CN116044904A - Drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing - Google Patents
Drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing Download PDFInfo
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- CN116044904A CN116044904A CN202310161092.0A CN202310161092A CN116044904A CN 116044904 A CN116044904 A CN 116044904A CN 202310161092 A CN202310161092 A CN 202310161092A CN 116044904 A CN116044904 A CN 116044904A
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C32/00—Bearings not otherwise provided for
- F16C32/06—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings
- F16C32/0603—Bearings not otherwise provided for with moving member supported by a fluid cushion formed, at least to a large extent, otherwise than by movement of the shaft, e.g. hydrostatic air-cushion bearings supported by a gas cushion, e.g. an air cushion
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
- F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
- F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
- F16C33/02—Parts of sliding-contact bearings
- F16C33/04—Brasses; Bushes; Linings
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Abstract
A drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing comprises a bearing outer ring and a bearing inner ring, wherein the bearing outer ring is in clearance fit with the bearing inner ring; the bearing inner ring consists of a hollow cylinder and two hollow truncated cones, and the lower bottom surfaces of the two hollow truncated cones are respectively connected to the two ends of the hollow cylinder; a divergent area gap is formed between the conical inclined surfaces of the two hollow truncated cones and the inner surface of the bearing outer ring, and a static pressure area gap is formed between the outer surface of the hollow cylinder and the inner surface of the bearing outer ring; and an air inlet groove is formed in the outer surface of the bearing outer ring at a position corresponding to the static pressure bearing area, and a plurality of air inlet throttling devices are uniformly distributed in the air inlet groove along the circumferential direction. The bearing can form a stable lubricating film by constructing the wedge-shaped gap to form a dynamic-static pressure effect, can bear a certain bidirectional axial load, has stronger static pressure and dynamic pressure effect, and has good stability and dynamic performance.
Description
Technical Field
The invention belongs to the technical field of sliding bearings, and relates to a drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing.
Background
The sliding bearing is suitable for high-speed working conditions due to the fluid film gap formed in the running process, has the characteristics of extremely low friction coefficient, small interface abrasion and the like, and is increasingly used in various rotary mechanical systems. The fluid radial sliding bearing lubrication medium can be liquid or gas, wherein the liquid lubrication, in particular the sliding bearing under the lubricating oil, has higher bearing capacity and good stability; the gas lubrication radial sliding bearing has the advantages of high rotor precision, small friction loss, low requirement on working environment, cleanness, environmental protection and the like, and is also applied to various high-precision machine tools, high-speed aerodynamic devices, precision equipment or instrument systems and other equipment. However, the conventional radial sliding bearing is generally difficult to bear axial load and has poor high-speed stability, and as the working condition of the bearing is more and more complex, the requirement for a new structure to solve the above problems is more and more urgent.
In terms of the proposal of a new structure of a sliding bearing, different documents and patents already discuss the structure updating strategy of the bearing, such as a rolling and sliding combined new bearing structure is proposed, and an adjustable positioning rolling and sliding radial composite bearing (application number: CN 112128237A) is disclosed in Zhang Guoyuan and the like. As another example, zhang Guoyuan et al discloses a rolling-sliding radial-sliding thrust combined bearing (application number: CN 112128236A), which combines a radial bearing with a thrust bearing, the radial bearing structure is the same as the above patent; the thrust bearing has the main structure that the mirror plate is fixed on the end face of the rotor, the double-round-table thrust bearing is arranged at the lower end of the radial bearing seat, and the tilting pad is arranged on the second round table.
On the other hand, for the development of new structures for sliding bearings, solutions are adopted which change the surface characteristics of the bearing or of the mating rotor, i.e. the surface reshaping. One is grooved or microtextured at the bearing inner diameter and the other is a modification (grooved or microtextured) of the bearing-mating rotor surface. However, the first solution is more difficult to achieve for smaller diameter sliding bearings, such as air radial sliding bearings, with grooving or texturing at the inner diameter, and in high speed operation, the clearances of the bearings need to be designed more accurately, otherwise bearing instability is very likely to occur under high speed conditions; the second scheme is not easy to realize in actual engineering, and in practice, the design of the rotor and the bearing belongs to different departments, and the bearing serving as a basic component cannot bring requirements to the design of the rotor; in addition, the reshaping of the rotor surface may have an influence on the strength of the rotor as a whole, which may even affect the safety and stability of the rotor operation.
