Flange structure, pump body assembly and compressor

Abstract

The invention discloses a flange structure, a pump body assembly and a compressor. The flange structure comprises a flange journal and a flange plate which are connected with each other, a through hole is formed in the flange journal in the vertical direction, the flange plate is located at the bottom of the through hole and provided with an oil storage groove communicated with the through hole, a spiral groove is formed in the hole wall of the through hole, the lower end of the spiral groove extends to the oil storage groove, and the upper end of the spiral groove extends to the upper end face of the flange journal. The spiral groove is formed in the hole wall of the through hole of the flange shaft neck, so that lubricating oil is conveyed and distributed more effectively; when the compressor runs, lubricating oil flows into the oil storage tank and then enters the spiral groove, due to the design of the spiral groove, the lubricating oil can form a certain dynamic pressure effect in the flowing process, the pressure and thickness of an oil film are increased, and therefore the lubricating effect of the bearing is improved; in addition, the continuity of the spiral groove ensures that lubricating oil is uniformly distributed on the surface of the flange journal, and the situation of insufficient local lubrication is avoided.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a flange structure, a pump body assembly and a compressor. Background Art

[0002] As a key component in refrigeration and air-conditioning systems, the operating principle of the rolling rotor compressor is based on a carefully designed mechanical structure. Specifically, the compressor consists of a cylindrical cylinder with a cylindrical roller positioned inside, coinciding with its center. The roller's rotational power comes from the motor, which is driven by the eccentric circle of the crankshaft, causing the roller to rotate inside the cylinder. To achieve effective compression and discharge of gas, a sliding vane groove is designed in the cylinder, in which a sliding vane that can slide back and forth is installed. One end of the sliding vane is maintained in close contact with the circumference of the roller by a pump spring, thereby forming a high-pressure chamber and a low-pressure chamber between the inner surface of the cylinder, the outer surface of the roller, the sliding vane, and the upper and lower flange end faces. As the roller rotates, the compressor draws gas from the low-pressure chamber and discharges the compressed gas into the high-pressure chamber, completing a complete working cycle. This process is repeated continuously under the continuous drive of the motor.

[0003] In the structure of a rolling rotor compressor, the upper and lower flanges not only separate the high- and low-pressure chambers, but their necks also serve the important function of forming a sliding bearing with the crankshaft to support the crankshaft's rotation. Therefore, ensuring effective lubrication of the inner wall of the flange neck is crucial for reducing friction between the flange and the crankshaft and lowering the compressor's power consumption. Existing technology typically involves opening a central oil hole in the center of the crankshaft and designing oil grooves on the inner wall of the flange. Lubricating oil is then pumped to the ends of the inner circular surfaces of the lower and upper flanges through the side oil holes at the roots of the major and minor axes of the crankshaft. The lubricating oil is then transported through the oil grooves on the flanges to the friction pair surfaces where the flanges contact the crankshaft, thereby achieving oil circuit lubrication of the primary and secondary bearings.

[0004] However, as the compressor's operating frequency increases, the need for lubrication between the contact surfaces of moving parts also increases accordingly, especially between the crankshaft and the upper flange, placing higher demands on the lubricant supply. Insufficient lubrication will lead to increased friction, generating a large amount of heat, which in turn causes a rapid increase in pump body temperature. This not only heats the cylinder working chamber, reducing the compressor's volumetric efficiency, but also causes a sharp increase in exhaust temperature, affecting the operating efficiency of the motor and ultimately leading to a decline in the compressor's overall performance.

[0005] As a core component of the compressor pump body, optimizing the flange design is crucial for ensuring adequate bearing lubrication and reducing frictional power loss and the resulting temperature rise. Therefore, developing new technologies or solutions that effectively enhance lubrication between the flange and the crankshaft is crucial for improving the operating efficiency and stability of rolling rotor compressors. Summary of the Invention

[0006] The purpose of the present invention is to overcome the deficiencies of the prior art and to provide a flange structure, a pump assembly and a compressor.

