Flange, pump body assembly, rotary compressor and air conditioner

Abstract

The present invention provides a flange, a pump body assembly, a rotary compressor and an air conditioner. The flange includes a flange body, and a bearing hole for inserting a crankshaft is formed on the flange body. A damping ring groove is formed on the orifice wall of the bearing hole close to the side of the eccentric part of the crankshaft. A spiral oil guiding groove is formed on the hole wall of the bearing hole. The spiral oil guiding groove includes a first groove section on a first hole section and a second groove section on a second hole section. The maximum groove width of the second groove section and the maximum groove depth of the first groove section are smaller than the minimum groove depth of the second groove section. According to the present invention, the spiral oil guiding groove on the first hole section, that is, the first groove section, is designed as a shallow groove structure, so that the outer ring groove wall of the damping ring groove can be closer to the bearing hole, thereby increasing the sealing distance at the matching position between the end of the flange body and the roller, improving the volumetric efficiency of the pump body structure, and at the same time facilitating the prevention of the chipping phenomenon caused by the too small wall thickness between the damping ring groove and the bearing hole.

Description

Technical Field

[0001] The present invention belongs to the technical field of compressor manufacturing, and particularly relates to a flange, a pump body assembly, a rotary compressor and an air conditioner. Background Art

[0002] With the improvement of people's living standards, people have higher and higher requirements for environmental comfort, and air conditioners have almost become a necessity for every household. The rotary compressor is widely used in the field of household air conditioners due to its low manufacturing cost and low price. With the improvement of people's environmental protection awareness, more efficient rotary compressors have become the general choice of major air conditioner manufacturers, and major compressor manufacturers are all committed to developing more efficient rotary compressors.

[0003] Currently, the main development directions of rotary compressors are high efficiency and cost reduction, and miniaturization is an important solution. In the prior art, leakage is avoided by controlling the sealing distance between the flexible groove of the flange and the outer diameter of the roller; however, miniaturization leads to a decrease in the shell diameter and cylinder diameter. In order to improve the volumetric efficiency, the eccentricity of the crankshaft is designed to be increased, which in turn leads to a thinner wall thickness of the roller, which conflicts with controlling the sealing distance between the flexible groove of the flange and the outer diameter of the roller to avoid leakage. The flexible groove is also called a damping groove, and its main function is that under high load, the deflection change of the crankshaft causes the inner diameter of the flange to deform moderately, which helps to form a thicker oil film. This design is generally applied to large-series flanges and flanges of some high-efficiency models. Therefore, how to solve the above design contradiction problems in large-series flanges and flanges of some high-efficiency models has also become an urgent problem for those skilled in the art to solve.

[0004] Another problem existing in the prior art is that the wall thickness of the flexible groove is reduced, which will directly affect the depth of the oil guiding groove. For example, if the oil groove is too deep, there is a thin wall between the flexible groove and the oil guiding groove, which is prone to chipping; if the oil groove is too shallow, the oil pumping ability of the crankshaft is weak, which will affect the reliability of the pump body. Summary of the Invention

[0005] Therefore, the present invention provides a flange, a pump body assembly, a rotary compressor and an air conditioner to overcome the deficiency in the prior art that the minimum sealing distance between the damping ring groove of the flange and the outer diameter of the roller is too small, resulting in too thin wall thickness at the corresponding position between the damping ring groove and the spiral oil guiding groove and prone to chipping.

[0006] To solve the above problems, the present invention provides a flange, including a flange body, on which a bearing hole for inserting a crankshaft is formed. A damping ring groove is formed on the orifice wall of the bearing hole near the side where the eccentric part of the crankshaft is located. A spiral oil guiding groove is formed on the wall of the bearing hole. The spiral oil guiding groove includes a first groove section on a first hole section and a second groove section on a second hole section. The maximum groove width of the second groove section and the maximum groove depth of the first groove section are less than the minimum groove depth of the second groove section. Wherein, the first hole section is the hole wall section of the bearing hole corresponding to the groove depth of the damping ring groove, and the second hole section is the hole wall section of the bearing hole adjacent to the first hole section.