For the first scheme, a few researchers have proposed a new bearing structure, for example, patent application number CN113431844a, entitled "a high-speed helical groove small hole throttling dynamic and static gas bearing device", discloses a dynamic and static gas bearing with an air supply hole and small hole throttler on the outer side and helical grooves and axial micro-through grooves on the inner side. The dynamic and static pressure gas bearing can meet the aim of avoiding dry friction and improving stability of the rotor in starting and stopping stages, can stop external continuous high-pressure gas supply when the rotor runs at high speed, and can press gas into the spiral groove by utilizing the rotation of the shaft neck so as to improve the overall performance of the bearing; however, the spiral groove of the bearing is positioned at the inner side, the axial micro-through groove is positioned at the middle section of the inner side of the bearing, and the processing is difficult. As another example, the patent CN 110242671A entitled "a conical foil hydrodynamic air bearing" discloses a conical bearing to which radial foil is applied, which is structured to change a hollow cylinder into a hollow cone and mount the radial foil on the outside. The invention can bear radial force and axial force simultaneously and has larger bearing capacity, but does not point out the matching relation between the bearing and the rotor, and can not form effective oil film thickness when the rotor starts and stops, so that the friction resistance is overlarge and the stability of the rotor is affected.
In recent years, researchers have proposed a surface reshaping method for improving the performance of a sliding bearing, and have made some theoretical progress, such as aiming at the influence of surface micro-texture on the bearing performance, ding Hao and the like, by calculating the bearing capacity of the bearing model by adopting a hydrodynamic method through an established bearing model taking different shapes and micro-textures into consideration, and knowing the influence rule of the shape and depth of the micro-texture on the bearing capacity of the gas dynamic bearing, the research result shows that the surface micro-texture has a certain influence on the bearing performance of the gas dynamic bearing [ Ding Hao, high strength, feng Wei, liu Baoguo, li Hangyu ]. Such methods for achieving improved bearing performance by surface modification are increasingly receiving attention from researchers and are an important direction of bearing technology development.
In summary, with respect to new structural requirements and theoretical research progress of sliding bearings, there is a need to develop solutions that are more convenient to manufacture and improve their overall performance.
Disclosure of Invention
In order to overcome the defects in the prior art, the invention aims to provide a drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing, which can form a stable lubricating film by constructing a wedge-shaped gap to form a dynamic-static pressure effect, can bear a certain bidirectional axial load, has stronger static pressure and dynamic pressure effect and has good stability and dynamic performance.
In order to achieve the above purpose, the technical scheme adopted by the invention is as follows:
the drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing comprises a bearing outer ring and a bearing inner ring, wherein the bearing outer ring is in clearance fit with the bearing inner ring;
the bearing inner ring consists of a hollow cylinder and two hollow truncated cones, and the lower bottom surfaces of the two hollow truncated cones are respectively connected to the two ends of the hollow cylinder; a divergent area gap is formed between the conical inclined surfaces of the two hollow truncated cones and the inner surface of the bearing outer ring, and a static pressure area gap is formed between the outer surface of the hollow cylinder and the inner surface of the bearing outer ring;
and an air inlet groove is formed in the outer surface of the bearing outer ring at a position corresponding to the static pressure bearing area, and a plurality of air inlet throttling devices are uniformly distributed in the air inlet groove along the circumferential direction.
In one embodiment, the gap at the minimum gap of the bearing outer ring and the bearing inner ring is 0.1-50 μm.
In one embodiment, the bearing outer ring is a hollow cylinder, and the air inlet groove is formed in the outer surface of the hollow cylinder along the circumferential direction; the central lines of the hollow cylinder and the two hollow truncated cones are coincident, and the lower bottom surfaces of the two hollow truncated cones are respectively equal to and attached to the two bottom surfaces of the hollow cylinder.
In one embodiment, the air inlet throttling device is a circular through hole, the axis of the air inlet throttling device is orthogonal to the axis of the bearing outer ring, the diameter is 0.5-5 mm, the length is 0.4-0.9 times of the thickness of the bearing outer ring, the ratio of the length to the diameter is 1-20, and the short capillary throttling condition is met.
In one embodiment, the tail end of the air inlet throttling device is provided with a rectangular pressure cavity, and the cavity depth of the rectangular pressure cavity is 0.5-5 mm; the axial length is 1/9-2/9 of the width of the bearing, and the ratio of the circumferential length to the axial length is 0.8-1.2.
In one embodiment, the taper inclined planes of the hollow truncated cones are uniformly distributed with a plurality of groups of modified groove structures or micro-textures along the circumferential direction, and the modified groove structures or micro-textures on the two hollow truncated cones are identical in number and symmetrically distributed.
In one embodiment, the groove type of the modified groove structure is a spiral groove, a rectangular groove or a triangular groove, and the groove depth is 0.1-10 mu m so as to facilitate the formation of dynamic pressure effect; the microtexture is a plurality of rows of combined circular microtrences, triangular microtrences, square microtrences or rectangular microtrences, the total area of the microtexture occupies 1/3-2/3 of the area of the conical inclined surface, and the pit depth is 0.1-3 mm, so that the local hydrostatic effect is formed on the microtexture part.
