Crankshaft structure and compressor with same

Abstract

The invention provides a crankshaft structure and a compressor with the same. The crankshaft structure comprises a shaft body part and an eccentric part, the shaft body part and the eccentric part both extend in the preset direction, and at least part of the eccentric part protrudes out of the outer edge of the shaft body part; wherein the shaft body part is provided with a first connecting part, the eccentric part is provided with a second connecting part used for being connected with at least part of the first connecting part, and the end of the first connecting part and the end of the second connecting part are arranged in a spaced mode to define an avoiding groove. By means of the technical scheme, the technical problem that in the prior art, the contact stress of the matching face of the crankshaft and the flange of the compressor is large can be solved.

Description

Technical Field

[0001] The present invention relates to the technical field of crankshaft structures, and in particular to a crankshaft structure and a compressor having the same. Background Art

[0002] At present, in rolling rotor compressors, the crankshaft plays the role of driving the rollers and vanes to slide relative to each other. The long axis and short axis of the crankshaft are matched with the upper flange and lower flange of the compressor respectively, forming the main bearing and auxiliary bearing structure. However, during the operation of the compressor, the crankshaft is simultaneously subjected to the combined effects of multiple unbalanced forces such as the electromagnetic force generated by the motor, the centrifugal force generated by its own rotation, and the gas compression force, which causes the crankshaft to be easily deformed significantly in the root area connected to the flange. This deformation will not only reduce the matching clearance of the bearing and cause high contact stress, but also the root area will become the peak position of the contact stress, which is prone to abnormal wear.

[0003] However, in order to alleviate the problem of high contact stress in the root area of ​​the crankshaft, the prior art generally adopts the setting of adding flexible grooves to the end faces of the upper flange and the lower flange. The introduction of the flexible groove is intended to reduce the rigidity of the flange end face and increase its local flexible deformation under the action of the unbalanced force of the compressor, thereby expanding the contact area with the crankshaft, reducing the contact stress, and avoiding premature wear of the crankshaft root. However, this design has obvious limitations in the application of the lower flange end face. The lower flange is not only responsible for cooperating with the crankshaft thrust surface, thereby providing the necessary axial support for the entire shaft system, but also bears the role of forming a seal with the roller end face and preventing compressed gas leakage. Although the flexible groove is provided on the end face of the lower flange, it can reduce the contact stress, but it inevitably reduces the effective support area of ​​the thrust surface, destroys the original roller end face sealing distance, causes the compressor to produce greater abnormal noise in the air-conditioning system, increases the power consumption and wear of the thrust surface, and the leakage of the roller end face is also aggravated, which will eventually affect the cooling efficiency and overall energy efficiency of the compressor. Summary of the invention

[0004] The main purpose of the present invention is to provide a crankshaft structure and a compressor having the same, so as to solve the technical problem of large contact stress at the flange matching surface between the crankshaft and the compressor in the prior art.

[0005] In order to achieve the above object, according to one aspect of the present invention, a crankshaft structure is provided, comprising:

[0006] A shaft body portion and an eccentric portion, wherein the shaft body portion and the eccentric portion are both extended along a preset direction, and at least a portion of the eccentric portion protrudes from an outer edge of the shaft body portion;

[0007] The shaft body has a first connection portion, the eccentric portion has a second connection portion for connecting to at least part of the first connection portion, and the end of the first connection portion is spaced apart from the end of the second connection portion to form an avoidance groove.

[0008] Further, the avoidance groove is an annular groove, and the annular groove is arranged around the periphery of the shaft body; and / or,

[0009] There are at least two avoidance grooves, and the at least two avoidance grooves are arranged at intervals along the periphery of the shaft body.

[0010] Further, the spacing distance between the end of the first connecting portion and the end of the second connecting portion is c1;

[0011] Among them, c1≥0.5mm; and / or, c1≤3mm.

[0012] Furthermore, the avoidance groove is extended along a preset direction, and the depth of the avoidance groove along the preset direction is h1.

[0013] Among them, h1≥4mm; and / or, h1≤15mm.

[0014] Further, the eccentric portion includes a first side portion and a second side portion spaced apart along a preset direction, and the shaft body portion includes a first shaft connected to the first side portion and a second shaft connected to the second side portion; the length of the first shaft in the preset direction is less than the length of the second shaft in the preset direction;

[0015] Wherein, the avoidance groove is arranged on the first side portion; or,

[0016] The avoidance groove is arranged on the second side portion; or,

[0017] There are at least two avoidance grooves, and one of the at least two avoidance grooves is arranged on the first side portion, and the other is arranged on the second side portion.