[0007] Preferably, the minimum groove width of the first groove section is greater than the maximum groove width of the second groove section; and / or, the central spiral angle of the first groove section is less than the central spiral angle of the second groove section.

[0008] Preferably, the central spiral angle of the first groove section is α, and the central spiral angle of the second groove section is β, 0.07β ≤ α ≤ 0.75β.

[0009] Preferably, the aperture of the bearing hole is D, and the groove depth of the damping ring groove is H, H / D ≥ 0.4.

[0010] Preferably, the inner diameter of the damping ring groove is d, 0.8mm ≤ (d - D) / 2 ≤ 1.5mm.

[0011] Preferably, the minimum radial thickness of the wall body between the damping ring groove and the first groove section is h, 0.5mm ≤ h ≤ 1mm.

[0012] Preferably, the oil guiding cross-sectional area of the first groove section is s, 1mm 2 ≤ s ≤ 1.6mm 2 .

[0013] The present invention also provides a pump body assembly, including an upper flange and a lower flange, at least one of the upper flange and the lower flange being the above-mentioned flange.

[0014] The present invention also provides a rotary compressor, including the above-mentioned pump body assembly.

[0015] The present invention also provides an air conditioner, including a compressor, and the compressor is the above-mentioned rotary compressor.

[0016] A flange, a pump body assembly, a rotary compressor, and an air conditioner provided by the present invention design the spiral oil guiding groove on the first hole section, that is, the first groove section, as a shallow groove structure, so that the outer ring groove wall of the damping ring groove can be closer to the bearing hole, thereby increasing the sealing distance at the matching position between the end of the flange body and the roller, improving the volumetric efficiency of the pump body structure, and at the same time facilitating the prevention of the chipping phenomenon caused by the too small wall thickness of the wall body between the damping ring groove and the bearing hole. In addition, the second groove section is a deep groove structure relative to the first groove section, which is beneficial to ensuring the lubricating oil pumping performance of the crankshaft, further increasing the lubricating time of the lubricating oil in the flange, improving the lubricating performance of the pump body, reducing the wear of the pump body parts, improving the reliability and service life of the compressor, and enhancing the product quality. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] Figure 1 is a perspective structural view of the flange according to an embodiment of the present invention;

[0018] Figure 2 Figure 1 Internal structural view;

[0019] Figure 3 is an internal structural view of the flange according to another embodiment of the present invention;

[0020] Figure 4 is an internal structural view of the pump body assembly according to an embodiment of the present invention;

[0021] Figure 5 is Figure 4 Partial enlarged view at A in

[0022] The reference signs are shown as:

[0023] 1. Flange body; 11. Bearing hole; 12. Damping ring groove; 13. First groove section; 14. Second groove section; 100. Crankshaft; 101. Eccentric part; 102. Roller; 200. Upper flange; 201. Lower flange. DETAILED DESCRIPTION OF THE EMBODIMENTS

[0024] Referring to Figures 1 to 5As shown, according to an embodiment of the present invention, a flange is provided, including a flange body 1. A bearing hole 11 for inserting a crankshaft 100 is formed on the flange body 1. A damping ring groove 12 is formed on the orifice wall of the bearing hole 11 close to the side of the eccentric part 101 of the crankshaft 100. A spiral oil guiding groove is formed on the wall of the bearing hole 11. The spiral oil guiding groove includes a first groove section 13 on a first hole section and a second groove section 14 on a second hole section. The maximum groove depth of the first groove section 13 is less than the minimum groove depth of the second groove section 14. Wherein, the first hole section is the wall section of the bearing hole 11 corresponding to the groove depth of the damping ring groove 12 (also called a flexible ring groove), and the second hole section is the wall section of the bearing hole 11 adjacent to the first hole section. In this technical solution, the spiral oil guiding groove on the first hole section, that is, the first groove section 13, is designed as a shallow groove structure, so that the outer ring groove wall of the damping ring groove 12 can be closer to the bearing hole 11, thereby increasing the sealing distance ( Figure 5 shown as L in) at the mating position between the end part (flange disk end face) of the flange body 1 and the roller 102, improving the volumetric efficiency of the pump body structure, and at the same time facilitating the prevention of the chipping phenomenon caused by the too small wall thickness between the damping ring groove 12 and the bearing hole 11. In addition, the second groove section 14 being a deep groove structure relative to the first groove section 13 is beneficial to ensuring the lubricating oil pumping performance of the crankshaft 100, and further can increase the lubricating time of the lubricating oil in the flange, improve the lubricating performance of the pump body, reduce the wear of the pump body parts, improve the reliability and service life of the compressor, and improve the product quality.

