Flange structure, pump body assembly, compressor and heat exchange system

Abstract

The application provides a flange structure, a pump body assembly, a compressor and a heat exchange system. The flange structure comprises a flange body and a bearing, a mounting ring groove is arranged on a support end surface of the flange body, the bearing comprises an outer ring, an inner ring and a plurality of rolling bodies, the outer ring is fixed in the mounting ring groove in interference fit with the groove wall of the mounting ring groove, the inner ring is rotatably arranged between the outer ring to form a raceway groove, and the plurality of rolling bodies are arranged in the raceway groove in self-rotation in the circumferential direction of the raceway groove. The self-rotation axis of each rolling body is outwardly and obliquely arranged from the support end surface of the flange body towards the sleeving hole, so that the bearing can bear the combined load of the axial magnetic pull and the radial centrifugal force caused by the thickening of the motor core, effectively disperse the local stress to the contact area of the bearing, effectively maintain the stable fit clearance between the crankshaft and the bearing, and realize the collaborative optimization between high efficiency, energy saving and structural reliability.

Description

Technical Field

[0001] This invention relates to the field of compressor technology, and in particular to a flange structure, a pump body assembly having the flange structure, a compressor having the pump body assembly, and a heat exchange system having the compressor. Background Technology

[0002] In heat exchange systems, the compressor performs mechanical work to achieve changes in the state and circulation of the refrigerant, thereby completing the absorption, transfer, and release of heat. Rotary compressors are widely used in heat exchange systems due to their advantages such as low manufacturing cost, low price, compact structure, low vibration and noise, and high compression efficiency.

[0003] A rotary compressor consists of a motor, crankshaft, upper flange, lower flange, cylinder, rollers, and vanes. The rollers are fitted onto the eccentric part of the crankshaft, and the cylinder is fitted onto the outer circumference of the rollers, forming a crescent-shaped working chamber. The vanes are pressed against the rollers by back pressure and the force of the springs, so that the ends of the vanes are in close contact with the rollers, dividing the crescent-shaped working chamber into two chambers. The chamber connected to the intake port of the cylinder is called the intake chamber, and the other chamber is called the compression chamber. The motor controls the crankshaft to rotate, and the eccentric wheel drives the rollers to roll, thereby changing the volume of the intake chamber and the compression chamber, completing the three-stage cycle of intake, compression, and exhaust. The upper flange is located on the upper end face of the cylinder and fitted onto the crankshaft, and the lower flange is located on the lower end face of the cylinder and fitted onto the crankshaft.

[0004] To improve energy efficiency, existing rotary compressors either increase the thickness of the motor core to enhance motor efficiency or reduce the crankshaft diameter to improve mechanical transmission efficiency. However, when increasing the motor core thickness significantly increases the axial magnetic pull and radial centrifugal force from the motor core, it intensifies the load on the upper and lower flanges, particularly the lower flange. Conversely, reducing the crankshaft diameter reduces the crankshaft's structural stiffness, exacerbating elastic deformation during rotation. This leads to stress concentration in the contact areas between the crankshaft and the upper and lower flanges (especially between the crankshaft thrust face and the flange end face), disrupting the stability of the lubricating oil film and causing poor lubrication, increased friction, and even localized wear and component failure. Therefore, existing rotary compressors struggle to balance energy efficiency with mechanical reliability and structural durability, particularly addressing stress concentration issues caused by load concentration. Summary of the Invention

[0005] To achieve the first objective of this invention, a flange structure is provided. By incorporating a high-rigidity and deformation-resistant bearing on the flange body to actively compensate for the stiffness of the crankshaft, the structure can withstand the combined loads of axial magnetic pull and radial centrifugal force caused by the thickening of the motor core. Furthermore, it effectively disperses the localized stress originally concentrated on the contact surface between the flange body and the crankshaft to the contact area of ​​the bearing, thereby significantly reducing the peak contact stress. This fundamentally alleviates the stress concentration problem caused by load concentration on the flange body and effectively maintains a stable fit clearance between the crankshaft and the bearing, preventing elastic deformation of the crankshaft that could lead to oil film rupture and dry friction. Ultimately, this significantly improves the stability and durability of the system, achieving a synergistic optimization between high efficiency, energy saving, and structural reliability.

