Bearing structure and chiller

Abstract

The present invention provides a bearing structure and a chiller, wherein the bearing structure comprises a bearing body having a bearing hole, wherein the inner wall surface of the bearing hole is provided with a plurality of strip grooves arranged at intervals along the circumference of the bearing hole, wherein the two ends of each strip groove are respectively a first end and a second end and are respectively extended toward the two ends of the bearing hole; the second end of each strip groove deviates from the first end thereof along the circumference of the bearing hole by a predetermined angle. By providing a plurality of strip grooves, the liquid film structure formed when the bearing structure of the present application adopts a refrigerant-lubricated bearing is relatively stable, thereby solving the problem that the liquid film formed by the refrigerant-lubricated bearing in the prior art is easily broken.

Description

Technical Field

[0001] The present invention relates to the technical field of bearings, and in particular to a bearing structure and a chiller. Background Art

[0002] At present, oil-lubricated bearings dominate centrifugal chillers. However, due to the presence of lubricating oil, the oil lubrication system and oil separation system of oil supply and return must be considered during the design of the chiller, which increases the complexity of design, manufacturing, maintenance and control, and greatly increases the initial cost and operation and maintenance cost. Lubricating oil leakage will also cause environmental pollution. At the same time, the lubricating oil enters the evaporator and condenser with the refrigerant, affecting the heat exchange effect and system energy efficiency, and will cause the performance of the unit to degrade after long-term operation. Therefore, oil-free is the development direction of centrifugal chillers.

[0003] At present, there are three main development directions for oil-free operation: air bearings, magnetic bearings, and refrigerant-lubricated bearings. Air bearings are only suitable for small cooling units due to their high speed and light load characteristics. Magnetic bearings have many sensors and complex control systems, and cannot completely solve the reliability problem of units in the event of sudden power outages. The refrigerant bearing solution achieves oil-free operation of the chiller by using pure refrigerant-lubricated bearings, which improves the energy efficiency of the chiller, greatly simplifies the system design, reduces the system manufacturing and maintenance costs, and eliminates the environmental problems caused by lubricating oil. Due to these advantages, refrigerant-lubricated bearings are increasingly being studied and applied in chillers.

[0004] Refrigerant-lubricated bearings form a liquid film based on fluid dynamic pressure, that is, they rely on the high-speed relative motion between the shaft and the bearing to bring the refrigerant on the friction surface into the wedge-shaped gap to form a high-pressure water film, thereby separating the two friction surfaces of the shaft and the bearing and reducing the wear of the bearing. However, due to the large differences in the physical and chemical properties between refrigerants and traditional lubricants, refrigerants have the characteristics of low viscosity, poor lubricity, and high volatility. As a result, when refrigerant lubrication is used, the refrigerant liquid film formed between the bearing gaps is very thin and easy to break, which can easily lead to wear and poor service life of the sliding bearing, bringing many difficulties to the design and development of centrifugal chillers. Summary of the invention

[0005] The main purpose of the present invention is to provide a bearing structure and a chiller to solve the problem that the liquid film formed by the refrigerant-lubricated bearing in the prior art is easy to rupture.

[0006] In order to achieve the above-mentioned purpose, according to one aspect of the present invention, a bearing structure is provided, which includes a bearing body having a bearing hole, and the inner wall surface of the bearing hole is provided with a plurality of strip grooves arranged at intervals along the circumference of the bearing hole, and the two ends of each strip groove are respectively a first end and a second end and extend toward the two ends of the bearing hole respectively; the second end of each strip groove deviates from its first end by a predetermined angle along the circumference of the bearing hole.

[0007] Furthermore, the second ends of the plurality of strip grooves are all deviated in the clockwise direction or are all deviated in the counterclockwise direction; and / or both ends of each strip groove extend to the two end surfaces of the bearing hole respectively; and / or the number of the strip grooves is an even number.