In one embodiment, when the groove type of the modified groove structure is a spiral groove, the spiral grooves have a plurality of groups; spiral grooves on the two hollow truncated cones are opposite in rotation direction; when the bearing inner ring rotates anticlockwise, the rotation directions of the spiral grooves on the two hollow truncated cones are consistent with the fluid flow trend, so that the fluid circulation is promoted, and the lubrication effect is maintained; when the bearing inner ring rotates clockwise, the spiral directions of the spiral grooves on the two hollow truncated cones are opposite to the fluid flow trend, so that the bearing flow is reduced, and the bearing hydrostatic effect is improved.
In one embodiment, the axial lengths of the clearance of the divergence area and the clearance of the static pressure area are equal, the taper range of the hollow truncated cone is 0.5-10 degrees, the design is carried out according to the external axial force born by the hollow truncated cone or the purpose of increasing the bearing flow to realize the cooling of the bearing, when the taper is increased, the axial limit load born by the bearing is increased, and meanwhile, the clearance of the divergence area of the bearing is increased, so that the bearing flow is increased, and the heat dissipation capacity of the bearing is further improved; when the taper is reduced, the radial limit load born by the bearing is increased, and meanwhile, the clearance of the divergent area of the bearing is reduced, so that the flow of the bearing is reduced, and the heat dissipation capacity of the bearing is further reduced.
In one embodiment, the inner bore of the bearing inner race is an interference fit or a transition fit with the shaft.
Compared with the prior art, the invention has the beneficial effects that:
1. the split type fluid lubrication sliding bearing innovative structural scheme adopted by the invention can design reasonable throttling devices and groove type parameters according to working conditions so as to increase the functions of bearing and air film rigidity. Specifically, at a higher rotating speed, the fluid dynamic pressure effect is enhanced through spiral grooves or micro-textures symmetrically distributed on two cone inclined planes of the bearing inner ring so as to improve the bearing and air film rigidity; at lower rotational speeds, the static pressure effect of the fluid is increased by short capillary throttling and an external higher air supply pressure to achieve an increase in load bearing performance and the like.
2. In the invention, a micro-gap in a micron level exists between the inner ring and the outer ring, and the pressure cavity is in a millimeter level, so that a more stable air film can be obtained, and the bearing capacity of the bearing is improved.
3. In the running process, the truncated cone structure adopted by the inner ring has larger two ends, can effectively press a medium into the bearing, can bear the impact of axial force and radial force at the same time, and prolongs the service life of the bearing.
Drawings
Fig. 1 is a schematic diagram of the overall structure of the present invention.
Fig. 2 is a front view of the bearing outer race.
Fig. 3 is a radial cross-sectional view of the bearing outer race.
Fig. 4 is a schematic structural view of an inner race of a bearing spiral groove.
Fig. 5 is a schematic structural view of a bearing triangular micro-textured inner ring.
Detailed Description
Embodiments of the present invention will be described in detail below with reference to the accompanying drawings and examples.
The invention discloses a dynamic and static pressure radial sliding bearing with dynamic and static pressure effect formed by constructing wedge-shaped gaps, in particular to a separable dynamic and static pressure radial sliding bearing with a drum-shaped double conical surface of an inner ring and a throttling device of an outer ring, which is used for improving bearing static characteristics of the bearing and enhancing running dynamic characteristics.
Specifically, as shown in fig. 1 to 5, the drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing comprises a bearing outer ring 1 and a bearing inner ring 2, wherein the bearing outer ring 1 and the bearing inner ring 2 are in clearance fit, the bearing inner ring 2 is coaxially arranged in the bearing outer ring 1, and an inner hole of the bearing inner ring 2 is in interference fit or transition fit with a shaft.
The outer surface of the bearing outer ring 1 is provided with a circumferential air inlet groove 1-1, and a plurality of air inlet throttling devices 1-2 are uniformly distributed in the circumferential direction in the air inlet groove 1-1.