[0006] To achieve the second objective of the present invention, the present invention provides a pump body assembly having the above-described flange structure.

[0007] To achieve the third objective of the present invention, the present invention provides an energy-saving gas compressor having the above-described pump body assembly.

[0008] To achieve the fourth objective of the present invention, the present invention provides a heat exchange system having the above-described compressor.

[0009] To achieve the first objective of this invention, a flange structure is provided, comprising a flange body and a bearing. The flange body has a through-hole for fitting onto the shaft of a crankshaft. A mounting ring groove is formed on the support end face of the flange body near the eccentric portion of the crankshaft. The mounting ring groove is coaxial with and communicates with the fitting hole. The bearing includes an outer ring, an inner ring, and multiple rolling elements. The outer ring is fixed in the mounting ring groove with an interference fit to the groove wall. The inner ring is fitted onto the shaft and forms a raceway groove between the inner ring and the outer ring in a rotatable manner relative to the outer ring. The multiple rolling elements are arranged circumferentially in the raceway groove, and the rotation axis of each rolling element is inclined outward from the support end face of the flange body toward the fitting hole.

[0010] As can be seen from the above scheme, the crankshaft shaft is stably supported on the bearing of the flange structure of the present invention. The bearing has excellent load-bearing capacity, fatigue resistance, and resistance to plastic deformation. Because the rotation axis of the rolling elements of the bearing is inclined outward from the support end face of the flange body toward the mounting hole, that is, the rotation axis of the rolling elements of the bearing is inclined outward from the eccentric part of the crankshaft, it can withstand the combined loads such as axial magnetic pull and radial centrifugal force caused by the thickening of the motor core, and can effectively disperse the local stress originally concentrated on the contact surface between the flange body and the crankshaft to the bearing. The bearing contact area is significantly reduced, thereby significantly reducing the peak contact stress and fundamentally alleviating the stress concentration problem caused by load concentration in the flange body. This greatly improves the structural durability and fatigue life of the flange structure of the present invention. Furthermore, the outer ring of the bearing in the flange structure of the present invention is fixed in the mounting ring groove with an interference fit to the groove wall of the mounting ring groove of the flange body, ensuring no gaps or looseness after assembly. This effectively maintains a stable fit clearance between the crankshaft and the bearing, preventing the crankshaft from elastically deforming and causing the risk of oil film rupture and dry friction, thereby significantly improving the stability and durability of the system operation.

[0011] Therefore, the flange structure of this invention, by setting a bearing with high rigidity and strong deformation resistance on the flange body to actively compensate for the stiffness of the crankshaft, can withstand the combined loads such as axial magnetic pull and radial centrifugal force caused by the thickening of the motor core. It can also effectively disperse the local stress originally concentrated on the contact surface between the flange body and the crankshaft to the contact area of ​​the bearing, thereby significantly reducing the peak contact stress, alleviating the stress concentration problem caused by load concentration, and effectively maintaining a stable fit clearance between the crankshaft and the bearing, preventing the crankshaft from elastically deforming and causing the risk of oil film rupture and dry friction. This significantly improves the stability and durability of the system operation, ensuring that the compressor has excellent dynamic stability and long-term durability in a high-efficiency and energy-saving operating state, and achieving synergistic optimization between high efficiency and energy saving and structural reliability.

[0012] A further embodiment is that a first convex ring is provided on the outer periphery of the first end of the inner ring near the eccentric part, and a second convex ring is provided on the outer periphery of the second end of the inner ring away from the eccentric part. A limiting ring groove is formed between the first convex ring and the second convex ring, and the inner side of the rolling element near the inner ring is supported in the limiting ring groove.

[0013] A further option is to have multiple limiting grooves on the inner wall of the outer ring, with the multiple limiting grooves arranged in the circumferential direction of the outer ring, and a rolling element supported in the limiting groove near the outer side of the outer ring.

[0014] A further option is to arrange multiple limiting grooves at equal intervals along the circumference of the outer ring.

[0015] A further embodiment is that the first end of the outer ring near the eccentric portion and the first end of the inner ring near the eccentric portion have a first opening that communicates with the raceway groove. The bearing also includes an end cover, which seals and covers the first opening.