[0008] Furthermore, each strip groove has a longitudinal section perpendicular to its extension direction, and the shape of the longitudinal section is any one of a trapezoid, a rectangle, and a triangle; or the outer periphery of the longitudinal section is a part of a predetermined circle; or the outer periphery of the longitudinal section is a part of a predetermined ellipse.

[0009] Furthermore, each strip groove extends along a predetermined curve or a predetermined straight line, the predetermined curve is a smooth curve; the predetermined angle ranges from 20 degrees to 40 degrees; and / or the length of the bearing body along its axial direction is L, the inner diameter of the bearing hole is D, the aspect ratio is L / D, and the aspect ratio ranges from 1.8 to 2.

[0010] Furthermore, each strip groove extends along a predetermined curve, and the predetermined curve includes a first smooth curve segment, a second line segment, and a third smooth curve segment connected in sequence, and the second line segment is a smooth curve segment or a straight line segment; the first smooth curve segment has a connecting end connected to the second line segment and a free end away from the second line segment, and the free end of the first smooth curve segment forms the first end of the strip groove, and the connecting end of the first smooth curve segment deviates from the circumference of the bearing hole by a first set angle relative to its free end, and the first set angle is an acute angle, and the deviation direction of the connecting end of the first smooth curve segment is the same as the deviation direction of the second end of the strip groove; and / or the second line segment has a first end connected to the first smooth curve segment and a free end away from the first smooth curve segment. The second end of the curved segment, the second end of the second line segment deviates from its first end along the circumference of the bearing hole by a second set angle, the second set angle is an acute angle, and the deviation direction of the second end of the second line segment is the same as the deviation direction of the second end of the strip groove; and / or the third smooth curve segment has a connecting end connected to the second line segment and a free end away from the second line segment, the free end of the third smooth curve segment forms the second end of the strip groove, the free end of the third smooth curve segment deviates from its connecting end along the circumference of the bearing hole by a third set angle, the third set angle is an acute angle, and the deviation direction of the free end of the third smooth curve segment relative to its connecting end is the same as the deviation direction of the second end of the strip groove relative to its first end.

[0011] Further, the first set angle has a value range of 25 degrees to 50 degrees; and / or the second set angle has a value range of 15 degrees to 25 degrees; and / or the third set angle has a value range of 25 degrees to 50 degrees; and / or the length along the axial direction of the bearing body between the connecting end and the free end of the first smooth curve segment is 1 / 6 of the length of the bearing body along its axial direction; and / or the length along the axial direction of the bearing body between the connecting end and the free end of the third smooth curve segment is 1 / 6 of the length of the bearing body along its axial direction; and / or the length of the bearing body along its axial direction is L, the inner diameter of the bearing hole is D, the aspect ratio is L / D, and the aspect ratio ranges from 1.8 to 2.

[0012] Furthermore, the hole radius of the bearing hole is R, the radius of the rotating shaft arranged in the bearing hole is r, and the radius gap δ is (Rr); the distance between the centerline of the bearing hole and the central axis of the rotating shaft is the eccentricity, the eccentricity is the ratio of the eccentricity to the radius gap, and the eccentricity ranges from 0.5 to 0.8; and / or the relative gap is C, C = (Rr) / R, and the value range of C is 0.5% to 2%.

[0013] Furthermore, the outer wall surface of the bearing body is provided with a plurality of annular grooves spaced apart along the axial direction of the bearing body, and an elastic ring is provided in the annular groove; and / or the bearing body is made of silicon nitride ceramic material; and / or the inner wall surface of the bearing hole is provided with a solid lubrication layer.

[0014] Furthermore, the material components of the solid lubricating layer include polytetrafluoroethylene, graphite, a binder and molybdenum disulfide; wherein the content of polytetrafluoroethylene ranges from 10% to 20%, the content of graphite ranges from 5% to 10%, and the content of the binder ranges from 1% to 3%; the particle size of molybdenum disulfide is less than 10 μm; and / or the thickness of the solid lubricating layer is greater than 0.5 mm.