The bearing inner ring 2 is composed of a hollow cylinder 2-1 and two left-right symmetrical hollow truncated cones 2-2, wherein the hollow truncated cone 2-2 is a truncated cone-shaped structure obtained by truncated one hollow cone, and the hollow refers to a through hole along the direction of the central axis, and the central axis of the through hole is easy to understand and is consistent with the central axis of the cone or truncated cone. Similarly, the hollow cylinder 2-1 is a cylinder having an axial through hole, and it is easy to understand that the center axis of the through hole coincides with the center axis of the cylinder. The lower bottom surfaces of the two hollow truncated cones 2-2 are respectively connected with the two ends of the hollow cylinder 2-1; obviously, the hollow portion of the hollow cylinder 2-1, i.e. "through hole", and the hollow portion of the two hollow truncated cones 2-2, i.e. "through hole", are of equal diameter and coaxial, i.e. the centerlines of the hollow cylinder 2-1 and the two hollow truncated cones 2-2 coincide. Illustratively, the lower bottom surfaces of the two hollow truncated cones 2-2 are respectively equal to and fit against the two bottom surfaces of the hollow cylinder 2-1. In the present invention, "lower bottom surface" refers to the larger bottom surface in the cross-sectional frustoconical structure. Correspondingly, "upper bottom surface" refers to the smaller bottom surface in the cross-sectional frustoconical configuration. The two ends of the bearing inner ring 2 are the upper bottom surfaces of the two hollow truncated cones 2-2 "
When the bearing inner ring 2 is placed in the bearing outer ring 1, a divergent area gap is formed between the conical inclined surfaces of the two hollow truncated cones 2-2 and the inner surface of the bearing outer ring 1, and a static pressure area gap is formed between the outer surface of the hollow cylinder 2-1 and the inner surface of the bearing outer ring 1. Wherein the air inlet groove 1-1 corresponds to the position of the static pressure bearing area. The divergent region gap promotes the formation of dynamic pressure effects during rotation of the inner ring, and the static pressure region gap forms static pressure effects under passing through the air inlet throttling device. Therefore, in the running process, the two ends are larger and the middle gap is smaller, so that the medium can be effectively pressed into the bearing, the impact of axial force and radial force can be borne at the same time, and the service life of the bearing is prolonged.
The axial lengths of the three sections of gaps are the same, truncated cone taper is designed according to actual working conditions, and then different gaps in the divergence areas are obtained, so that the mechanical property and the heat dissipation performance of the bearing are improved.
In some embodiments of the invention, the gap at the smallest gap of the bearing outer ring 1 and the bearing inner ring 2 is 0.1-50 μm, at a micrometer-scale gap.
In some embodiments of the invention, the bearing outer ring 1 is a hollow cylinder, where the hollow cylinder is defined as similar to the hollow cylinder 2-1 described above, i.e. a cylinder with an axial through hole. The bearing inner ring 2 is located coaxially in the axial through hole. The number of the air inlet grooves 1-1 is 1, or a plurality of air inlet grooves can be symmetrical, and the air inlet grooves are formed in the outer surface of the hollow cylinder along the circumferential direction. The inlet air restriction devices 1-2 are arranged in a single row, i.e. all the inlet air restriction devices 1-2 are on the same circumference and preferably evenly distributed. The number of the air inlet throttling devices 1-2 is generally 4-16, and the number is designed according to the working condition and the structural parameters of the bearing.
In some embodiments of the invention, the air inlet throttling device 1-2 is a circular through hole, the axis of the air inlet throttling device is orthogonal to the axis of the bearing outer ring 1, the diameter is in the range of 0.5-3 mm, the length is 0.4-0.9 times of the thickness of the bearing outer ring 1, the ratio of the length to the diameter is in the range of 1-20, and the short capillary throttling condition is met.
In some embodiments of the present invention, the end of the air inlet throttling device 1-2 is further provided with a rectangular pressure cavity 1-3, two ends of the air inlet throttling device 1-2 are respectively communicated with the air inlet groove 1-1 and the rectangular pressure cavity 1-3, and the axis of the air inlet throttling device 1-2 coincides with the geometric center line of the rectangular pressure cavity 1-3. The rectangular pressure cavity 1-3 is rectangular or approximately rectangular in cross section along the vertical axial direction, and has a cavity depth (namely radial length) of mm level and a range of 0.5-5 mm; the axial length is 1/9-2/9 of the width of the bearing, and the ratio of the circumferential length to the axial length is 0.8-1.2. The micron-level gap between the inner ring and the outer ring and the millimeter-level cavity depth of the pressure cavity can obtain a more stable air film, and the bearing capacity of the bearing is improved. The design of deep cavity parameters can be reasonably performed by combining the static pressure bearing characteristic of the bearing.
In some embodiments of the present invention, the taper slope of the hollow truncated cone 2-2 is uniformly distributed with multiple groups of modified groove structures 2-2-1 or other micro textures along the circumferential direction, and the modified groove structures 2-2-1 or micro textures on the two hollow truncated cones 2-2 are identical in number and symmetrically distributed.
In some embodiments of the present invention, the groove type of the groove structure 2-2-1 is a spiral groove, a rectangular groove or a triangular groove, the number of grooves is 4-16, and the number of grooves is in the micrometer scale, and the range is 0.1-10 μm, so as to facilitate the formation of dynamic pressure effect; the micro-texture is a plurality of rows of combined circular micro-pits, triangular micro-pits, square micro-pits or rectangular micro-pits, and the like, the total area of the micro-texture occupies 1/3-2/3 of the area of the conical inclined surface, and the pit depth is 0.1-3 mm, so that the local hydrostatic effect is formed on the micro-texture part.