[0007] In order to solve the above technical problems, the present invention adopts the following technical solutions:

[0008] In the first aspect, an embodiment of the present invention provides a flange structure, comprising a flange neck and a flange plate connected to each other, wherein the flange neck is provided with a through hole in a vertical direction, the flange plate is located at the bottom of the through hole, and is provided with an oil storage tank connected to the through hole, the hole wall of the through hole is provided with a spiral groove, and the lower end of the spiral groove extends to the oil storage tank, and the upper end extends to the upper end surface of the flange neck.

[0009] In a specific embodiment, the spiral groove spirals upward from the lower end surface of the hole wall, and forks in two different directions at the middle section of the flange shaft neck and continues to spiral upward to the upper end surface of the flange shaft neck to form a lower end spiral oil groove, a first spiral oil groove and a second spiral oil groove. The lower end spiral oil groove, the first spiral oil groove and the second spiral oil groove are combined to form a Y shape.

[0010] In a specific embodiment, the phase angle difference between the first spiral oil groove and the second spiral oil groove is 120°.

[0011] In a specific embodiment, the first spiral oil groove and the second spiral oil groove have the same groove width and groove depth.

[0012] In a specific embodiment, the groove width and groove depth of the lower spiral oil groove are greater than those of the first spiral oil groove.

[0013] In a specific embodiment, the flange is located on the outer periphery of the oil storage tank and is provided with a flexible groove communicating with the oil storage tank.

[0014] In a specific embodiment, the thickness of the flexible groove is not less than 2 mm, and the depth is not more than 4 mm.

[0015] In a specific embodiment, a third spiral oil groove is further provided on the side of the first spiral oil groove or the second spiral oil groove;

[0016] Or a lower end additional oil groove is further provided on one side of the lower end spiral oil groove, so that the lower end spiral oil groove, the lower end additional oil groove, the first spiral oil groove and the second spiral oil groove are combined to form an X shape.

[0017] The flange structure of the present invention has the following advantages compared with the prior art: by providing a spiral groove on the wall of the through hole of the flange journal, more effective delivery and distribution of lubricating oil is achieved; when the compressor is running, the lubricating oil flows to the oil storage tank and then enters the spiral groove. Due to the design of the spiral groove, the lubricating oil can form a certain dynamic pressure effect during the flow process, increasing the pressure and thickness of the oil film, thereby significantly improving the lubrication effect of the bearing; in addition, the continuity of the spiral groove ensures the uniform distribution of the lubricating oil on the surface of the flange journal, avoiding the situation of local insufficient lubrication.

[0018] In a second aspect, an embodiment of the present invention provides a pump body assembly, comprising the flange structure as described above and a crankshaft connected to the flange structure, wherein the crankshaft is provided with an oil guide hole, and the oil guide hole is connected to the oil storage tank.

[0019] The pump body assembly of the present invention has the following beneficial effects compared with the prior art: by applying the flange structure mentioned above, not only the pressure and thickness of the oil film are increased, but also the lubrication effect of the bearing is significantly improved; in addition, the design of the spiral groove not only promotes the flow of lubricating oil, but also forms a more uniform oil film on the surface of the flange journal through its unique geometric shape. This evenly distributed oil film can more effectively reduce the friction between the flange bearing and the crankshaft, reduce wear, and extend the service life of the bearing; at the same time, the uniform oil film thickness also helps to maintain the stable operation of the bearing and reduce vibration and noise caused by uneven lubrication.

[0020] In a third aspect, an embodiment of the present invention provides a compressor comprising the pump body assembly as described above.

[0021] The compressor of the present invention has the following beneficial effects compared with the prior art: by applying the pump body assembly mentioned above, the lubrication effect and uniformity of the oil film thickness of the flange bearing are improved, and the friction and wear of the bearing during operation can be significantly reduced. This not only reduces the heat generated by friction, lowers the temperature of the pump body and the cylinder working chamber, but also improves the volumetric efficiency and operating stability of the compressor; in addition, the reduction in friction and wear also directly reduces the power consumption of the compressor and improves energy utilization efficiency.

[0022] The present invention will be further described below with reference to the accompanying drawings and specific embodiments. BRIEF DESCRIPTION OF THE DRAWINGS

[0023] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the following briefly introduces the drawings required for use in the embodiments or the description of the prior art. Obviously, the drawings described below are only some embodiments of the present invention. For ordinary technicians in this field, other drawings can be obtained based on these drawings without paying any creative work.