[0018] Furthermore, an oil passage for circulating lubricating medium is arranged in the shaft body, and the avoidance groove is connected to the oil passage.

[0019] Furthermore, an oil passage for circulating lubricating medium is arranged in the shaft body, a groove is arranged on the eccentric part, an oil outlet hole connected with the oil passage is arranged on the inner wall of the groove, and the avoidance groove is arranged in communication with the groove;

[0020] The notch of the avoidance groove is located at the outer end wall of the eccentric part; along the preset direction, the distance between the notch and the center of the oil outlet hole is h2, the radius of the oil outlet hole is r2, the depth of the avoidance groove along the preset direction is h1, h1≤h2-r2; and / or,

[0021] Along the preset direction, the distance between the inner end wall of the avoidance groove and the center of the oil outlet hole is d1, and d1≥1mm.

[0022] Furthermore, an oil passage for circulating lubricating medium is arranged in the shaft body, a groove is arranged on the eccentric part, an oil outlet hole connected to the oil passage is arranged on the inner wall of the groove; an oil groove is arranged on the outer wall surface of the eccentric part, and the oil groove is connected to the groove;

[0023] Wherein, the oil groove is a strip-shaped groove, and the oil groove is arranged around the outer edge of the eccentric part; and / or,

[0024] The inner wall of the groove is an arc-shaped structure; and / or,

[0025] The groove is extended along a preset direction.

[0026] Furthermore, there are at least two eccentric parts, and the at least two eccentric parts are arranged at intervals along a preset direction;

[0027] There are at least two avoidance grooves, one of the at least two avoidance grooves is arranged on a side of one of the at least two eccentric parts away from the other, and the other of the at least two avoidance grooves is arranged on a side of the other of the at least two eccentric parts away from one.

[0028] According to another aspect of the present invention, a compressor is provided, comprising: the crankshaft structure provided above.

[0029] By applying the technical solution of the present invention, the setting of the avoidance groove can reduce the rigidity of the connection between the eccentric part and the shaft body, so that when the crankshaft is subjected to the unbalanced force, the overall stress distribution can be adjusted through the local deformation of the avoidance groove. This design reduces the maximum contact stress formed in the root area on the eccentric part side, thereby avoiding abnormal wear in this area and extending the service life of the crankshaft. Due to the presence of the avoidance groove, the connection between the first connection part of the shaft body and the second connection part of the eccentric part is more flexible, which can better adapt to the dynamic changes during the operation of the compressor, ensure the stability of the bearing fitting clearance, and reduce the friction and power consumption caused by flexural deformation. The design of the avoidance groove not only reduces the abnormal wear and power consumption of the crankshaft, but also improves the efficiency and reliability of the compressor by improving lubrication and reducing vibration, and reduces energy consumption and maintenance costs. Therefore, the technical problem of large contact stress at the flange fitting surface of the crankshaft and the compressor in the prior art can be solved through the technical solution of the present invention. BRIEF DESCRIPTION OF THE DRAWINGS

[0030] The drawings constituting a part of the present application are used to provide a further understanding of the present invention. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0031] Figure 1 It shows a schematic structural diagram of a crankshaft structure provided according to the first embodiment of the present invention;

[0032] Figure 2 A partial structural schematic diagram of a crankshaft structure provided according to Embodiment 1 of the present invention is shown;

[0033] Figure 3 A partial cross-sectional structural schematic diagram of a crankshaft structure provided according to Embodiment 1 of the present invention is shown;

[0034] Figure 4 A partial structural schematic diagram of a crankshaft structure provided according to a second embodiment of the present invention is shown;

[0035] Figure 5 A partial cross-sectional structural schematic diagram of a crankshaft structure provided according to a third embodiment of the present invention is shown;

[0036] Figure 6 A partial cross-sectional structural schematic diagram of a compressor provided according to a fourth embodiment of the present invention is shown.