In some embodiments of the present invention, when the groove type of the groove structure 2-2-1 is changed into a spiral groove, the spiral grooves have multiple groups, and the forms can be various types of line pairs, involute, expansion lines, etc.; the spiral grooves on the two hollow truncated cones 2-2 are opposite in rotation direction, namely the spiral grooves on the two hollow truncated cones 2-2 are symmetrical with respect to the center plane of the width of the bearing, and in the embodiment, the spiral grooves on the side surface of the left cone are left-handed and the spiral grooves on the right side are right-handed. When the bearing inner ring 2 rotates anticlockwise, the spiral directions of the spiral grooves on the two hollow truncated cones 2-2 are consistent with the fluid flow trend, so that the fluid circulation is promoted, and the lubrication effect is maintained; when the bearing inner ring 2 rotates clockwise, the spiral directions of the spiral grooves on the two hollow truncated cones 2-2 are opposite to the fluid flow trend, so that the bearing flow is reduced, and the bearing hydrostatic effect is improved.
In some embodiments of the present invention, the axial lengths of the diverging zone gap and the static pressure zone gap are equal, and the taper of the hollow truncated cone 2-2 ranges from about 0.5 degrees to about 10 degrees, and is designed for the purpose of bearing cooling according to the external axial force to which it is subjected or for the purpose of increasing the bearing flow. Specifically: when the taper is increased, the axial limit load born by the bearing is increased, and meanwhile, the bearing flow is increased due to the increase of the clearance of the bearing divergence area, so that the heat dissipation capacity of the bearing is improved; when the taper is reduced, the radial limit load born by the bearing is increased, and meanwhile, the clearance of the divergent area of the bearing is reduced, so that the flow of the bearing is reduced, and the heat dissipation capacity of the bearing is further reduced.
The following are two specific embodiments of the present invention.
Example 1:
for high-speed heavy-duty application, a drum-shaped double-cone dynamic and static radial bearing is provided, and is described in further detail below with reference to the accompanying drawings:
referring to fig. 1, the present invention comprises a bearing outer race 1 and a bearing inner race 2, wherein:
the bearing outer ring 1 is structured as shown in fig. 2 and 3, and is provided with an air inlet groove 1-1, an air inlet throttling device 1-2 and a rectangular pressure cavity 1-3.
The bearing outer ring 1 is a hollow cylinder, an air inlet groove 1-1 is formed in the outer surface of the hollow cylinder along the circumferential direction, a plurality of single-row air inlet throttling devices 1-2 are uniformly distributed in the groove, and rectangular pressure cavities 1-3 are formed at the tail ends of some air inlet throttling devices 1-2. In this embodiment, the outer diameter of the outer ring is 60mm, the inner diameter is 50mm, the thickness is 5mm, the width is 9mm, and the depth of the air inlet groove is 1mm.
The single-row air inlet throttling device 1-2 is positioned in the air inlet groove 1-1, and as shown in fig. 2, the single-row air inlet throttling devices are uniformly distributed along the circumferential direction, and all circle centers are positioned on the central line of the air inlet groove; the number is 8, the length takes 3mm, the diameter takes 0.5mm, the ratio of the length to the diameter is 6, and the parameter range of the short capillary throttling structure device is satisfied.
The upper end of the rectangular pressure cavity 1-3 is communicated with the air inlet throttling device 1-2 as shown in fig. 3, so that the static pressure effect of the tail part of the throttling device can be further enhanced, the axis of the air inlet throttling device is coincident with the geometric center line of the pressure cavity, the axis of the air inlet throttling device is orthogonal with the axis of the hollow cylinder, and the tail end of the air inlet throttling device is communicated with the gap between the outer ring and the inner ring, so that sufficient liquid is provided for the bearing, and the lubricating requirement of the bearing is met; the static pressure bearing characteristic of the bearing is combined, and the depth of a pressure cavity is designed to be 1mm; the deep cavity has a rectangular cross-section structure, the circumferential length of the pressure cavity is 2.4mm, the axial length is 2mm, and the ratio of the two is 1.2.
The bearing inner ring 2 has a structure shown in figure 4 and comprises a hollow cylinder 2-1 and a hollow truncated cone 2-2, wherein a modified groove structure 2-2-1 is arranged on the hollow truncated cone 2-2.
Specifically, the bearing inner ring 2 is composed of a hollow cylinder 2-1 and a pair of hollow truncated cones 2-2 which are bilaterally symmetrical, the symmetrical central lines of the hollow cylindrical body 2-1 and the hollow truncated cones are overlapped, the lower bottom surfaces of the two hollow truncated cones 2-2 are respectively overlapped with the two bottom surfaces of the hollow cylindrical body 2-1, the two ends of the inner ring are the upper bottom surfaces of the two hollow truncated cones 2-2, and the two cone inclined surfaces are used for forming a divergence clearance area; the hollow cylinder 2-1 is positioned in the middle of the small ends of the double-sided cone and is used for forming a static pressure bearing area; the inner diameter of the inner ring is in interference fit with the shaft, so that the inner ring rotates along with the rotor. The inner ring has an outer diameter of 50mm and an inner diameter of 40mm.