[0015] According to another aspect of the present invention, a chiller is provided, which includes a compressor, and the compressor includes the above-mentioned bearing structure.

[0016] The technical solution of the present invention is applied, and the bearing structure includes a bearing body having a bearing hole, and the inner wall surface of the bearing hole is provided with a plurality of strip grooves arranged at intervals along the circumference of the bearing hole, and the two ends of each strip groove are respectively a first end and a second end and extend toward the two ends of the bearing hole; the second end of each strip groove deviates from the first end along the circumference of the bearing hole by a predetermined angle. By providing a plurality of strip grooves, the liquid film structure formed when the bearing structure of the present application adopts a refrigerant lubricated bearing is relatively stable, which solves the problem that the liquid film formed by the refrigerant lubricated bearing in the prior art is easy to rupture. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] 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:

[0018] Figure 1 A structural schematic diagram showing a first embodiment of a bearing body of a bearing structure according to the present invention is shown;

[0019] Figure 2 Shows Figure 1 A side structural diagram of a bearing body of the bearing structure in FIG.

[0020] Figure 3 A structural schematic diagram showing a second embodiment of a bearing body of a bearing structure according to the present invention is shown;

[0021] Figure 4 Shows Figure 3 A side structural diagram of a bearing body of the bearing structure in FIG.

[0022] Figure 5 A schematic structural diagram of a third embodiment of a bearing body of a bearing structure according to the present invention is shown;

[0023] Figure 6 A schematic structural diagram showing a fourth embodiment of a bearing body of a bearing structure according to the present invention;

[0024] Figure 7 Shows Figure 6 A side structural diagram of a bearing body of the bearing structure in FIG.

[0025] Figure 8 A schematic structural diagram showing a fifth embodiment of a bearing body of a bearing structure according to the present invention is shown;

[0026] Fig. 9 A schematic diagram of the matching structure between the bearing structure and the rotating shaft according to the present invention is shown;

[0027] Fig.10 A schematic diagram showing the eccentricity between the bearing hole and the rotating shaft of the bearing structure according to the present invention;

[0028] Fig.11 A schematic structural diagram of an elastic ring disposed on a bearing body according to a bearing structure of the present invention is shown.

[0029] The above drawings include the following reference numerals:

[0030] 10. Bearing body; 11. Bearing hole; 12. Strip groove; 121. First groove section; 122. Second groove section; 123. Third groove section; 13. Solid lubrication layer; 14. Elastic ring; 20. Rotating shaft. DETAILED DESCRIPTION

[0031] 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.

[0032] It should be noted that the following detailed descriptions are illustrative and are intended to provide further explanation of the present application. Unless otherwise specified, all technical and scientific terms used herein have the same meanings as those commonly understood by those skilled in the art to which the present application belongs.

[0033] 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.

[0034] The present invention provides a bearing structure, please refer to Figures 1 to 11 The bearing structure includes a bearing body 10 having a bearing hole 11, and the inner wall surface of the bearing hole 11 is provided with a plurality of strip grooves 12 arranged at intervals along the circumference of the bearing hole 11, and the two ends of each strip groove 12 are respectively a first end and a second end and extend toward the two ends of the bearing hole 11; the second end of each strip groove 12 deviates from the first end thereof along the circumference of the bearing hole 11 by a predetermined angle. By providing a plurality of strip grooves 12, the liquid film structure formed when the bearing structure of the present application adopts a refrigerant lubricated bearing is relatively stable, solving the problem that the liquid film formed by the refrigerant lubricated bearing in the prior art is easy to rupture.

[0035] Compared with the ordinary straight groove structure extending axially along the bearing hole 11, the bearing body 10 with the strip groove 12 of the present application can have better heat dissipation characteristics while ensuring a high load-bearing capacity, thereby avoiding the refrigerant from vaporizing due to excessive temperature and affecting the stability of the liquid film. The structure of the strip groove 12 of the present application is conducive to the discharge of the refrigerant from the strip groove 12.