[0024] Figure 1A perspective schematic diagram of a first embodiment of a flange structure provided by the present invention;

[0025] Figure 2 A bottom view schematically showing a first embodiment of a flange structure provided by the present invention;

[0026] Figure 3 A schematic cross-sectional view of a first embodiment of a flange structure provided by the present invention;

[0027] Figure 4 for Figure 3 A partial enlarged schematic diagram;

[0028] Figure 5 A schematic cross-sectional view of a spiral groove in a second embodiment of a flange structure provided by the present invention;

[0029] Figure 6 A schematic cross-sectional view of a spiral groove in a third embodiment of a flange structure provided by the present invention;

[0030] Figure 7 A schematic cross-sectional view of the pump assembly provided by the present invention;

[0031] Figure 8 for Figure 7 A partial enlarged schematic diagram of B in the figure.

[0032] Reference numerals:

[0033] Flange journal 10, spiral groove 11, lower end spiral oil groove 111, first spiral oil groove 112, second spiral oil groove 113, third spiral oil groove 114, lower end additional oil groove 115, flange plate 20, oil storage groove 21, flexible groove 22, crankshaft 30, oil guide hole 31. DETAILED DESCRIPTION

[0034] In order to make the purpose, technical solutions and advantages of the present invention more clear, the present invention is further described in detail below with reference to the accompanying drawings and specific embodiments.

[0035] The following will clearly and completely describe the technical solutions in the embodiments of the present invention in conjunction with the accompanying drawings. Obviously, the described embodiments are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without making any creative efforts shall fall within the scope of protection of the present invention.

[0036] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0037] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature identified as "first" or "second" may explicitly or implicitly include one or more of the features. In the description of the present invention, "plurality" means two or more, unless otherwise specifically defined.

[0038] In the present invention, unless otherwise expressly specified or limited, terms such as "mounted," "connected," "connect," and "fixed" should be understood broadly. For example, they may refer to connection, detachable connection, or integration; mechanical connection or electrical connection; direct connection or indirect connection through an intermediate medium; and internal communication between two components or interaction between two components. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0039] In the present invention, unless otherwise expressly specified or limited, a first feature being "above" or "below" a second feature may include the first and second features being in direct contact, or may include the first and second features being in contact not directly but through another feature between them. Furthermore, a first feature being "above," "above," and "above" a second feature may include the first feature being directly above or obliquely above the second feature, or may simply mean that the first feature is higher in level than the second feature. A first feature being "below," "below," and "below" a second feature may include the first feature being directly below or obliquely below the second feature, or may simply mean that the first feature is lower in level than the second feature.

[0040] In the description of this specification, the reference terms "one embodiment", "some embodiments", "example", "specific example", or "some examples" mean that the specific features, structures, materials or characteristics described in conjunction with the embodiment or example are included in at least one embodiment or example of the present invention. In this specification, the schematic expressions of the above terms should not be understood as necessarily referring to the same embodiment or example. Moreover, the specific features, structures, materials or characteristics described can be combined in any one or more embodiments or examples in a suitable manner. In addition, those skilled in the art can combine and combine different embodiments or examples described in this specification.

[0041] See also Figures 1 to 6 As shown, the present invention discloses a specific embodiment of a flange structure, including a flange neck 10 and a flange plate 20 connected to each other, the flange neck 10 is provided with a through hole in the vertical direction, the flange plate 20 is located at the bottom of the through hole, and is provided with an oil storage tank 21 connected to the through hole, the hole wall of the through hole is provided with a spiral groove 11, and the lower end of the spiral groove 11 extends to the oil storage tank 21, and the upper end extends to the upper end surface of the flange neck 10.

[0042] Specifically, by opening a spiral groove 11 on the wall of the through hole of the flange journal 10, more effective delivery and distribution of the lubricating oil is achieved; when the compressor is running, the lubricating oil flows to the oil storage tank 21 and then enters the spiral groove 21. Due to the design of the spiral groove 11, the lubricating oil can form a certain dynamic pressure effect during the flow process, increasing the pressure and thickness of the oil film, thereby significantly improving the lubrication effect of the bearing; in addition, the continuity of the spiral groove 11 ensures the uniform distribution of the lubricating oil on the surface of the flange journal 10, avoiding the situation of local insufficient lubrication.