[0037] The above drawings include the following reference numerals:

[0038] 10. Shaft body;

[0039] 100. a first connecting portion;

[0040] 101, oil channel;

[0041] 11. First axis;

[0042] 12. Second axis;

[0043] 13. Back cutter groove;

[0044] 20. Eccentric part;

[0045] 200, second connecting portion;

[0046] 201, first side portion;

[0047] 202, second side portion;

[0048] 21. Avoidance slot;

[0049] 211, notch;

[0050] 212. Inner end wall;

[0051] 22. Groove;

[0052] 221, oil outlet hole;

[0053] 23. Oil tank;

[0054] 31. Upper flange;

[0055] 32. Lower flange;

[0056] 33. Roller. DETAILED DESCRIPTION

[0057] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present invention will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0058] like Figures 1 to 3 As shown, the first embodiment of the present invention provides a crankshaft structure, which includes a shaft body 10 and an eccentric portion 20. The shaft body 10 and the eccentric portion 20 are both extended along a preset direction, and at least a portion of the eccentric portion 20 is protruded from the outer edge of the shaft body 10. The shaft body 10 has a first connecting portion 100, and the eccentric portion 20 has a second connecting portion 200 for connecting to at least a portion of the first connecting portion 100. The end of the first connecting portion 100 is spaced apart from the end of the second connecting portion 200 to form a avoiding groove 21.

[0059] By adopting the crankshaft structure provided by the first embodiment of the present invention, the setting of the avoidance groove 21 can reduce the rigidity of the connection between the eccentric part 20 and the shaft body part 10, so that when the crankshaft is subjected to the unbalanced force, the overall stress distribution can be adjusted by the local deformation of the avoidance groove 21. This design reduces the maximum contact stress formed in the root area on the side of the eccentric part 20, thereby avoiding abnormal wear in this area and extending the service life of the crankshaft. Due to the presence of the avoidance groove 21, the connection between the first connection part 100 of the shaft body part 10 and the second connection part 200 of the eccentric part 20 is more flexible, which can better adapt to the dynamic changes during the operation of the compressor, ensure the stability of the bearing fitting clearance, and reduce the friction and power consumption caused by flexural deformation. The design of the avoidance groove 21 not only reduces the abnormal wear and power consumption of the crankshaft, but also improves the efficiency and reliability of the compressor by improving lubrication and reducing vibration, and reduces energy consumption and maintenance costs. Therefore, the crankshaft structure provided by this embodiment can solve the technical problem of large contact stress at the flange fitting surface of the crankshaft and the compressor in the prior art.

[0060] It should be noted that the present solution extends the shaft body 10 to the inside of the eccentric part 20 by setting the avoidance groove 21 at the end of the first connection part 100 and the end of the second connection part 200, and its goal is to reduce the maximum contact stress between the shaft body 10 and the inner wall of the flange. By changing the position where the shaft body 10 is prone to flexural deformation, it is adjusted from the original position where the shaft body 10 and the eccentric part 20 are directly connected (that is, the end of the first connection part 100 and the end of the second connection part 200 are mutually attached and connected, and there is no gap between the end of the first connection part 100 and the end of the second connection part 200, in this case, the starting position of deformation coincides with the maximum contact stress position) to the inside of the eccentric part 20, that is, the position of the inner end wall 212 of the avoidance groove 21. By such a setting, the starting position of deformation can be separated from the maximum contact stress position, thereby improving the flexural deformation of the shaft body 10, changing the size of the contact area with the inner wall of the flange, and reducing the maximum contact stress.

[0061] Specifically, the avoidance groove 21 is an annular groove, and the annular groove is arranged around the periphery of the shaft body 10. With such a structural arrangement and the design of the annular avoidance groove 21, the stress generated by the crankshaft during operation can be evenly distributed to avoid stress concentration. This uniform stress distribution helps to reduce abnormal wear at the root of the eccentric portion 20 of the crankshaft (i.e., the connection between the shaft body 10 and the eccentric portion 20) and enhance the stability of the crankshaft structure. The setting of the annular groove also ensures that the lubricating oil can be evenly distributed along the periphery of the shaft body 10, thereby improving the lubrication effect, further reducing friction and wear, and improving the operating efficiency and life of the compressor.

[0062] Specifically, there are at least two avoidance grooves 21, and at least two avoidance grooves 21 are arranged at intervals along the periphery of the shaft body 10. With such a structural arrangement, multiple avoidance grooves 21 arranged at intervals can provide a more flexible deformation space, so that the crankshaft can more effectively adjust its flexural deformation when subjected to unbalanced forces, thereby reducing contact stress and wear. In addition, the design of multiple avoidance grooves 21 can also improve the storage and distribution capacity of lubricating oil, ensuring that each bearing part can obtain sufficient lubrication under high-speed operation conditions, preventing overheating and wear caused by poor lubrication.