[0036] Specifically, the predetermined angle is an acute angle.

[0037] Specifically, the second ends of the plurality of strip-shaped grooves 12 are all deviated in the clockwise direction or are all deviated in the counterclockwise direction.

[0038] Specifically, two ends of each strip groove 12 extend to two end surfaces of the bearing hole 11 respectively.

[0039] In this embodiment, the number of the strip grooves 12 is an even number, for example, the number of the strip grooves 12 is 4, 6, or 8, and the number of the strip grooves 12 being 6 is the optimal case.

[0040] In this embodiment, each strip groove 12 has a longitudinal section perpendicular to its extension direction. The first arrangement form of the longitudinal section is as follows: Figures 1 to 5 As shown, the shape of the longitudinal section is any one of a trapezoid, a rectangle, and a triangle; when the shape of the longitudinal section is a triangle, the shape of the longitudinal section may preferably be an isosceles triangle; the second setting form of the longitudinal section is: the outer periphery of the longitudinal section is a part of a predetermined circle, and the outer periphery of the longitudinal section is preferably a semicircle; the third setting form of the longitudinal section is: as Figure 6 and Figure 7 As shown, the outer periphery of the longitudinal cross section is a part of a predetermined ellipse, and the outer periphery of the longitudinal cross section is preferably a semi-ellipse.

[0041] During the specific implementation process, when the shape of the longitudinal cross-section of the strip groove 12 is an isosceles triangle, the bearing capacity and lubrication performance of the bearing body 10 are the highest, followed by when the shape of the longitudinal cross-section of the strip groove 12 is a semi-ellipse and when the shape of the longitudinal cross-section of the strip groove 12 is a trapezoid, and again when the shape of the longitudinal cross-section of the strip groove 12 is a rectangle.

[0042] In this embodiment, the first structural form of the strip grooves 12 is: each strip groove 12 extends along a predetermined curve or a predetermined straight line, the predetermined curve is a smooth curve, and the predetermined curve is preferably an arc; the value range of the predetermined angle is 20 degrees to 40 degrees.

[0043] It is found that along the axial direction of the bearing body 10, the liquid film pressure is the largest at the middle position, the liquid film at the position 1 / 6 of the distance from the end of the bearing body 10 and the middle position does not change much, and the liquid film pressure at the position 1 / 6 of the distance from the end of the bearing body 10 and the end of the bearing body 10 drops rapidly; therefore, in this embodiment, the second structural form of the strip groove 12 is: Figure 8 As shown, each strip groove 12 extends along a predetermined curve, and the predetermined curve includes a first smooth curve segment, a second line segment, and a third smooth curve segment connected in sequence, and the second line segment is a smooth curve segment or a straight line segment; the strip groove 12 includes a first groove segment 121, a second groove segment 122, and a third groove segment 123 connected in sequence, and the first groove segment 121, the second groove segment 122, and the third groove segment 123 are respectively arranged in a one-to-one correspondence with the first smooth curve segment, the second line segment, and the third smooth curve segment, that is, the first groove segment 121 extends along the first smooth curve segment, the second groove segment 122 extends along the second line segment, and the third groove segment 123 extends along the third smooth curve segment.

[0044] Optionally, the first smooth curve segment is an arc segment, and the third smooth curve segment is an arc segment; when the second line segment is a smooth curve segment, the second line segment is preferably an arc segment.

[0045] Specifically, the first smooth curve segment has a connecting end connected to the second line segment and a free end away from the second line segment, the free end of the first smooth curve segment forms the first end of the strip groove 12, the connecting end of the first smooth curve segment deviates from the circumference of the bearing hole 11 by a first set angle relative to its free end, the first set angle is an acute angle, and the deviation direction of the connecting end of the first smooth curve segment is the same as the deviation direction of the second end of the strip groove 12; optionally, the value range of the first set angle is 25 degrees to 50 degrees.