[0043] See also Figures 1 to 4 In the first embodiment shown, the spiral groove 11 spirally rises from the lower end surface of the hole wall, and forks in two different directions at the middle section of the flange journal 10 and continues to spiral upward to the upper end surface of the flange journal 10 to form a lower spiral oil groove 111, a first spiral oil groove 112 and a second spiral oil groove 113. The lower spiral oil groove 111, the first spiral oil groove 112 and the second spiral oil groove 113 are combined to form a Y shape.

[0044] Specifically, when the oil is carried to the oil guide hole as the crankshaft rotates, and then flows from the oil guide hole into the oil storage tank 21, since the spiral groove 11 extends to the oil storage tank 21, under the action of oil pressure, the oil flows into the cross-spiral oil groove and then lubricates the bearing. That is, by setting up the cross-oil groove, the distribution path of the oil is increased. With the help of the dynamic pressure effect, the oil enters the contact area from multiple directions, thereby reducing the problem of uneven oil film thickness. The distribution of oil in multiple directions also reduces the oil loss caused by a single flow direction, and to a certain extent ensures the uniformity of the oil film thickness. In addition, the flow of oil in multiple directions can better remove heat and reduce local overheating. The change and increase in the flow direction of the oil also reduces the retention of oil, improves the fluidity of the oil, and enables the oil to respond to motion changes more quickly and form a stable oil film, especially under low-frequency conditions.

[0045] More specifically, through the bifurcation and Y-shaped design of the spiral groove 11, the oil is guided into the contact area from multiple directions, effectively reducing the problem of uneven oil film thickness. In addition, the multi-directional oil flow not only increases the lubrication area, but also improves the load-bearing capacity and stability of the oil film through the dynamic pressure effect. Especially under low-frequency working conditions, it can respond to motion changes more quickly and form a stable oil film. In addition, the flow of oil in multiple directions improves the efficiency of heat conduction, can more effectively carry away heat, reduce the risk of local overheating, and help maintain the normal operating temperature of mechanical components. In addition, by changing the flow direction of the oil and increasing the flow path, the problem of oil loss caused by a single flow direction is reduced, and the efficiency of the lubrication system is improved. In addition, the diversity of the oil flow direction and the increase in the path reduce the retention of oil, allowing the oil to flow more smoothly and respond more quickly, thereby optimizing the overall lubrication performance.

[0046] In one embodiment, the phase angle difference between the first spiral oil groove 112 and the second spiral oil groove 113 is 120°.

[0047] Specifically, the phase angles of the first spiral oil groove 112 and the second spiral oil groove 113 are designed to differ by 120°, which can ensure that the oil is more evenly distributed on the surface of the flange journal 10. This even distribution helps to reduce local insufficient lubrication or excessively thick oil film, thereby improving the overall lubrication effect. In addition, by optimizing the phase angle of the spiral groove 11, the stability of the oil film on the surface of the flange journal 10 can be enhanced. During the operation of the compressor, this stable oil film can better withstand the friction and wear between the journal and the bearing, extending the service life of the mechanical components. In addition, the reasonable design of the phase angle can also help optimize the flow path of the oil on the surface of the flange journal 10, thereby more effectively carrying away the heat generated by friction, which helps to reduce the operating temperature of the journal and bearing, and improve the operating efficiency and stability of the compressor. In addition, in the design of the spiral groove 11, the difference in phase angle can produce a stronger dynamic pressure effect, which helps to form a more stable oil film between the journal and the bearing, further improving the lubrication effect and load-bearing capacity.

[0048] In one embodiment, the first spiral oil groove 112 and the second spiral oil groove 113 have the same groove width and groove depth.

[0049] Specifically, since the groove width and groove depth of the first spiral oil groove 112 and the second spiral oil groove 113 are equal, the obstruction or deviation of the lubricating oil flow due to structural differences is avoided, which helps to ensure the uniform distribution and smooth flow of the lubricating oil in the two spiral oil grooves. In addition, the two spiral oil grooves with the same structure can more effectively utilize the dynamic pressure effect to form a stable oil film between the shaft neck and the bearing. This stable oil film helps to reduce friction and wear and improve the operating efficiency and stability of the compressor. In addition, the use of the same groove width and groove depth design can simplify the design and manufacturing process of the spiral oil grooves, reduce production costs and time; at the same time, it also helps to improve the manufacturability and consistency of the product. In addition, the uniform flow of lubricating oil and the stable oil film help to reduce friction and wear of mechanical parts, thereby extending their service life, which is of great significance to improving the reliability and durability of the compressor.