[0063] Specifically, the avoidance groove 21 is arranged on the first connection part 100; or, the avoidance groove 21 is arranged on the second connection part 200; or, a first avoidance notch is arranged on the first connection part 100, and a second avoidance notch is arranged on the second connection part 200, and at least a part of the first avoidance notch and the second avoidance notch are arranged opposite to each other to enclose the avoidance groove 21. In this way, the contact stress in the crankshaft root area is effectively relieved, abnormal wear is reduced, lubrication performance and shaft system balance are enhanced, and the operating efficiency and reliability of the compressor are improved. At the same time, under the premise of ensuring structural strength, the maintenance process is simplified and the cost is reduced.

[0064] Specifically, the spacing distance between the end of the first connection part 100 and the end of the second connection part 200 is c1. Wherein, c1≥0.5mm. With such a structural setting, it is ensured that the width of the avoidance groove 21 is at least 0.5mm, which can provide sufficient space to allow local deformation, thereby adjusting the stress distribution, reducing the contact stress, and preventing abnormal wear. At the same time, such a width design also ensures the strength and stability of the overall crankshaft structure, avoiding structural failure or performance degradation caused by excessive clearance.

[0065] Specifically, the spacing distance between the end of the first connection part 100 and the end of the second connection part 200 is c1. Wherein, c1≤3mm. With such a structural setting, the width of the avoidance groove 21 is limited to within 3mm, which helps to maintain a close fit between the crankshaft and the upper and lower flanges, ensuring the stability of the bearing and the sealing of the compressor. The smaller gap c1 can also reduce the leakage of lubricating oil, maintain the effectiveness and efficiency of the lubrication system, and avoid the vibration and noise problems aggravated by excessive gaps, thereby improving the smoothness of the compressor operation and the comfort of users.

[0066] It should be noted that “the spacing distance between the end of the first connection part 100 and the end of the second connection part 200” refers to the spacing distance between the end of the first connection part 100 and the end of the second connection part 200 along the direction from the first connection part 100 to the second connection part 200.

[0067] Specifically, the avoidance groove 21 is extended along a preset direction, and the depth of the avoidance groove 21 along the preset direction is h1. Wherein, h1≥4mm. With such a structural setting, the depth of the avoidance groove is at least 4mm. This design ensures that the crankshaft has enough space for local deformation at the connection between the eccentric portion 20 and the shaft body portion 10, so that there is enough spacing between the deformation starting position and the maximum contact stress position, which helps to absorb and disperse the flexural deformation caused by the unbalanced force. The avoidance groove 21 with a larger depth can more effectively reduce the maximum contact stress in the root area of ​​the eccentric portion 20 of the crankshaft and prevent the occurrence of abnormal wear. At the same time, it also provides sufficient space for the storage of lubricating oil, improves lubrication conditions, reduces power consumption and high temperature caused by friction, and improves the overall efficiency and reliability of the compressor.

[0068] Specifically, the avoidance groove 21 is extended along a preset direction, and the depth of the avoidance groove 21 along the preset direction is h1. Among them, h1≤15mm. With such a structural setting, the upper limit of the depth of the avoidance groove 21 is set to 15mm, in order to ensure the mechanical strength and rigidity of the crankshaft structure while allowing local deformation of the crankshaft and reducing contact stress. Excessive depth may weaken the overall stability of the crankshaft and increase the risk of fracture, and the 15mm limit ensures that the avoidance groove 21 can provide the necessary stress relief without excessively weakening the structural strength of the crankshaft. In addition, limiting the depth range also helps to control the difficulty and cost of processing, ensure the feasibility and economy of the design, while avoiding leakage or pressure fluctuations caused by excessive storage of lubricating oil, and maintaining the balance and stability of the lubrication system in the compressor.

[0069] In this embodiment, the eccentric portion 20 includes a first side portion 201 and a second side portion 202 arranged at intervals along a preset direction, and the shaft body portion 10 includes a first shaft 11 connected to the first side portion 201 and a second shaft 12 connected to the second side portion 202; the length of the first shaft 11 in the preset direction is less than the length of the second shaft 12 in the preset direction. Among them, the avoidance groove 21 is arranged on the first side portion 201; or, the avoidance groove 21 is arranged on the second side portion 202. With such a structural arrangement, by arranging the avoidance groove 21 on the first side portion 201 or the second side portion 202, the local elasticity of the crankshaft can be increased, and the maximum contact stress in the root area can be effectively reduced, thereby avoiding abnormal wear and extending the service life of the crankshaft. At the same time, due to the flexibility of the arrangement of the avoidance groove 21, the dynamic balance of the shaft system can be optimized, vibration and noise can be reduced, and the operating stability of the compressor can be improved while maintaining the compactness of the overall structure of the compressor.