The bearing inner ring 2 is in clearance fit with the bearing outer ring 1, three sections of gaps are formed between the bearing outer ring and the inner ring, and the three sections of gaps are respectively the gaps of divergent areas formed by the left conical outer side and the right conical outer side of the inner ring and the inner diameter of the outer ring; and a static pressure area gap is formed between the outer diameter of the inner ring and the inner diameter of the outer ring of the middle part. The divergent region gap promotes the formation of dynamic pressure effects during rotation of the inner ring, and the static pressure region gap forms static pressure effects under passing through the air inlet throttling device. The axial lengths of the three sections of gaps are all the same, 3mm is taken, and the gap in the static pressure area is 5 mu m.
The taper of the cone is 3 degrees; the taper size directly influences the clearance size of the divergent area formed by the divergent clearance areas on the left and right tapered outer sides of the inner ring and the inner diameter of the outer ring, in the embodiment, the bearing is positioned on a high-speed heavy-load occasion, and in order to prevent the deformation of the bearing structure and the possible exceeding of the temperature rise caused by the overhigh temperature of the bearing, the bearing must be ensured to have good heat dissipation performance when the truncated cone taper is designed, so that the existence of the taper can increase the flow of the bearing and further reduce the temperature rise of the bearing. Meanwhile, different bearing performances can be obtained by changing the taper of the cone, namely, the taper is increased, and the axial load borne by the drum-shaped double-taper dynamic and static radial bearing is increased; the taper is reduced, and the axial load of the drum-shaped double-taper dynamic and static radial bearing is reduced; for this purpose, the truncated cone taper is taken into account comprehensively by 3 °.
The truncated cone is uniformly distributed with a plurality of groups of modified groove structures 2-2-1 along the circumferential direction on the outer side surface, the modified grooves are a plurality of groups of spiral grooves, the spiral directions of the side grooves of the left cone and the right cone are opposite (namely, the spiral grooves on the two hollow truncated cones 2-2 are symmetrical about the central surface of the width of the bearing), the side spiral grooves of the left cone are left-handed, and the spiral grooves of the right cone are right-handed; when the bearing inner ring 2 rotates anticlockwise, the rotation directions of the spiral grooves on the side surfaces of the left cone and the right cone are consistent with the fluid flow trend, so that the fluid circulation is promoted, and the lubrication effect is maintained; when the bearing inner ring 2 rotates clockwise, the rotation direction of the spiral grooves on the side surfaces of the left cone and the right cone is opposite to the fluid flow trend, so that the flow of the bearing is reduced, and the static pressure effect of the bearing is improved; in the embodiment, the number of the modified grooves on the side surface of the cone is 16, the groove depth is 1 mu m, and the helix angle is 45 degrees; the width of the spiral groove is 2mm.
Example 2:
the invention will be described in further detail below with reference to the accompanying drawings, taking as an example a sliding bearing for a main shaft of a wind turbine generator set:
referring to fig. 1, the present invention comprises a bearing outer race 1 and a bearing inner race 2, wherein:
the bearing outer ring 1 is structured as shown in fig. 2 and 3, and is provided with an air inlet groove 1-1, an air inlet throttling device 1-2 and a rectangular pressure cavity 1-3.
The bearing outer ring 1 has the same structure as that of embodiment 1, and only the respective structural parameters are different. In this embodiment, the outer diameter of the outer ring is 800mm, the inner diameter is 700mm, the thickness is 50mm, the width is 90mm, and the depth of the air inlet groove is 10mm. The externally supplied medium must be high pressure lubrication oil to ensure a good lubrication film for the bearing.
The single-row air inlet throttling device 1-2 is positioned in the air inlet groove 1-1, and as shown in fig. 2, the single-row air inlet throttling devices are uniformly distributed along the circumferential direction, and all circle centers are positioned on the central line of the air inlet groove; the number is 12, and the interval between two adjacent throttling devices is 30 degrees. The length is 30mm, the diameter is 3mm, the ratio of the length to the diameter is 10, and the parameter range of the short capillary throttling structure device is satisfied.
The upper end of the rectangular pressure cavity 1-3 is communicated with the air inlet throttling device 1-2 as shown in fig. 3, so that the static pressure effect of the tail part of the throttling device can be further enhanced, the axis of the air inlet throttling device coincides with the geometric center line of the pressure cavity, the axis of the air inlet throttling device is orthogonal with the axis of the hollow cylinder, and the tail end of the air inlet throttling device is communicated with the gap between the outer ring and the inner ring, so that sufficient liquid is provided for the bearing, and the lubricating requirement of the bearing is met; the static pressure bearing characteristic of the bearing is combined, and the depth of a pressure cavity is designed to be 10mm; the deep cavity has a rectangular cross-section structure, the circumferential length is 12mm, the axial length is 10mm, and the ratio of the two is 1.2.