[0046] Specifically, the second line segment has a first end connected to the first smooth curve segment and a second end away from the first smooth curve segment. The second end of the second line segment deviates from the first end thereof by a second set angle along the circumference of the bearing hole 11. The second set angle is an acute angle. The deviation direction of the second end of the second line segment is the same as the deviation direction of the second end of the strip groove 12. Optionally, the value range of the second set angle is 15 degrees to 25 degrees.

[0047] Specifically, the third smooth curve segment has a connecting end connected to the second line segment and a free end away from the second line segment, the free end of the third smooth curve segment forms the second end of the strip groove 12, the free end of the third smooth curve segment deviates from its connecting end along the circumference of the bearing hole 11 by a third set angle, the third set angle is an acute angle, and the deviation direction of the free end of the third smooth curve segment relative to its connecting end is the same as the deviation direction of the second end of the strip groove 12 relative to its first end; optionally, the value range of the third set angle is 25 degrees to 50 degrees.

[0048] Specifically, the axial length of the first smooth curve segment between the connecting end and the free end of the bearing body 10 is 1 / 6 of the axial length of the bearing body 10, and the axial length of the third smooth curve segment between the connecting end and the free end of the bearing body 10 is 1 / 6 of the axial length of the bearing body 10.

[0049] With respect to the structural setting of the strip groove 12 of the second structural form, the torsion angle of the second groove section 122 is small, and the length of the strip groove 12 along its extension direction is small, so the contact line between the strip groove 12 and the rotating shaft in the bearing hole 11 along the extension direction of the strip groove 12 is short, and the contact area between the strip groove 12 and the rotating shaft in the bearing hole 11 is small. Then, when the axial length and radius of the bearing hole 11 are constant, the contact area between the hole wall of the bearing hole 11 (the wall surface remaining after removing the strip groove 12) and the rotating shaft is large, and the contact area between the two is proportional to the bearing capacity, that is, the bearing hole 11 is 1, the larger the contact area between the hole wall of the bearing hole 11 and the rotating shaft, the greater the bearing capacity. Therefore, by making the torsion angle of the second groove section 122 smaller, the bearing body 10 can have a higher load-bearing capacity. At the same time, since the torsion angles of the first groove section 121 and the third groove section 123 are larger, the length of the strip groove 12 along its extension direction is longer, and the contact line between the strip groove 12 and the rotating shaft in the bearing hole 11 along the extension direction of the strip groove 12 is longer, and the contact area between the strip groove 12 and the rotating shaft in the bearing hole 11 is larger, thereby making the heat dissipation area of ​​the bearing body 10 larger, thereby enhancing the heat dissipation characteristics.

[0050] When the shaft rotates, a convergent wedge, i.e., a dynamic pressure lubrication film, is formed between the bearing and the shaft, thereby supporting the force applied to the shaft. Since the viscosity of the refrigerant is lower than that of the refrigeration oil, the lubricating liquid film that can be formed in the bearing gap is relatively thin, resulting in a relatively low bearing capacity of the bearing. In addition, the refrigerant itself is easily vaporized when heated or the pressure drops. In the liquid film divergence area, the dynamic pressure effect disappears. When the pressure is lower than the refrigerant vaporization pressure or the refrigerant absorbs more heat, the refrigerant liquid film will cavitate, i.e., vaporize. Cavitation will erode the surface of the shaft, resulting in poor lubrication, causing vibration of the shaft and poor stability of the shaft system. This requires the refrigerant bearing to have good heat dissipation characteristics.