[0016] A further embodiment is that the first end face of the outer ring near the eccentric portion is flush with the supporting end face of the flange body, and the first end face of the inner ring near the eccentric portion is recessed away from the eccentric portion and has a first discontinuity with the supporting end face of the flange body. The end cover includes an outer ring plate, a cover ring plate and an inner ring plate connected in sequence. The outer ring plate abuts against the peripheral wall of the inner hole of the first end of the outer ring near the eccentric portion. The cover ring plate covers the first opening and is flush with the supporting end face of the flange body. The inner ring plate abuts against the first end face of the inner ring near the eccentric portion and is used to be sleeved on the shaft.

[0017] A further option is to extend the outer ring plate parallel to the rotation axis of the rolling elements.

[0018] A further embodiment is that the second end of the outer ring away from the eccentric part and the second end of the inner ring away from the eccentric part have a second opening that communicates with the raceway groove. An oil storage groove that communicates with the second opening is opened at the bottom end of the groove adjacent to the mounting hole. An oil guide groove that communicates with the oil storage groove is opened on the peripheral wall of the mounting hole.

[0019] A further option is that the second end face of the outer ring, away from the eccentric part, is recessed near the eccentric part and has a second discontinuity with the bottom end face of the mounting ring groove; the second end face of the inner ring, away from the eccentric part, is flush with the bottom end face of the mounting ring groove and is opposite to the oil storage ring groove.

[0020] A further option is that the outer ring is made of high-carbon chromium bearing steel by heat treatment; and / or, the inner ring is made of high-carbon chromium bearing steel by heat treatment.

[0021] A further option is to use a cylinder as the rolling element.

[0022] A further option is to set the angle of inclination between the axis of rotation of the rolling element and the axis of the shaft to be between 10° and 20°.

[0023] A further proposed solution is to set the angle of inclination between the axis of rotation of the rolling element and the axis of the shaft to be 15°.

[0024] To achieve the second objective of the present invention, the present invention provides a pump body assembly, including a crankshaft, a cylinder, rollers, an upper flange, and a lower flange. The rollers are sleeved on the eccentric portion of the crankshaft, the cylinders are sleeved on the outer periphery of the rollers, the upper flanges are sleeved on the shaft of the crankshaft and located at the upper end of the cylinder, and the lower flanges are sleeved on the shaft and located at the lower end of the cylinder. At least one of the upper flanges and the lower flanges is a flange structure as described in any one of the preceding claims.

[0025] A further embodiment is that the lower flange is a flange structure according to any one of the above claims, the bushing hole of the upper flange is fitted onto the shaft, an oil storage groove is provided at one end of the bushing hole adjacent to the eccentric part, an oil supply channel is provided inside the shaft, and an oil guide hole is provided on the shaft, the oil guide hole connecting the oil storage groove and the oil supply channel.

[0026] A further option is to provide a vibration damping ring groove on the inner groove surface of the oil storage tank away from the eccentric part, and the vibration damping ring groove is connected to the oil storage tank.

[0027] To achieve the third objective of the present invention, the present invention provides a compressor including a pump body assembly, wherein the pump body assembly is as described above.

[0028] To achieve the fourth objective of this invention, this invention provides a heat exchange system including a compressor, wherein the compressor is the compressor described above. Attached Figure Description

[0029] Figure 1 This is a cross-sectional view of an embodiment of the compressor of the present invention.

[0030] Figure 2 This is a cross-sectional view of the pump body assembly in an embodiment of the compressor of the present invention.

[0031] Figure 3 This is a cross-sectional view of the upper flange in an embodiment of the compressor of the present invention.

[0032] Figure 4 This is a cross-sectional view of the compressor embodiment of the present invention, where the lower flange is a flange structure.

[0033] Figure 5 yes Figure 4 Sectional view at AA.

[0034] Figure 6 yes Figure 5 Enlarged view at point D.

[0035] Figure 7 yes Figure 4 Sectional view at BB.

[0036] Figure 8 yes Figure 7 Enlarged view at point E.

[0037] Figure 9 yes Figure 4 Enlarged view at point C.