[0070] In this embodiment, the eccentric portion 20 includes a first side portion 201 and a second side portion 202 arranged at intervals along a preset direction, and the shaft body portion 10 includes a first shaft 11 connected to the first side portion 201 and a second shaft 12 connected to the second side portion 202; the length of the first shaft 11 in the preset direction is less than the length of the second shaft 12 in the preset direction. Among them, there are at least two avoidance grooves 21, one of the at least two avoidance grooves 21 is arranged on the first side portion 201, and the other is arranged on the second side portion 202. The use of such a structural setting not only enhances the local elasticity of the crankshaft structure, but also can more comprehensively absorb and disperse the stress concentration caused by the unbalanced force, and further reduce the maximum contact stress of the crankshaft in the root area. At the same time, by respectively arranging the avoidance grooves 21 on the first side portion 201 and the second side portion 202, the adaptive balance adjustment of the shaft system can be achieved, the overall vibration and noise can be reduced, and the operating efficiency and reliability of the compressor can be optimized. This design can also ensure the uniform distribution of lubricating oil in different parts of the shaft system, improve the lubrication effect, and reduce friction power consumption.

[0071] Specifically, an oil passage 101 for circulating lubricating medium is provided in the shaft body 10, and the avoidance groove 21 is connected to the oil passage 101. With such a structural arrangement, the avoidance groove 21 is connected to the oil passage 101 in the shaft body, forming an innovative lubricating oil supply system. During the operation of the compressor, the lubricating oil can enter the avoidance groove 21 through the oil passage 101, and then flow to the part that needs lubrication through the opening of the avoidance groove 21 or the oil hole connected thereto. This design not only improves the storage and distribution efficiency of the lubricating oil, but also ensures sufficient lubrication of the bearing area, reduces wear and power consumption caused by poor lubrication, and keeps the interior of the compressor clean, avoiding performance degradation caused by residual lubricating oil. The combination of the connected avoidance groove 21 and the oil passage 101 optimizes the lubrication mechanism of the compressor, improves its operating efficiency and reliability, and reduces maintenance costs.

[0072] Specifically, the shaft body 10 is provided with an oil passage 101 for circulating lubricating medium, the eccentric part 20 is provided with a groove 22, the inner wall of the groove 22 is provided with an oil outlet hole 221 connected to the oil passage 101, and the avoidance groove 21 is connected to the groove 22. The notch 211 of the avoidance groove 21 is located at the outer end wall of the eccentric part 20; along the preset direction, the distance between the notch 211 and the center of the oil outlet hole 221 is h2, the radius of the oil outlet hole 221 is r2, and the depth of the avoidance groove 21 along the preset direction is h1, h1≤h2-r2. Such a structural setting ensures that the lubricating oil can effectively enter the avoidance groove 21 and the groove 22 from the oil passage 101 through the oil outlet hole 221, providing sufficient lubrication for the contact surface between the crankshaft and the flange, and reducing contact stress and wear. The relationship between the limited depth h1, the spacing h2 and the radius r2 (h1≤h2-r2) ensures that the avoidance groove 21 does not excessively weaken the structural strength of the eccentric part 20, while also providing sufficient space for local deformation to achieve the effect of stress relief. The notch 211 of the avoidance groove 21 is located on the outer end wall of the eccentric part 20, which can directly guide the lubricating oil to the contact area at the root of the crankshaft, thereby improving lubrication efficiency and reducing power consumption.

[0073] Specifically, the shaft body 10 is provided with an oil passage 101 for circulating lubricating medium, the eccentric part 20 is provided with a groove 22, the inner wall of the groove 22 is provided with an oil outlet hole 221 connected to the oil passage 101, and the avoidance groove 21 is connected to the groove 22. In the preset direction, the distance between the inner end wall 212 of the avoidance groove 21 and the center of the oil outlet hole 221 is d1, and d1 ≥ 1mm. In this way, the structural strength problem caused by too small a distance can be prevented, the durability and reliability of the eccentric part 20 are maintained, and the processing difficulty and production cost are reduced.

[0074] Specifically, the inner wall of the groove 22 is an arc-shaped structure. With such a structural setting, the groove 22 with an arc-shaped inner wall can better guide the flow of lubricating oil, avoiding uneven distribution of lubricating oil or excessive local pressure caused by right angles or sharp edges. The arc-shaped structure also helps to reduce mechanical stress concentration and increase the storage space of lubricating oil. In addition, the arc-shaped design is easier to implement during the processing, reducing the manufacturing difficulty and improving production efficiency.

