shaft hole (11) through the oil return channel (13).

2. The flange structure according to claim 1, wherein The flow guide member (20) has a flow guide surface (21) extending in a spiral shape, and one end of the flow guide surface (21) is communicated with the flow guide groove (121).

3. The flange structure according to claim 1, characterized in that, A micro-texture (30) is provided on the wall of the central shaft hole (11).

4. The flange structure according to claim 3, wherein The micro-texture (30) includes a plurality of micro-recessed textures recessed on the wall of the central shaft hole (11) arranged in a matrix, and an oil inlet hole (111) communicated with the oil return channel (13) is further provided on the wall of the central shaft hole (11), and the oil inlet hole (111) is located between all the micro-recessed textures.

5. The flange structure according to claim 4, characterized in that, The cross-sectional area of the central shaft hole (11) is S1, and the cross-sectional area of a single micro-recessed texture is S2, (S2 / S1)*100% ≤ 5%.

6. The flange structure according to claim 1, characterized in that Along the opening direction of the exhaust hole (12), the flow guide groove (121) extends in a spiral shape on the wall of the exhaust hole (12).

7. The flange structure according to claim 1, characterized in that, The flange body (10) is further provided with an oil collecting hole (14), the oil collecting hole (14) is disposed between the flow guide groove (121) and the oil return channel (13), and the flow guide groove (121) is communicated with the oil return channel (13) through the oil collecting hole (14).

8. The flange structure according to claim 7, characterized in that, The oil collecting hole (14) is opened along the thickness direction (L1) of the flange body (10).

9. The flange structure according to claim 1, characterized in that, The oil return channel (13) is linear or arc-shaped.

10. A pump body of a compressor, characterized in that, Including a crankshaft (500) of a compressor (1000) and the flange structure (100) according to any one of claims 1-9, the crankshaft (500) is rotatably disposed in the central shaft hole (11); The pump body (400) has an exhaust passage (480), and the exhaust hole (12) is a part of the exhaust passage (480).

11. The pump body of the compressor according to claim 10, characterized in that, The pump body (400) includes a lower flange (420), a lower cylinder (430), a sliding vane (440), a partition plate (450), an upper cylinder (460) and an upper flange (470) assembled and connected in sequence, the flange structure (100) is the upper flange (470) and / or the lower flange (420), and the pump body (400) has an exhaust passage (480); The exhaust passage (480) extends through the lower flange (420) to the upper flange (470), and the exhaust hole (12) of the lower flange (420) forms the inlet end of the exhaust passage (480), and the exhaust hole (12) of the upper flange (470) forms the outlet end of the exhaust passage (480).

12. A compressor, characterized in that, A pump body (400) according to any one of claims 10-11, including a housing (200) and a motor (300). The pump body (400) and the motor (300) are both assembled in the housing (200), and an oil storage chamber (700) is formed between the pump body (400) and the housing (200).

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