[0038] Figure 10 This is an exploded view of the compressor embodiment of the present invention, showing that the lower flange is a flange structure.

[0039] Figure 11 This is an exploded view of the load-bearing bearing with a flange structure in the compressor embodiment of the present invention.

[0040] Figure 12 This is a structural diagram of the flange body, where the lower flange is a flange structure, in an embodiment of the compressor of the present invention.

[0041] The present invention will be further described below with reference to the accompanying drawings and embodiments. Detailed Implementation

[0042] Various exemplary embodiments of the invention will now be described in detail with reference to the accompanying drawings. The descriptions of the exemplary embodiments are merely illustrative and are in no way intended to limit the invention or its application or use. The invention can be embodied in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the invention thorough and complete, and to fully express the scope of the invention to those skilled in the art. It should be noted that, unless otherwise specifically stated, the relative arrangement of components and steps, the composition of materials, numerical expressions, and values ​​set forth in these embodiments should be interpreted as merely exemplary and not as limiting.

[0043] The terms "first," "second," and similar words used in this invention do not indicate any order, quantity, or importance, but are merely used to distinguish different parts. Words such as "including" or "comprising" mean that the element preceding the word encompasses the element listed after it, without excluding the possibility of encompassing other elements. Terms such as "upper," "lower," "left," and "right" are used only to indicate relative positional relationships; when the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0044] In this invention, when a specific device is described as being located between a first device and a second device, an intermediary device may or may not be present between the specific device and the first or second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other devices without an intermediary device, or it may not be directly connected to the other devices but may have an intermediary device.

[0045] All terms used in this invention (including technical or scientific terms) have the same meaning as understood by one of ordinary skill in the art, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries should be interpreted as having the meaning consistent with their meaning in the context of the relevant art, and not as having an idealized or highly formalized meaning, unless expressly defined herein.

[0046] Techniques, methods, and equipment known to those skilled in the art may not be discussed in detail, but where appropriate, they should be considered part of the specification.

[0047] See Figures 1 to 12This embodiment discloses a compressor, including a pump body assembly 13, a motor 12 and a housing 11, wherein the motor 12 and the pump body assembly 13 are disposed inside the housing 11.

[0048] In this embodiment, the pump body assembly 13 includes a crankshaft, a cylinder 134, a roller 135, an upper flange 132, and a lower flange. The roller 135 is fitted onto the eccentric portion 1312 of the crankshaft, the cylinder 134 is fitted onto the outer periphery of the roller 135, the upper flange 132 is fitted onto the shaft 1311 of the crankshaft and located at the upper end of the cylinder 134, and the lower flange is fitted onto the shaft 1311 and located at the lower end of the cylinder 134. Furthermore, the pump body assembly 13 in this embodiment also includes a vane 136 and a spring, with the vane 136 located within the vane groove of the cylinder 134.

[0049] The rotor 121 of the motor 12 is sleeved on the crankshaft shaft 1311, thereby driving the crankshaft shaft 1311 to rotate. The eccentric part 1312 of the crankshaft drives the roller 135 to roll along the inner wall of the cylinder 134, thereby forming a crescent-shaped working cavity between the roller 135 and the inner wall of the cylinder 134. The slide 136 is pressed against the back and the force of the spring so that its end is in close contact with the roller 135, thereby dividing the crescent-shaped working cavity into two chambers. The chamber connected to the intake port of the cylinder 134 is called the intake chamber, and the other chamber is called the compression chamber. As the eccentric part 1312 of the crankshaft drives the roller 135 to roll along the inner wall of the cylinder 134, the volume of the intake chamber and the compression chamber changes, thereby completing the three-stage cycle of intake, compression and exhaust.

[0050] Specifically, in this embodiment, the lower flange is flange structure 133.