[0051] The main parameters that affect the load-bearing capacity W of water-lubricated sliding bearings are the length-to-diameter ratio L / D of the bearing, the relative clearance C of the bearing, and the eccentricity x of the bearing; among them, Figures 9 to 11 As shown, the length of the bearing body 10 along its axial direction is L, the inner diameter of the bearing hole 11 is D, and the aspect ratio is L / D; the hole radius of the bearing hole 11 is R, the radius of the rotating shaft 20 arranged in the bearing hole 11 is r, and the radius gap δ is (Rr), that is, δ=Rr; the hole centerline P1 of the bearing hole 11 and the central axis P2 of the rotating shaft 20 are parallel to each other, and the distance between the hole centerline P1 of the bearing hole 11 and the central axis P2 of the rotating shaft 20 is the eccentricity e, and the eccentricity x is the ratio of the eccentricity e to the radius gap δ, that is, x=e / δ; C=Rr / R.

[0052] In this embodiment, the eccentricity x ranges from 0.5 to 0.8, and the value range of C is 0.5% to 2%; when each strip groove 12 is of the first structural form, the aspect ratio ranges from 1.8 to 2; when each strip groove 12 is of the second structural form, the aspect ratio ranges from 1.8 to 2, so that the bearing capacity of the bearing structure is relatively high and the heat dissipation characteristics are better.

[0053] Since the clearance of the refrigerant lubricated bearing (the clearance between the bearing and the shaft when the shaft in the bearing hole 11 rotates) is only a dozen microns, the bearing body 10 is required to have good elasticity and vibration absorption, such as Fig.11 As shown, the outer wall surface of the bearing body 10 is provided with a plurality of annular grooves arranged at intervals along the axial direction of the bearing body 10, and an elastic ring 14 is provided in the annular groove; since there is a lubricating oil film between the hole wall of the bearing hole 11 and the rotating shaft 20, the lubricating oil film will generate a certain pressure on the bearing body 10, and the bearing body 10 will float under the action of this pressure. By arranging the elastic ring 14 to adapt to the floating of the bearing body 10 and absorb the pressure generated by the lubricating oil film on the bearing body 10 (that is, the elastic ring 14 has vibration absorption), the bearing body 10 can automatically adjust its position under the elastic action of the elastic ring 14 when working, which is also conducive to the formation of the lubricating liquid film, reducing the vibration of the shaft system and improving the stability of the shaft system.

[0054] Specifically, the elastic ring 14 is a Gley ring, or the material of the elastic ring 14 is polytetrafluoroethylene.

[0055] Since the refrigerant itself has low viscosity, the lubricating liquid film that can be formed in the bearing gap is thin and easy to break, which requires the bearing structure to have good self-lubricating properties. Therefore, the bearing body 10 adopts silicon nitride (Si3N4) ceramic material. Silicon nitride ceramic material has the advantages of high temperature resistance, corrosion resistance, high specific strength, good wear resistance, and small thermal expansion coefficient.

[0056] Since silicon nitride ceramic materials are brittle and have poor abrasive embedding properties, the bearing body 10 has a weak ability to resist abrasive wear, so a solid lubricating layer 13 is provided on the inner wall surface of the bearing hole 11 of the bearing body 10 to achieve self-lubricating properties of the bearing structure. Optionally, the solid lubricating layer 13 is a coating.

[0057] Specifically, due to the weak van der Waals force between the layers of molybdenum disulfide (MoS2), when subjected to external force, slippage between the layers easily occurs, which helps its lubrication, especially under high temperature, low temperature, high load, high speed and ultra-vacuum conditions, it has excellent lubrication properties; through research, it is found that the wear reduction and wear resistance of molybdenum disulfide with the addition of polytetrafluoroethylene and graphite are better, so the material components of the solid lubrication layer 13 of the present application include polytetrafluoroethylene, graphite, binder and molybdenum disulfide, the content of polytetrafluoroethylene is in the range of 10%-20%, the content of graphite is in the range of 5%-10%, the content of binder is in the range of 1%-3%, and the rest is molybdenum disulfide, so that the bearing body 10 is suitable for the centrifugal refrigeration compressor environment under high temperature and high pressure.