[0075] Specifically, the groove 22 is extended along a preset direction. With such a setting, the groove 22 extends along the preset direction, and forms a flow path for the lubricating oil with the oil channel 101 and the avoidance groove 21, ensuring the uniform distribution and effective utilization of the lubricating oil in the shaft system. This design can improve the efficiency of the lubricating medium reaching the key contact area, reduce the friction and wear caused by poor lubrication, reduce the power consumption and heat generation during the operation of the compressor, thereby improving the energy efficiency and service life of the equipment. At the same time, the groove 22 extending along the preset direction can better adapt to the dynamic deformation of the crankshaft, avoid stress concentration caused by excessive local rigidity, and optimize the operating stability of the compressor.

[0076] Specifically, the end of the groove 22 extends to the end of the second connecting portion 200 along a preset direction. Such a structural arrangement ensures that the lubricating oil can directly and fully cover the connection area between the eccentric portion 20 and the shaft body portion 10, that is, the root area of ​​the short shaft, which is a key part of the crankshaft that is susceptible to stress concentration and wear. Through the extended groove 22, the lubricating oil can flow into and distribute in the area more effectively, forming a stable oil film, reducing direct contact, reducing contact stress and wear, and increasing the service life of the crankshaft and the reliability of the compressor. In addition, the extended groove 22 also helps to optimize the flow path of the lubricating oil, increase the storage space of the lubricating medium, reduce power consumption and temperature during operation, and further improve the energy efficiency and operating stability of the compressor.

[0077] like Figure 4As shown, in the second embodiment, an oil passage 101 for circulating lubricating medium is provided in the shaft body 10, a groove 22 is provided on the eccentric part 20, and an oil outlet hole 221 connected to the oil passage 101 is provided on the inner wall of the groove 22; an oil groove 23 is provided on the outer wall surface of the eccentric part 20, and the oil groove 23 is connected to the groove 22. Among them, the oil groove 23 is a strip groove, and the oil groove 23 is arranged around the outer edge of the eccentric part 20. With such an arrangement, a surrounding strip oil groove 23 is arranged on the outer wall surface of the eccentric part 20, which is connected to the groove 22 and the oil passage 101, forming a complete lubricating oil circulation system. The arrangement of the strip oil groove 23 can evenly distribute the lubricating oil to the entire outer surface of the eccentric part 20, especially those areas in close contact with the upper and lower flanges, thereby improving the lubrication effect, reducing power consumption and high temperature caused by friction, and reducing the risk of abnormal wear. The surrounding oil tank 23 design can also increase the storage capacity of the lubricating oil, ensure sufficient supply of lubricating oil when the compressor is running at high speed, and improve the cooling efficiency and operating stability of the equipment. This layout simplifies the management of lubricating oil, reduces maintenance costs, and improves the energy efficiency and reliability of the compressor.

[0078] like Figure 5 As shown, in the third embodiment, there are at least two eccentric parts 20, and at least two eccentric parts 20 are arranged at intervals along a preset direction. There are at least two avoidance grooves 21, and one of the at least two avoidance grooves 21 is arranged on a side of one of the at least two eccentric parts 20 away from the other, and the other of the at least two avoidance grooves 21 is arranged on a side of the other of the at least two eccentric parts 20 away from one. In this way, in a double eccentric or multi-eccentric crankshaft structure, avoidance grooves 21 are arranged on at least two eccentric parts 20 arranged at intervals along a preset direction, which can achieve more balanced stress distribution and more effective stress relief. The avoidance groove 21 on the outside of each eccentric part 20 can independently absorb and disperse the local stress caused by the unbalanced force, reduce the maximum contact stress in the root area, avoid abnormal wear, and extend the service life of the crankshaft. In addition, the design of at least two avoidance grooves 21 can also provide additional lubricating oil storage space, which can ensure sufficient supply of lubricating medium even when the compressor is running at high speed or high load, thereby improving the lubrication effect and the dynamic balance performance of the shaft system. This design can also reduce vibration and noise caused by stress concentration, optimizing the operating efficiency of the compressor and the comfort of the user.

[0079] Specifically, the shaft body 10 is also provided with an undercut 13. As the compressor develops towards high speed, the crankshaft journal tends to be designed to be smaller. Since the diameter of the short shaft is equal to or smaller than that of the long shaft, the depth of the undercut 13 is inevitably reduced to weaken the attenuation of the crankshaft stiffness. The arrangement of this solution can compensate for the weakening of the oil storage capacity caused by the change of the undercut 13.