[0050] In one embodiment, the groove width and groove depth of the lower spiral oil groove 111 are greater than those of the first spiral oil groove 112 .

[0051] Specifically, the larger groove width and groove depth of the lower spiral oil groove 111 can accommodate more lubricating oil, thereby quickly filling the entire lubrication system when the bearing starts, which helps to reduce dry friction during startup and extend the service life of the bearing. In addition, the lower spiral oil groove 111 acts as a "reservoir" for lubricating oil and can continuously provide sufficient oil to the upper first spiral oil groove 112 and second spiral oil groove 113, which ensures that the upper spiral oil groove always maintains sufficient lubrication during the operation of the bearing, helps to form a stable oil film, and reduces friction and wear. In addition, by increasing the groove width and groove depth of the lower spiral oil groove 111, the lubrication conditions of the bearing can be improved and the lubrication effect can be enhanced, which helps to reduce the operating temperature of the bearing, reduce energy loss, and improve the operating efficiency and stability of the compressor.

[0052] In one embodiment, the flange 20 is located on the outer periphery of the oil storage tank 21 and is provided with a flexible groove 22 communicating with the oil storage tank 21 .

[0053] Specifically, the cross-sectional combination of the oil storage tank 21 and the flexible groove 22 presents a "concave" shape, and the flexible groove 22 is connected to the oil storage tank 21, mainly to reduce the contact stress between the crankshaft and the hole wall, thereby reducing wear. The main principle is that after adding the flexible groove 22, not only the contact line length between the crankshaft and the hole wall is reduced, but also the oil entering the flexible groove 22 will act on the groove wall of the flexible groove 22, thereby reducing the force of the crankshaft on the hole wall to a certain extent.

[0054] That is, the design of the flexible groove 22 reduces the length of the contact line between the crankshaft and the hole wall during rotation, thereby reducing the contact stress, which helps to reduce wear and fatigue damage caused by stress concentration. In addition, when the crankshaft rotates, the lubricating oil flows from the oil storage tank 21 into the flexible groove 22 and acts on the groove wall of the flexible groove 22, which to a certain extent reduces the force exerted by the crankshaft on the hole wall, thereby reducing wear. In addition, the deformation capacity of the flexible groove 22 also helps to absorb some impact and vibration energy, further reducing wear. In addition, the connection design of the oil storage tank 21 and the flexible groove 22 allows the lubricating oil to be more effectively distributed between the crankshaft and the hole wall, forming a more uniform oil film, which helps to improve the lubrication effect and reduce friction and energy loss. In addition, by reducing contact stress and reducing wear, the design of the flexible groove 22 helps to improve the durability and reliability of mechanical components, which helps to extend the service life of the equipment and reduce maintenance and replacement costs.

[0055] In one embodiment, the thickness of the flexible groove 22 is not less than 2 mm, and the depth is not greater than 4 mm.

[0056] Specifically, if the thickness of the flexible groove 22 is too small, it will cause insufficient rigidity and there may be a risk of breakage during high-frequency operation; if the groove is too deep, too much oil will enter the flexible groove 22, affecting the amount of oil entering the bearing, and even affecting the oil film thickness at low frequencies. Therefore, the wall thickness of the flexible groove 22 should not be too small, and the groove depth should not be too large.

[0057] That is to say, by ensuring that the thickness of the flexible groove 22 is not less than 2 mm, the rigidity of the flexible groove 22 during high-frequency operation is improved, and the risk of fracture due to insufficient rigidity is avoided, which helps to extend the service life of the flexible groove 22 and improve the reliability of the equipment. In addition, by setting the groove depth of the flexible groove 22 to no more than 4 mm, excessive oil is prevented from entering the flexible groove 22 and affecting the amount of oil entering the bearing. This ensures that the bearing can maintain a sufficient oil film thickness during low-frequency operation, ensures good lubrication, and reduces friction and wear. In addition, a reasonable design of the flexible groove 22 not only improves the lubrication effect, but also enhances the durability of mechanical components. By reducing friction and wear, it extends the service life of the equipment and reduces maintenance and replacement costs. In addition, a reasonable design of the flexible groove 22 helps to absorb some impact and vibration energy, improves the stability of the equipment, and helps to reduce failures and damage caused by vibration and impact, thereby improving the overall performance of the equipment.