[0058] Specifically, the particle size of molybdenum disulfide is less than 10 μm, and the thickness of the solid lubricating layer 13 is greater than 0.5 mm. The solid lubricating layer 13 has high compressive strength, good wear resistance, strong adhesion, and low friction factor. It has good film-forming structure characteristics and can generate a thin film that still has good stability under high pressure, thereby preventing the bearing body 10 from failing due to bearing structure rupture due to liquid film rupture, thereby improving the stability and service life of the shaft system.

[0059] The bearing structure of the present application has the following advantages: 1. Good self-lubricating performance, small bearing wear and long life; 2. High bearing capacity; 3. Good bearing shock absorption characteristics; 4. Good bearing heat dissipation characteristics.

[0060] The present invention also provides a water chiller, which comprises a compressor, and the compressor comprises the above-mentioned bearing structure.

[0061] From the above description, it can be seen that the above embodiments of the present invention achieve the following technical effects:

[0062] In the bearing structure of the present invention, the bearing structure includes a bearing body 10 having a bearing hole 11, and the inner wall surface of the bearing hole 11 is provided with a plurality of strip grooves 12 arranged at intervals along the circumference of the bearing hole 11, and the two ends of each strip groove 12 are respectively a first end and a second end and extend toward the two ends of the bearing hole 11; the second end of each strip groove 12 deviates from the first end thereof along the circumference of the bearing hole 11 by a predetermined angle. By providing a plurality of strip grooves 12, the liquid film structure formed when the bearing structure of the present application adopts a refrigerant lubricated bearing is relatively stable, and the problem that the liquid film formed by the refrigerant lubricated bearing in the prior art is easy to rupture is solved.

[0063] It should be noted that the terms "first", "second", etc. in the specification and claims of the present application and the above-mentioned drawings are used to distinguish similar objects, and are not necessarily used to describe a specific order or sequence. It should be understood that the data used in this way can be interchangeable where appropriate, so that the embodiments of the present application described herein can be implemented in an order other than those illustrated or described herein, for example. In addition, the terms "including" and "having" and any of their variations are intended to cover non-exclusive inclusions, for example, a process, method, system, product or device that includes a series of steps or units is not necessarily limited to those steps or units that are clearly listed, but may include other steps or units that are not clearly listed or inherent to these processes, methods, products or devices.

[0064] 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.

[0065] 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 bearing structure, characterized in that: A bearing body (10) is provided with a bearing hole (11); the inner wall surface of the bearing hole (11) is provided with a plurality of strip grooves (12) arranged at intervals along the circumference of the bearing hole (11); the two ends of each strip groove (12) are respectively a first end and a second end and are respectively extended toward the two ends of the bearing hole (11); the second end of each strip groove (12) deviates from the first end thereof by a predetermined angle along the circumference of the bearing hole (11); Each of the strip-shaped grooves (12) extends along a predetermined curve, the predetermined curve comprising a first smooth curve segment, a second line segment, and a third smooth curve segment connected in sequence, the second line segment being a smooth curve segment or a straight line segment; The first smooth curve segment has a connection end connected to the second line segment and a free end away from the second line segment, the free end of the first smooth curve segment forming a first end of the strip groove (12), the connection end of the first smooth curve segment deviates from the free end thereof by a first set angle along the circumference of the bearing hole (11), the first set angle is an acute angle, and the deviation direction of the connection end of the first smooth curve segment is the same as the deviation direction of the second end of the strip groove (12); and / or The second line segment has a first end connected to the first smooth curve segment and a second end away from the first smooth curve segment, the second end of the second line segment deviates from the first end thereof by a second set angle along the circumference of the bearing hole (11), the second set angle is an acute angle, and the deviation direction of the second end of the second line segment is the same as the deviation direction of the second end of the strip groove (12); and / or The third smooth curve segment has a connection end connected to the second line segment and a free end away from the second line segment, the free end of the third smooth curve segment forming the second end of the strip groove (12), the free end of the third smooth curve segment deviates from its connection end by a third set angle along the circumference of the bearing hole (11), the third set angle is an acute angle, and the deviation direction of the free end of the third smooth curve segment from its connection end is the same as the deviation direction of the second end of the strip groove (12) from its first end.