[0080] like Figure 6As shown, embodiment 2 of the present invention provides a compressor, and the compressor includes the crankshaft structure provided by any one of embodiments 1 to 3.

[0081] In the compressor provided by the second embodiment of the present invention, the setting of the avoidance groove 21 can reduce the rigidity of the connection between the eccentric part 20 and the shaft body 10, so that when the crankshaft is subjected to the unbalanced force, the overall stress distribution can be adjusted by the local deformation of the avoidance groove 21. This design reduces the maximum contact stress formed in the root area on the side of the eccentric part 20, thereby avoiding abnormal wear in this area and extending the service life of the crankshaft. Due to the presence of the avoidance groove 21, the connection between the first connection part 100 of the shaft body 10 and the second connection part 200 of the eccentric part 20 is more flexible, which can better adapt to the dynamic changes during the operation of the compressor, ensure the stability of the bearing fitting clearance, and reduce the friction and power consumption caused by flexural deformation. The design of the avoidance groove 21 not only reduces the abnormal wear and power consumption of the crankshaft, but also improves the efficiency and reliability of the compressor by improving lubrication and reducing vibration, and reduces energy consumption and maintenance costs. Therefore, the compressor provided by this embodiment can solve the technical problem of large contact stress at the flange fitting surface of the crankshaft and the compressor in the prior art.

[0082] Specifically, the compressor is a rolling rotor compressor, and the rolling rotor compressor includes a single rotor, a dual rotor or a multi-rotor structure. The compressor can be any one of a single rotor compressor, a dual rotor compressor and a multi-rotor compressor. In the rolling rotor compressor, the roller 33 and the sliding vane are driven synchronously by the motor to slide relative to each other, and the long axis and the short axis are respectively matched with the upper flange 31 and the lower flange 32 to form a main bearing and a secondary bearing.

[0083] From the above description, it can be seen that the above-mentioned embodiments of the present invention achieve the following technical effects: an avoidance groove is provided on the crankshaft thrust surface to appropriately reduce local stiffness, adjust flexural deformation, and reduce the maximum contact stress in the short shaft contact area; the crankshaft avoidance groove is connected to the radial oil outlet hole of the eccentric part, and has oil storage capacity to provide sufficient lubrication requirements for the lower flange; the lower flange oil storage groove is eliminated, the bearing area and bearing capacity of the lower flange are increased, which helps to form an oil film and reduce abnormal wear; the avoidance groove is provided at the root of the crankshaft short shaft, and the existing crankshaft thrust area and roller end face sealing distance are not changed, thereby ensuring reliable and efficient operation of the compressor; the avoidance groove is provided on the eccentric part to reduce the mass of the eccentric part, reduce the centrifugal imbalance effect, and optimize the balance of the shaft system.

[0084] It should be noted that the terms used herein are only for describing specific embodiments and are not intended to limit the exemplary embodiments according to the present application. As used herein, unless the context clearly indicates otherwise, the singular form is also intended to include the plural form. In addition, it should be understood that when the terms "comprise" and / or "include" are used in this specification, it indicates the presence of features, steps, operations, devices, components and / or combinations thereof.

[0085] Unless otherwise specifically stated, the relative arrangement, numerical expressions and numerical values ​​of the parts and steps set forth in these embodiments do not limit the scope of the application. Meanwhile, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to actual proportional relationships. The technology, methods and equipment known to those of ordinary skill in the relevant art may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be considered as a part of the specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, and therefore, once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0086] In the description of the present application, it should be understood that the directions or positional relationships indicated by directional words such as "front, back, up, down, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom" are usually based on the directions or positional relationships shown in the drawings, and are only for the convenience of describing the present application and simplifying the description. Unless otherwise specified, these directional words do not indicate or imply that the device or element referred to must have a specific direction or be constructed and operated in a specific direction, and therefore cannot be understood as limiting the scope of protection of the present application; the directional words "inside and outside" refer to the inside and outside relative to the contours of each component itself.

[0087] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" can include both "above" and "below". The device can also be positioned in other different ways (rotated 90 degrees or in other orientations), and the spatially relative descriptions used here are interpreted accordingly.

[0088] In addition, it should be noted that the use of terms such as "first" and "second" to limit components is only for the convenience of distinguishing the corresponding components. Unless otherwise stated, the above terms have no special meaning and therefore cannot be understood as limiting the scope of protection of this application.