[0051] In this embodiment, the flange structure 133 includes a flange body 1331 and a bearing 1332. The flange body 1331 has a through-hole 13311 for fitting onto the crankshaft shaft 1311. A mounting annular groove 13312 is formed on the support end face of the flange body 1331 near the eccentric portion 1312 of the crankshaft. The mounting annular groove 13312 is coaxial with and communicates with the through-hole 13311. The bearing 1332 includes an outer ring 13321, an inner ring 13322, and multiple rolling elements 13323. The outer ring 13321 is connected to the mounting annular groove 13322. The groove circumferential wall of the annular groove 13312 is fixedly installed in the mounting annular groove 13312 with an interference fit. The inner ring 13322 is used to be sleeved and fixed on the shaft 1311. The inner ring 13322 rotatably forms a raceway annular groove 13325 with the outer ring 13321. Multiple rolling elements 13323 are arranged circumferentially in the raceway annular groove 13325. The rotation axis 133231 of each rolling element 13323 is inclined outward from the support end face of the flange body 1331 toward the fitting hole 13311.

[0052] Thus, the crankshaft shaft 1311 is stably supported on the bearing 1332 of the flange structure 133 in this embodiment. The bearing 1332 has excellent load-bearing capacity, fatigue resistance, and resistance to plastic deformation. Because the rotation axis 133231 of the rolling elements 13323 of the bearing 1332 is inclined outward from the support end face of the flange body 1331 toward the fitting hole 13311, that is, the rotation axis 133231 of the rolling elements 13323 of the bearing 1332 is inclined outward from the eccentric part 1312 of the crankshaft, it can withstand the combined loads such as the axial magnetic pull and radial centrifugal force brought about by the thickening of the iron core of the motor 12, and can dissipate the local stress originally concentrated on the contact surface between the flange body 1331 and the crankshaft. The force is effectively dispersed to the contact area of ​​the bearing 1332, thereby significantly reducing the peak contact stress and fundamentally alleviating the stress concentration problem caused by load concentration in the flange body 1331. This greatly improves the structural durability and fatigue life of the flange structure 133 in this embodiment. Furthermore, the outer ring 13321 of the bearing 1332 of the flange structure 133 is fixed in the mounting ring groove 13312 of the flange body 1331 with an interference fit, ensuring no gaps or looseness after assembly. This effectively maintains a stable fit clearance between the crankshaft and the bearing 1332, preventing the crankshaft from undergoing elastic deformation and causing oil film rupture and dry friction risks, thereby significantly improving the stability and durability of the system operation.

[0053] Therefore, in this embodiment, the flange structure 133, by setting a bearing 1332 with high rigidity and strong deformation resistance on the flange body 1331, actively compensates for the stiffness of the crankshaft. It can withstand the combined loads such as axial magnetic pull and radial centrifugal force caused by the thickening of the motor 12 core, and can effectively disperse the local stress originally concentrated on the contact surface between the flange body 1331 and the crankshaft to the contact area of ​​the bearing 1332, thereby significantly reducing the peak contact stress, alleviating the stress concentration problem caused by load concentration, and effectively maintaining a stable fit clearance between the crankshaft and the bearing 1332, preventing the crankshaft from elastically deforming and causing the risk of oil film rupture and dry friction. This significantly improves the stability and durability of the system operation, ensuring that the compressor has excellent dynamic stability and long-term durability in a high-efficiency and energy-saving operating state, and achieving synergistic optimization between high efficiency and energy saving and structural reliability.

[0054] To further enhance the load-bearing capacity, fatigue resistance, and resistance to plastic deformation of the bearing 1332, in this embodiment, the outer ring 13321 of the bearing 1332 is made of high-carbon chromium bearing steel through heat treatment to strengthen the rigidity of the outer ring 13321. Furthermore, in this embodiment, the inner ring 13322 of the bearing 1332 is also made of high-carbon chromium bearing steel through heat treatment to further strengthen the rigidity of the inner ring 13322. Moreover, in this embodiment, the angle θ between the rotation axis 133231 of the rolling element 13323 and the axis of the shaft 1311 is between 10° and 20°. Preferably, the angle θ between the rotation axis 133231 of the rolling element 13323 and the axis of the shaft 1311 is 15°, resulting in a better stress dispersion effect.