2. The bearing structure according to claim 1, characterized in that: The second ends of the plurality of strip-shaped grooves (12) are all deviated in a clockwise direction or are all deviated in a counterclockwise direction; and / or Two ends of each of the strip-shaped grooves (12) extend to two end surfaces of the bearing hole (11) respectively; and / or The number of the strip-shaped grooves (12) is an even number.

3. The bearing structure according to claim 1, characterized in that: Each of the strip-shaped grooves (12) has a longitudinal cross section perpendicular to its extension direction. The shape of the longitudinal cross section is any one of a trapezoid, a rectangle, and a triangle; or The outer periphery of the longitudinal cross section is a portion of a predetermined circle; or The outer periphery of the longitudinal cross section is a portion of a predetermined ellipse.

4. The bearing structure according to claim 3, characterized in that: Each of the strip-shaped grooves (12) extends along a predetermined curve, and the predetermined curve is a smooth curve; The predetermined angle ranges from 20 degrees to 40 degrees; and / or The length of the bearing body (10) along its axial direction is L, the inner diameter of the bearing hole (11) is D, the length-to-diameter ratio is L / D, and the value range of the length-to-diameter ratio is 1.8 to 2.

5. The bearing structure according to claim 2, characterized in that: The first setting angle has a value range of 25 degrees to 50 degrees; and / or The second set angle has a value range of 15 to 25 degrees; and / or The third setting angle has a value range of 25 degrees to 50 degrees; and / or The length between the connecting end and the free end of the first smooth curve segment along the axial direction of the bearing body (10) is 1 / 6 of the length of the bearing body (10) along the axial direction thereof; and / or The length between the connecting end and the free end of the third smooth curve segment along the axial direction of the bearing body (10) is 1 / 6 of the length of the bearing body (10) along the axial direction thereof; and / or The length of the bearing body (10) along its axial direction is L, the inner diameter of the bearing hole (11) is D, the length-to-diameter ratio is L / D, and the value range of the length-to-diameter ratio is 1.8 to 2.

6. The bearing structure according to claim 1, characterized in that: The hole radius of the bearing hole (11) is R, the radius of the rotating shaft (20) disposed in the bearing hole (11) is r, The radius gap δ is (Rr); the distance between the centerline of the bearing hole (11) and the central axis of the rotating shaft (20) is the eccentricity, the eccentricity is the ratio of the eccentricity to the radius gap, and the eccentricity ranges from 0.5 to 0.8; and / or The relative gap is C, C= (Rr) / R, and the value range of C is 0.5% to 2%.

7. The bearing structure according to claim 1, characterized in that: The outer wall surface of the bearing body (10) is provided with a plurality of annular grooves spaced apart along the axial direction of the bearing body (10), and an elastic ring (14) is provided in the annular groove; and / or The bearing body (10) is made of silicon nitride ceramic material; and / or The inner wall surface of the bearing hole (11) is provided with a solid lubricating layer (13).

8. The bearing structure according to claim 7, characterized in that: The material components of the solid lubricating layer (13) include polytetrafluoroethylene, graphite, a binder and molybdenum disulfide; wherein the content of the polytetrafluoroethylene is in the range of 10%-20%, the content of the graphite is in the range of 5%-10%, and the content of the binder is in the range of 1%-3%; the particle size of the molybdenum disulfide is less than 10 μm; and / or The thickness of the solid lubricating layer (13) is greater than 0.5 mm.

9. A chiller, comprising a compressor, characterized in that: The compressor comprises the bearing structure according to any one of claims 1 to 8.

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