[0089] The above description is only a preferred embodiment of the present invention and is not intended to limit the present invention. For those skilled in the art, the present invention may have various modifications and variations. Any modification, equivalent replacement, improvement, etc. made within the spirit and principle of the present invention shall be included in the protection scope of the present invention.

Claims

1. A crankshaft structure, characterized in that: include: A shaft portion (10) and an eccentric portion (20), wherein the shaft portion (10) and the eccentric portion (20) are both extended along a preset direction, and at least a portion of the eccentric portion (20) is protruding from an outer edge of the shaft portion (10); The shaft body (10) has a first connection portion (100), the eccentric portion (20) has a second connection portion (200) for connecting to at least part of the first connection portion (100), and the end of the first connection portion (100) and the end of the second connection portion (200) are spaced apart to form an avoidance groove (21).

2. The crankshaft structure according to claim 1, characterized in that: The avoidance groove (21) is an annular groove, and the annular groove is arranged around the periphery of the shaft body (10); and / or, There are at least two avoidance grooves (21), and at least two avoidance grooves (21) are arranged at intervals along the periphery of the shaft body (10).

3. The crankshaft structure according to claim 1, characterized in that: The spacing distance between the end of the first connecting portion (100) and the end of the second connecting portion (200) is c1; Among them, c1≥0.5mm; and / or, c1≤3mm.

4. The crankshaft structure according to claim 1, characterized in that: The avoidance groove (21) is extended along the preset direction, and the depth of the avoidance groove (21) along the preset direction is h1. Among them, h1≥4mm; and / or, h1≤15mm.

5. The crankshaft structure according to claim 1, characterized in that: The eccentric portion (20) comprises a first side portion (201) and a second side portion (202) arranged at intervals along the preset direction, and the shaft body portion (10) comprises a first shaft (11) connected to the first side portion (201) and a second shaft (12) connected to the second side portion (202); the length of the first shaft (11) in the preset direction is smaller than the length of the second shaft (12) in the preset direction; Wherein, the avoidance groove (21) is arranged on the first side portion (201); or, The avoidance groove (21) is arranged on the second side portion (202); or, There are at least two avoidance grooves (21), and one of the at least two avoidance grooves (21) is arranged on the first side portion (201), and the other is arranged on the second side portion (202).

6. The crankshaft structure according to claim 1, characterized in that: An oil passage (101) for circulating a lubricating medium is arranged in the shaft body (10), and the avoidance groove (21) is connected to the oil passage (101).

7. The crankshaft structure according to claim 1, characterized in that: An oil passage (101) for circulating a lubricating medium is arranged in the shaft body (10), a groove (22) is arranged on the eccentric portion (20), an oil outlet hole (221) connected to the oil passage (101) is arranged on the inner wall of the groove (22), and the avoidance groove (21) is arranged in communication with the groove (22); Wherein, the notch (211) of the avoidance groove (21) is located at the outer end wall of the eccentric portion (20); along the preset direction, the distance between the notch (211) and the center of the oil outlet hole (221) is h2, the radius of the oil outlet hole (221) is r2, and the depth of the avoidance groove (21) along the preset direction is h1, h1≤h2-r2; and / or, Along the preset direction, the distance between the inner end wall (212) of the avoidance groove (21) and the center of the oil outlet hole (221) is d1, and d1 is ≥ 1 mm.

8. The crankshaft structure according to claim 1, characterized in that: An oil passage (101) for circulating a lubricating medium is arranged in the shaft body (10); a groove (22) is arranged on the eccentric portion (20); an oil outlet hole (221) connected to the oil passage (101) is arranged on the inner wall of the groove (22); an oil groove (23) is arranged on the outer wall surface of the eccentric portion (20); the oil groove (23) is connected to the groove (22); Wherein, the oil groove (23) is a strip-shaped groove, and the oil groove (23) is arranged around the outer edge of the eccentric portion (20); and / or, The inner wall of the groove (22) is an arc-shaped structure; and / or, The groove (22) is extended along the preset direction.

9. The crankshaft structure according to claim 1, characterized in that: There are at least two eccentric parts (20), and at least two eccentric parts (20) are arranged at intervals along the preset direction; There are at least two avoidance grooves (21), one of the at least two avoidance grooves (21) is arranged on a side of one of the at least two eccentric parts (20) away from the other, and the other of the at least two avoidance grooves (21) is arranged on a side of the other of the at least two eccentric parts (20) away from one.

10. A compressor, characterized in that: include: The crankshaft structure according to any one of claims 1 to 9.

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