[0058] In one embodiment, the cross-sectional shape of the spiral oil groove may be a fan-shaped, trapezoidal, rectangular or other polygonal shapes; among which the fan-shaped is preferred.

[0059] Specifically, the fan-shaped cross-section gradually accelerates the oil as it flows, improving its fluidity. This acceleration helps deliver the oil more efficiently to the areas requiring lubrication. Furthermore, because the fan-shaped spiral oil grooves enhance fluidity, they deliver more oil to the contact surfaces between rotating and stationary components, enhancing lubrication and reducing friction and wear. Furthermore, optimizing the cross-sectional shape of the spiral oil grooves can improve overall equipment performance, including reducing energy consumption, increasing operational efficiency, and extending service life.

[0060] In addition, the trapezoidal cross-section may improve the fluidity of the oil to a certain extent, but its effect may not be as significant as that of the fan-shaped cross-section. In addition, the machining difficulty of the trapezoidal spiral oil groove may be relatively low.

[0061] In addition, the rectangular cross-section is simple and clear, and easy to process, but it may not be as effective as the fan-shaped and trapezoidal shapes in improving oil fluidity.

[0062] In addition, the spiral oil groove with a polygonal cross-section may have a special lubrication effect or structural strength, but its design and processing difficulty may be relatively high, and its performance in different application scenarios may vary.

[0063] See also Figure 5 In the second embodiment shown, a third spiral oil groove 114 is further provided on the side of the first spiral oil groove 112 or the second spiral oil groove 113 .

[0064] Specifically, on the basis of the Y-shaped spiral groove 11, a third spiral oil groove 114 is further provided to further increase the flow direction of the oil, increase the uniformity of the oil film, and improve the lubrication effect.

[0065] In other words, the addition of the third spiral oil groove 114 provides more flow paths and directions for the oil, which helps to form a more complex and uniform oil flow network within the bearing, thereby improving lubrication efficiency. Furthermore, by adding the third spiral oil groove 114, the oil can be more evenly distributed across the contact surface of the bearing, which helps to form a more stable and uniform oil film, reducing friction and wear caused by uneven oil film. Furthermore, the addition of the third spiral oil groove 114 significantly improves the lubrication effect of the bearing, not only reducing friction and wear, but also lowering the operating temperature and energy consumption of the bearing, thereby increasing the bearing's service life and reliability.

[0066] See also Figure 6 In the third embodiment shown, a lower additional oil groove 115 is further provided on one side of the lower spiral oil groove 111, so that the lower spiral oil groove 111, the lower additional oil groove 115, the first spiral oil groove 112 and the second spiral oil groove 113 are combined to form an X shape.

[0067] Specifically, on the basis of the Y-shaped spiral groove 11, an oil groove 115 is added at the lower end to form an X-shaped oil groove, which can also improve the uniformity of the oil film thickness to a certain extent and enhance the lubrication effect.

[0068] In other words, the X-shaped oil groove layout increases the flow path and direction of the oil, allowing the oil to be more evenly distributed on the bearing contact surface. This helps form a more stable and uniform oil film thickness, reducing friction and wear caused by uneven oil film. Furthermore, the X-shaped oil groove layout significantly improves the bearing's lubrication performance. It not only reduces friction and wear, but also lowers the bearing's operating temperature and energy consumption, thereby increasing the bearing's service life and reliability. Furthermore, the X-shaped oil groove layout optimizes the oil's circulation path within the bearing, which helps speed up oil renewal and improves the efficiency of the lubrication system. Furthermore, the X-shaped oil groove layout design enables the bearing to better adapt to the lubrication needs of complex operating conditions. Whether operating at high speeds or under heavy loads, it provides stable and efficient lubrication.