[0055] To prevent the rolling element 13323 from shifting along the rotation axis 133231 and affecting the working reliability and stability of the bearing 1332, in this embodiment, the inner ring 13322 of the bearing 1332 has a first protruding ring 133221 protruding from the outer periphery of the first end near the eccentric portion 1312, and a second protruding ring 133222 protruding from the outer periphery of the second end away from the eccentric portion 1312. A limiting ring groove is formed between the first protruding ring 133221 and the second protruding ring 133222. The inner side of the rolling element 13323 near the inner ring 13322 is supported in the limiting ring groove, thereby stably restricting the rolling element 13323 within the limiting ring groove along the rotation axis 133231, thereby improving the working reliability and stability of the rolling element 13323.

[0056] To prevent the rolling elements 13323 from shifting circumferentially in the raceway groove 13325 and affecting the operational reliability and stability of the bearing 1332, this embodiment provides multiple limiting grooves 133211 on the inner wall of the outer ring 13321 of the bearing 1332. These limiting grooves are arranged circumferentially on the outer ring 13321. A rolling element 13323 is supported within the limiting groove 133211 near the outer side of the outer ring 13321, thus stably limiting each rolling element 13323 to a predetermined position circumferentially in the raceway groove 13325, thereby improving the operational reliability and stability of the rolling element 13323. Specifically, in this embodiment, the multiple limiting grooves 133211 are evenly spaced circumferentially on the outer ring 13321 to improve the circumferential performance uniformity of the bearing 1332, thereby improving the balance performance of the bearing 1332.

[0057] In order to further improve the load-bearing capacity and stress dispersion capacity of the rolling element 13323, the rolling element 13323 in this embodiment is a cylinder.

[0058] Combination Figures 9 to 11 In this embodiment, the outer ring 13321 of the bearing 1332 near the first end of the eccentric portion 1312 and the inner ring 13322 near the first end of the eccentric portion 1312 have a first opening 13326 that communicates with the raceway groove 13325. Furthermore, the bearing 1332 in this embodiment also includes an end cap 13324, which seals the first opening 13326 to prevent foreign objects from entering the raceway groove 13325 from the first opening 13326 and affecting the smooth rotation of the rolling element 13323, and to prevent the lubricating oil in the raceway groove 13325 from leaking from the first opening 13326 and affecting the smooth rotation of the rolling element 13323. In addition, the end cap 13324 also plays a role in bearing and stress dispersion, thereby further improving the bearing capacity and stress dispersion capacity of the bearing 1332.

[0059] Specifically, in this embodiment, the first end face of the outer ring 13321 of the bearing 1332 near the eccentric portion 1312 is flush with the support end face of the flange body 1331. The first end face of the inner ring 13322 of the bearing 1332 near the eccentric portion 1312 is recessed away from the eccentric portion 1312 and has a first discontinuity with the support end face of the flange body 1331. Furthermore, in this embodiment, the end cover 13324 of the bearing 1332 includes an outer ring plate 133243, a cover ring plate 133242, and an inner ring plate 133241 connected in sequence. The outer ring plate 133243 and... The outer ring 13321 abuts against the inner wall of the first end hole near the eccentric portion 1312. The cover ring plate 133242 covers the first opening 13326 and is flush with the supporting end face of the flange body 1331. The inner ring plate 133241 abuts against the first end face of the inner ring 13322 near the eccentric portion 1312 and is used to be sleeved on the shaft 1311. This forms a first oil storage cavity between the end cover 13324 and the first end face of the inner ring 13322, which communicates with the raceway annular groove 13325, thereby improving the lubrication effect of the rolling element 13323 in the raceway annular groove 13325. In this embodiment, the outer ring plate 133243 of the end cover 13324 extends parallel to the rotation axis 133231 of the rolling element 13323 to improve the stress dispersion capability of the end cover 13324.