The bearing inner ring 2 has a structure as shown in figure 4, and comprises a hollow cylinder 2-1 and a hollow truncated cone 2-2, wherein the hollow truncated cone 2-2 is provided with a micro-texture to replace the modified groove structure 2-2-1.
Specifically, the bearing inner ring 2 is composed of a hollow cylinder 2-1 and a pair of hollow truncated cones 2-2 which are bilaterally symmetrical, the symmetrical central lines of the hollow cylindrical body 2-1 and the hollow truncated cones are overlapped, the lower bottom surfaces of the two hollow truncated cones 2-2 are respectively overlapped with the two bottom surfaces of the hollow cylindrical body 2-1, the two ends of the inner ring are the upper bottom surfaces of the two hollow truncated cones 2-2, and the two cone inclined surfaces are used for forming a divergence clearance area; the hollow cylinder 2-1 is positioned in the middle of the small ends of the double-sided cone and is used for forming a static pressure bearing area; the inner diameter of the inner ring is in transition fit with the main shaft, so that the inner ring rotates along with the main shaft. The inner ring has an outer diameter of 700mm and an inner diameter of 650mm.
The bearing inner ring 2 is in clearance fit with the bearing outer ring 1, three sections of gaps are formed between the bearing outer ring and the bearing inner ring, the axial lengths of the three sections of gaps are the same, 30mm is taken, and the gap of the static pressure area is 20 mu m. In this embodiment, the bearing is subjected to a very large load, and therefore, a sufficient oil film thickness is required to ensure the normal operation of the bearing.
The taper of the cone is 0.5 degrees; because the main shaft bearing of the wind generating set mainly bears the weight of the fan blade and the hub and the force of the wind acting on the main shaft through the wind wheel, the main shaft bearing mainly bears the radial force, the taper of the cone is changed to obtain different bearing performances, the taper is increased, and the axial load borne by the drum-shaped double-cone dynamic-static pressure radial bearing is increased; the conicity is reduced, the maximum radial load which can be borne by the drum-shaped double-cone dynamic and static pressure radial bearing is increased, and the axial load is reduced. In order to improve the bearing capacity of the bearing, the truncated cone taper is designed to be 0.5 DEG according to the ratio of the radial limit load to the axial limit load
The truncated cone is uniformly distributed with a plurality of groups of micro-textures 2-2-1 along the circumferential direction on the outer side surface, the micro-textures are double-row triangular micro-pits, 16 groups are distributed on each side, the side surfaces of the left cone and the right cone are symmetrical, the triangle is an equilateral triangle, the side length is 10mm, the occupied area is 2/3 of the area of the whole side surface, and the groove depth is 2mm; the adoption of the triangular micro-texture improves the bearing capacity and can form a local hydrostatic effect on the side surface of the truncated cone.
Claims (10)
1. The drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing is characterized by comprising a bearing outer ring (1) and a bearing inner ring (2), wherein the bearing outer ring (1) is in clearance fit with the bearing inner ring (2);
the bearing inner ring (2) is composed of a hollow cylinder (2-1) and two hollow truncated cones (2-2), and the lower bottom surfaces of the two hollow truncated cones (2-2) are respectively connected to the two ends of the hollow cylinder (2-1); a divergent area gap is formed between the conical inclined surfaces of the two hollow truncated cones (2-2) and the inner surface of the bearing outer ring (1), and a static pressure area gap is formed between the outer surface of the hollow cylinder (2-1) and the inner surface of the bearing outer ring (1);
an air inlet groove (1-1) is formed in the position, corresponding to the static pressure bearing area, of the outer surface of the bearing outer ring (1), and a plurality of air inlet throttling devices (1-2) are uniformly distributed in the air inlet groove (1-1) along the circumferential direction.
2. Drum-shaped double-cone hydrostatic radial sliding bearing according to claim 1, characterized in that the clearance at the smallest clearance of the bearing outer ring (1) and the bearing inner ring (2) is 0.1-50 μm.
3. The drum-shaped double-cone dynamic-static pressure radial sliding bearing according to claim 1, wherein the bearing outer ring (1) is a hollow cylinder, and the air inlet groove (1-1) is circumferentially formed on the outer surface of the hollow cylinder; the central lines of the hollow cylinder (2-1) and the two hollow truncated cones (2-2) are coincident, and the lower bottom surfaces of the two hollow truncated cones (2-2) are respectively equal to and attached to the two bottom surfaces of the hollow cylinder (2-1).