[0069] See also Figures 7 and 8As shown, the present invention further discloses a pump body assembly, including the flange structure as described above and a crankshaft 30 connected to the flange structure, wherein the crankshaft 30 is provided with an oil guide hole 31 , and the oil guide hole 31 is connected to the oil storage tank 21 .

[0070] Specifically, when the oil is brought to the oil guide hole 31 as the crankshaft 30 rotates, it flows from the oil guide hole 31 into the oil storage tank 21 and then into the flexible groove 22. Since the spiral groove 11 extends to the oil storage tank 21, under the action of oil pressure, the oil flows into the cross spiral oil groove and lubricates the bearings.

[0071] That is to say, by applying the flange structure mentioned above, the pump body assembly not only increases the pressure and thickness of the oil film, but also significantly improves the lubrication effect of the bearing; in addition, the design of the spiral groove 11 not only promotes the flow of lubricating oil, but also forms a more uniform oil film on the surface of the flange journal 10 through its unique geometric shape. This evenly distributed oil film can more effectively reduce the friction between the flange bearing and the crankshaft 30, reduce wear, and extend the service life of the bearing; at the same time, the uniform oil film thickness also helps to maintain the stable operation of the bearing and reduce vibration and noise caused by uneven lubrication.

[0072] The present invention also discloses a compressor, comprising the pump body assembly described above.

[0073] Specifically, by applying the pump body assembly mentioned above, the lubrication effect and uniformity of the oil film thickness of the flange bearing are improved, which can significantly reduce the friction and wear of the bearing during operation. This not only reduces the heat generated by friction, lowers the temperature of the pump body and the cylinder working chamber, but also improves the volumetric efficiency and operating stability of the compressor; in addition, the reduction in friction and wear also directly reduces the power consumption of the compressor and improves energy utilization efficiency.

[0074] The above embodiments are preferred implementation schemes of the present invention. In addition, the present invention can also be implemented in other ways. Any obvious replacement without departing from the concept of the present technical solution is within the scope of protection of the present invention.

Claims

1. A flange structure comprising a flange journal and a flange plate connected to each other, characterized in that: The flange journal is provided with a through hole in the vertical direction, the flange plate is located at the bottom of the through hole, and is provided with an oil storage tank connected to the through hole, the hole wall of the through hole is provided with a spiral groove, and the lower end of the spiral groove extends to the oil storage tank, and the upper end extends to the upper end surface of the flange journal.

2. The flange structure according to claim 1, characterized in that: The spiral groove spirally rises upward from the lower end surface of the hole wall, and forks in the middle section of the flange journal and continues to spiral upward in two different directions to the upper end surface of the flange journal to form a lower end spiral oil groove, a first spiral oil groove and a second spiral oil groove. The lower end spiral oil groove, the first spiral oil groove and the second spiral oil groove are combined to form a Y shape.

3. The flange structure according to claim 2, characterized in that: The phase angle difference between the first spiral oil groove and the second spiral oil groove is 120°.

4. The flange structure according to claim 2, characterized in that: The first spiral oil groove and the second spiral oil groove have the same groove width and groove depth.

5. The flange structure according to claim 4, characterized in that: The groove width and groove depth of the lower end spiral oil groove are greater than those of the first spiral oil groove.

6. The flange structure according to claim 1, characterized in that: The flange is located on the outer periphery of the oil storage tank and is provided with a flexible groove communicated with the oil storage tank.

7. The flange structure according to claim 6, characterized in that: The thickness of the flexible groove is not less than 2 mm, and the depth is not more than 4 mm.

8. The flange structure according to claim 2, characterized in that: A third spiral oil groove is further provided on the side of the first spiral oil groove or the second spiral oil groove; Or a lower end additional oil groove is further provided on one side of the lower end spiral oil groove, so that the lower end spiral oil groove, the lower end additional oil groove, the first spiral oil groove and the second spiral oil groove are combined to form an X shape.

9. A pump assembly, characterized in that: It comprises the flange structure according to any one of claims 1 to 8 and a crankshaft connected to the flange structure, wherein the crankshaft is provided with an oil guide hole, and the oil guide hole is connected to the oil storage tank.

10. A compressor, characterized in that: Comprising the pump body assembly as claimed in claim 9.

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