[0025] Preferably, the minimum groove width of the first groove section 13 is greater than the maximum groove width of the second groove section 14 to ensure that the oil guiding flow area at the first groove section 13 is within a reasonable range.

[0026] As Figure 2 and Figure 3 show, two different implementation forms of the spiral oil guiding groove are given. Specifically, in Figure 2 , the first groove section 13 is an equal-width and equal-depth groove section, and the second groove section 14 is also an equal-width and equal-depth groove section. At this time, the groove width of the aforementioned first groove section 13 is the minimum groove width and all are the same groove width, and the maximum groove depth are all the same groove depth. Similarly, the maximum groove width of the second groove section 14 are all the same groove width, and the minimum groove depth are all the same groove depth. However, the groove width of the first groove section 13 is greater than the groove width of the second groove section 14, and the groove depth of the first groove section 13 is less than the groove depth of the second groove section 14; in Figure 3 , the first groove section 13 and the second groove section 14 are grooves that gradually change along the extension direction of the spiral oil guiding groove. Specifically, extending from the first groove section 13 to the second groove section 14, the groove width of the spiral oil guiding groove gradually becomes smaller, and the groove depth of the spiral oil guiding groove gradually becomes larger.

[0027] In some embodiments, the central spiral angle of the first groove section 13 is smaller than that of the second groove section 14. Preferably, the central spiral angle of the first groove section 13 is α, and the central spiral angle of the second groove section 14 is β, where 0.7β ≤ α ≤ 0.75β. Preferably, α = 0.72β. This can make the processing of the shallow-wide groove structure at the first groove section 13 more convenient, and can increase the residence time of the lubricating oil at the first groove section 13 to ensure the lubrication effect at the corresponding position. In some embodiments, 14° ≤ α ≤ 20°.

[0028] The aperture of the bearing hole 11 is D, and the groove depth of the damping ring groove 12 is H, where H / D ≥ 0.4. In this technical solution, the groove depth of the damping ring groove 12 is limited, which ensures the fine-tuning effect of the damping ring groove 12 on the flange under high load, prevents the increase of processing difficulty due to excessive groove depth, and increases the wall thickness between the flange bearing and the upper flange disk surface; at the same time, it prevents the reduction of the fine-tuning effect due to too small groove depth.

[0029] In some embodiments, the inner diameter of the damping ring groove 12 is d, where 0.8 mm ≤ (d - D) / 2 ≤ 1.5 mm, that is Figure 5 as shown in 0.8 mm ≤ T ≤ 1.5 mm, which prevents the thickness of the wall between the damping ring groove 12 and the bearing hole 11 from being too thin, resulting in large deformation of the flange surface when the load is too large, reducing the reliability of the compressor, and at the same time preventing the thickness of the wall between the damping ring groove 12 and the bearing hole 11 from being too thick, so that the fine-tuning function cannot be achieved.

[0030] Furthermore, the minimum radial thickness of the wall between the damping ring groove 12 and the first groove section 13 is h, where 0.5 mm ≤ h ≤ 1 mm, which prevents the occurrence of chipping phenomenon caused by too thin thickness of the wall between the inner ring wall of the damping ring groove 12 and the first groove section 13.