4. The drum-shaped double-conical surface dynamic-static pressure radial sliding bearing according to claim 1, wherein the air inlet throttling device (1-2) is a circular through hole, the axis of the air inlet throttling device is orthogonal to the axis of the bearing outer ring (1), the diameter is in the range of 0.5-5 mm, the length is 0.4-0.9 times of the thickness of the bearing outer ring (1), the ratio of the length to the diameter is in the range of 1-20, and the short capillary throttling condition is met.
5. The drum-shaped double-cone dynamic-static pressure radial sliding bearing according to claim 1, wherein a rectangular pressure cavity (1-3) is arranged at the tail end of the air inlet throttling device (1-2), and the cavity depth of the rectangular pressure cavity (1-3) is 0.5-5 mm; the axial length is 1/9-2/9 of the width of the bearing, and the ratio of the circumferential length to the axial length is 0.8-1.2.
6. The drum-shaped double-conical surface dynamic-static pressure radial sliding bearing according to claim 1, wherein conical inclined surfaces of the hollow truncated cones (2-2) are uniformly distributed with a plurality of groups of modified groove structures (2-2-1) or micro textures along the circumferential direction, and the number of the modified groove structures (2-2-1) or the micro textures on the two hollow truncated cones (2-2) is the same and symmetrically distributed.
7. The drum-shaped double-cone hydrostatic dynamic radial sliding bearing according to claim 6, characterized in that the groove type of the modified groove structure (2-2-1) is a spiral groove, a rectangular groove or a triangular groove, the groove depth is 0.1-10 μm to facilitate the formation of dynamic pressure effect; the microtexture is a plurality of rows of combined circular microtrences, triangular microtrences, square microtrences or rectangular microtrences, the total area of the microtexture occupies 1/3-2/3 of the area of the conical inclined surface, and the pit depth is 0.1-3 mm, so that the local hydrostatic effect is formed on the microtexture part.
8. The drum-shaped double-cone hydrostatic radial sliding bearing according to claim 7, characterized in that when the groove type of the modified groove structure (2-2-1) is a spiral groove, there are a plurality of sets of spiral grooves; spiral grooves on the two hollow truncated cones (2-2) are opposite in rotation direction; when the bearing inner ring (2) rotates anticlockwise, the spiral directions of the spiral grooves on the two hollow truncated cones (2-2) are consistent with the fluid flow trend, so that the fluid circulation is promoted, and the lubrication effect is maintained; when the bearing inner ring (2) rotates clockwise, the spiral directions of the spiral grooves on the two hollow truncated cones (2-2) are opposite to the fluid flow trend, so that the bearing flow is reduced, and the bearing static pressure effect is improved.
9. The drum-shaped double-cone dynamic-static pressure radial sliding bearing according to claim 1, wherein the axial lengths of the clearance of the divergence area and the clearance of the static pressure area are equal, the taper range of the hollow truncated cone (2-2) is 0.5-10 degrees, the bearing is designed according to the external axial force born by the hollow truncated cone or for increasing the bearing flow to achieve the purpose of cooling the bearing, when the taper is increased, the axial limit load born by the bearing is increased, and meanwhile, the bearing flow is increased due to the increase of the clearance of the divergence area of the bearing, so that the heat dissipation capacity of the bearing is improved; when the taper is reduced, the radial limit load born by the bearing is increased, and meanwhile, the clearance of the divergent area of the bearing is reduced, so that the flow of the bearing is reduced, and the heat dissipation capacity of the bearing is further reduced.
10. Drum-shaped double-cone hydrostatic radial sliding bearing according to claim 1, characterized in that the inner bore of the bearing inner ring (2) is in interference fit or transition fit with the shaft.
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202310161092.0A CN116044904A (en) | 2023-02-24 | 2023-02-24 | Drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing |
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| Application Number | Priority Date | Filing Date | Title |
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| CN202310161092.0A CN116044904A (en) | 2023-02-24 | 2023-02-24 | Drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing |
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Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116765442A (en) * | 2023-08-28 | 2023-09-19 | 凌远科技股份有限公司 | Bearing element and bearing |
| CN116972067A (en) * | 2023-09-25 | 2023-10-31 | 天津飞旋科技股份有限公司 | Dynamic and static pressure mixed foil bearing and shafting |
-
2023
- 2023-02-24 CN CN202310161092.0A patent/CN116044904A/en active Pending
Cited By (4)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN116765442A (en) * | 2023-08-28 | 2023-09-19 | 凌远科技股份有限公司 | Bearing element and bearing |
| CN116765442B (en) * | 2023-08-28 | 2023-11-10 | 凌远科技股份有限公司 | Bearing element and bearing |
| CN116972067A (en) * | 2023-09-25 | 2023-10-31 | 天津飞旋科技股份有限公司 | Dynamic and static pressure mixed foil bearing and shafting |
| CN116972067B (en) * | 2023-09-25 | 2023-11-28 | 天津飞旋科技股份有限公司 | Dynamic and static pressure mixed foil bearing and shafting |
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