[0060] Furthermore, in this embodiment, the second end of the outer ring 13321 of the bearing 1332 away from the eccentric portion 1312 and the second end of the inner ring 13322 away from the eccentric portion 1312 have a second opening 13327 communicating with the raceway annular groove 13325. An oil storage annular groove 13313 communicating with the second opening 13327 is formed at the bottom end of the mounting annular groove 13312 adjacent to the fitting hole 13311. The peripheral wall of the fitting hole 13311 is provided with an oil storage annular groove 13325. The interconnected oil guide grooves 13314 form a continuous and stable lubrication supply path from the oil guide groove 13314 to the oil storage ring groove 13313 to the raceway ring groove 13325. This ensures the continuous lubrication reliability of the bearing 1332 under high speed and heavy load conditions, and ensures that the bearing 1332 can maintain a stable oil film under various operating conditions. This effectively alleviates impact loads, suppresses friction and wear, and significantly improves the service life of the bearing 1332 and the stability of system operation. In this embodiment, there are at least two oil guide grooves 13314. Multiple oil guide grooves 13314 are evenly distributed on the circumferential wall of the mounting hole 13311 in the circumferential direction, so as to achieve the even distribution and efficient introduction of lubricating oil into the oil storage ring groove 13313 during rotation to supply the raceway ring groove 13325.

[0061] Furthermore, in this embodiment, the second end face of the outer ring 13321 of the bearing 1332 away from the eccentric portion 1312 is recessed near the eccentric portion 1312 and has a second discontinuity with the bottom end face of the mounting ring groove 13312. The second end face of the inner ring 13322 away from the eccentric portion 1312 is flush with the bottom end face of the mounting ring groove 13312 and is opposite to the oil storage ring groove 13313, so that a second oil storage cavity is formed between the bottom end face of the mounting ring groove 13312 and the second end face of the outer ring 13321, which connects the raceway ring groove 13325 and the oil storage ring groove 13313, thereby improving the lubrication effect of the rolling element 13323 in the raceway ring groove 13325.

[0062] Combination Figure 2 and 3 In this embodiment, the bushing hole 1321 of the upper flange 132 is fitted onto the shaft 1311. An oil storage groove 1322 is provided at one end of the bushing hole 1321 adjacent to the eccentric part 1312. An oil supply channel 13111 is provided inside the shaft 1311, and an oil guide hole 13112 is provided in the shaft 1311. The oil guide hole 13112 connects the oil storage groove 1322 and the oil supply channel 13111. Thus, the lubricating oil in the oil supply channel 13111 of the shaft 1311 is sent from the oil guide hole 13112 to the oil storage groove 1322 of the upper flange 132. The lubricating oil in the oil storage groove 1322 is sent upward to the gap between the bushing hole 1321 of the upper flange 132 and the shaft 1311 to form an oil film, effectively improving the lubrication effect between the upper flange 132 and the shaft 1311.

[0063] In addition, in this embodiment, a damping ring groove 1323 is provided on the inner groove surface of the oil storage tank 1322 away from the eccentric part 1312. The damping ring groove 1323 is connected to the oil storage tank 1322, so that the cross section of the oil storage tank 1322 and the damping ring groove 1323 in the axial direction of the shaft 1311 presents a "U" shape. This is mainly to reduce the contact stress between the shaft 1311 and the hole wall of the bushing hole 1321, thereby reducing wear and vibration.

[0064] The above embodiments are merely preferred examples of the present invention and are not intended to limit the scope of the present invention. Therefore, all equivalent changes or modifications made to the structure, features and principles of the present invention in accordance with the claims of the present invention should be included in the scope of the present invention patent application.

Claims

1. A flange structure, comprising a flange body, wherein the flange body has a through-hole for fitting onto a crankshaft shaft, characterized in that: The flange body has a mounting ring groove on the support end face near the eccentric part of the crankshaft. The mounting ring groove is coaxial with and connected to the fitting hole. The flange structure also includes a bearing, which comprises an outer ring, an inner ring, and multiple rolling elements. The outer ring is fixedly disposed in the mounting ring groove with an interference fit to the groove wall of the mounting ring groove. The inner ring is used to be sleeved and fixed on the shaft, and a raceway groove is formed between the inner ring and the outer ring in a rotatable manner relative to the outer ring. The multiple rolling elements are arranged circumferentially in the raceway groove, and the rotation axis of each rolling element is inclined outward from the support end face of the flange body toward the fitting hole.

2. The flange structure according to claim 1, characterized in that: The inner ring has a first protruding ring protruding from the outer periphery of the first end near the eccentric portion, and a second protruding ring protruding from the outer periphery of the second end away from the eccentric portion. A limiting ring groove is formed between the first protruding ring and the second protruding ring, and the inner side of the rolling element near the inner ring is supported in the limiting ring groove.