[0031] Preferably, the oil guiding cross-sectional area of the first groove section 13 is s, 1 mm 2 ≤ s ≤ 1.6 mm 2 , which ensures the oil guiding effect at the first groove section 13.

[0032] Through experimental analysis, it is obtained that compared with the prototype of the original oil groove, the volumetric efficiency of the compressor adopting the above technical solution of the present invention is increased by about 0.81%; the COP is significantly improved at low frequency, with an increase of 0.85% - 1.5%. From the experimental results, the double-section oil groove (that is, the spiral oil guiding groove including the above first groove section 13 and the second groove section 14) has an obvious improvement in volumetric efficiency, also improves the lubrication performance of the pump body, reduces the wear of pump body parts, improves the reliability and service life of the compressor, and improves the product quality.

[0033] According to an embodiment of the present invention, a pump body assembly is further provided, which includes an upper flange 200 and a lower flange 201, and at least one of the upper flange 200 and the lower flange 201 is the above-mentioned flange.

[0034] According to an embodiment of the present invention, a rotary compressor is further provided, which includes the above-mentioned pump body assembly.

[0035] According to an embodiment of the present invention, an air conditioner is further provided, which includes a compressor, and the compressor is the above-mentioned rotary compressor.

[0036] It is easily understood by those skilled in the art that, on the premise of no conflict, the above-mentioned advantageous manners can be freely combined and superimposed.

[0037] The above are only the preferred embodiments of the present invention, and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included within the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be pointed out that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and modifications can be made, and these improvements and modifications should also be regarded as the protection scope of the present invention.

Claims

1. A flange, characterized in that, it includes a flange body (1), a bearing hole (11) for inserting a crankshaft (100) is formed on the flange body (1), a damping ring groove (12) is formed on the orifice wall of the bearing hole (11) close to the side where the eccentric part (101) of the crankshaft (100) is located, a spiral oil guiding groove is formed on the hole wall of the bearing hole (11), the spiral oil guiding groove includes a first groove section (13) on a first hole section and a second groove section (14) on a second hole section, the maximum groove depth of the first groove section (13) is less than the minimum groove depth of the second groove section (14), wherein, the first hole section is the hole wall section of the bearing hole (11) corresponding to the groove depth of the damping ring groove (12), and the second hole section is the hole wall section of the bearing hole (11) adjacent to the first hole section.

2. The flange according to claim 1, characterized in that, the minimum groove width of the first groove section (13) is greater than the maximum groove width of the second groove section (14); and / or, the central spiral angle of the first groove section (13) is less than the central spiral angle of the second groove section (14).

3. The flange according to claim 2, characterized in that, the central spiral angle of the first groove section (13) is α, the central spiral angle of the second groove section (14) is β, 0.7β ≤ α ≤ 0.75β.

4. The flange according to claim 1, characterized in that, the aperture of the bearing hole (11) is D, the groove depth of the damping ring groove (12) is H, H / D ≥ 0.

4.

5. The flange according to claim 4, characterized in that, the inner diameter of the damping ring groove (12) is d, 0.8mm ≤ (d - D) / 2 ≤ 1.5mm.

6. The flange according to claim 1, characterized in that, the minimum radial thickness of the wall body between the damping ring groove (12) and the first groove section (13) is h, 0.5mm ≤ h ≤ 1mm.

7. The flange according to claim 1, characterized in that, The oil guiding cross-sectional area of the first tank section (13) is s, 1 mm 2 ≤ s ≤ 1.6 mm 2 .

8. A pump body assembly, characterized in that, it includes an upper flange (200) and a lower flange (201), and at least one of the upper flange (200) and the lower flange (201) is the flange according to any one of claims 1 to 7.

9. A rotary compressor, characterized in that, it includes the pump body assembly according to claim 8.

10. An air conditioner includes a compressor, characterized in that, the compressor is the rotary compressor according to claim 9.

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