3. The flange structure according to claim 1, characterized in that: The inner wall of the outer ring is provided with multiple limiting grooves, which are arranged in the circumferential direction of the outer ring. One of the rolling elements is supported in the limiting groove near the outer side of the outer ring.

4. The flange structure according to claim 3, characterized in that: The plurality of the limiting grooves are arranged at equal intervals in the circumferential direction of the outer ring.

5. The flange structure according to claim 1, characterized in that: The outer ring has a first opening that communicates with the raceway groove between the first end of the outer ring near the eccentric portion and the first end of the inner ring near the eccentric portion. The bearing also includes an end cap, which is sealed and closed at the first opening.

6. The flange structure according to claim 5, characterized in that: The first end face of the outer ring near the eccentric portion is flush with the support end face of the flange body, and the first end face of the inner ring near the eccentric portion is recessed away from the eccentric portion and has a first discontinuity with the support end face of the flange body. The end cap includes an outer ring plate, a cover ring plate, and an inner ring plate connected in sequence. The outer ring plate abuts against the peripheral wall of the first end hole of the outer ring near the eccentric portion. The cover ring plate covers the first opening and is flush with the supporting end face of the flange body. The inner ring plate abuts against the first end face of the inner ring near the eccentric portion and is used to be sleeved on the shaft.

7. The flange structure according to claim 6, characterized in that: The outer ring plate extends parallel to the rotation axis of the rolling element.

8. The flange structure according to claim 5, characterized in that: The second end of the outer ring away from the eccentric portion and the second end of the inner ring away from the eccentric portion have a second opening that communicates with the raceway groove. The bottom end of the mounting groove adjacent to the fitting hole has an oil storage groove that communicates with the second opening. The peripheral wall of the fitting hole has an oil guide groove that communicates with the oil storage groove.

9. The flange structure according to claim 8, characterized in that: The second end face of the outer ring, away from the eccentric portion, is recessed near the eccentric portion and has a second discontinuity with the bottom end face of the mounting ring groove. The second end face of the inner ring, away from the eccentric portion, is flush with the bottom end face of the mounting ring groove and is opposite to the oil storage ring groove.

10. The flange structure according to claim 1, characterized in that: The outer ring is made of high-carbon chromium bearing steel through heat treatment; And / or, the inner ring is made of high-carbon chromium bearing steel through heat treatment.

11. The flange structure according to claim 1, characterized in that: The rolling element is a cylinder.

12. The flange structure according to any one of claims 1 to 11, characterized in that: The angle of inclination between the axis of rotation of the rolling element and the axis of the shaft is between 10° and 20°.

13. The flange structure according to claim 12, characterized in that: The angle of inclination between the axis of rotation of the rolling element and the axis of the shaft is 15°.

14. A pump body assembly, comprising a crankshaft, a cylinder, rollers, an upper flange, and a lower flange, wherein the rollers are sleeved on the eccentric portion of the crankshaft, the cylinders are sleeved on the outer periphery of the rollers, the upper flanges are sleeved on the shaft of the crankshaft and located at the upper end of the cylinder, and the lower flanges are sleeved on the shaft and located at the lower end of the cylinder, characterized in that: At least one of the upper flange and the lower flange is a flange structure as described in any one of claims 1 to 13.

15. The pump body assembly according to claim 14, characterized in that: The lower flange is the flange structure described in any one of claims 1 to 13 above; The upper flange has a bushing hole fitted onto the shaft. An oil storage groove is provided at one end of the bushing hole adjacent to the eccentric part. An oil supply channel is provided inside the shaft, and an oil guide hole is provided on the shaft. The oil guide hole connects the oil storage groove and the oil supply channel.

16. The pump body assembly according to claim 15, characterized in that: The oil storage tank has a vibration damping ring groove on its inner groove surface away from the eccentric part, and the vibration damping ring groove is connected to the oil storage tank.

17. A compressor, including a pump body assembly, characterized in that: The pump assembly is the pump assembly described in any one of claims 14 to 16.

18. A heat exchange system, including a compressor, characterized in that: The compressor is the compressor described in claim 17.

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