CN116044904A - Drum-shaped double-conical-surface dynamic-static pressure radial sliding bearing - Google Patents

Abstract

A drum-shaped double-cone dynamic and static pressure radial sliding bearing, including a bearing outer ring and a bearing inner ring, the bearing outer ring and the bearing inner ring are in clearance fit; the bearing inner ring is composed of a hollow cylinder and two hollow truncated cones, The lower bottom surfaces of the two hollow truncated cones are respectively connected to the two ends of the hollow cylinder; the taper slopes of the two hollow truncated cones and the inner surface of the bearing outer ring form a gap in the divergent area, and the outer surface of the hollow cylinder A static pressure area gap is formed between the inner surface of the outer ring of the bearing and the position of the outer surface of the outer ring of the bearing corresponding to the static pressure bearing area. Air throttling device. The invention forms a dynamic and static pressure effect by constructing a wedge-shaped gap, the bearing can form a stable lubricating film and the bearing can bear a certain bidirectional axial load, has strong static pressure and dynamic pressure effects, and has good stability and dynamic performance.

Description

A drum-shaped double-cone dynamic and static pressure radial sliding bearing

technical field

The invention belongs to the technical field of sliding bearings, and relates to a drum-shaped double-cone dynamic and static pressure radial sliding bearing.

Background technique

Sliding bearings are suitable for high-speed working conditions due to the fluid film gap formed during their operation, and have the characteristics of extremely low friction coefficient and small interface wear. They are used more and more in various rotating mechanical systems. The lubricating medium of fluid radial sliding bearings can be liquid or gas, among which liquid lubrication, especially the sliding bearings under lubricating oil, has higher load capacity and good stability; gas-lubricated radial sliding bearings have high rotor precision, friction The advantages of low loss, low requirements on the working environment, clean and environmental protection are also used in various types of high-precision machine tools, high-speed aerodynamic devices, precision equipment or instrument systems and other equipment. However, traditional radial sliding bearings are generally difficult to bear axial loads and have poor high-speed stability. As the working conditions of bearings become more and more complex, the demand for new structures to solve the above problems is becoming more and more urgent.

In terms of the new structure of sliding bearings, there have been different literatures and patents discussing the structural update strategy of bearings, such as the new bearing structure of rolling-sliding combination, Zhang Guoyuan et al. disclosed a rolling-sliding radial composite bearing with adjustable positioning ( Application number: CN 112128237 A), its structure is mainly to install elastic cylindrical rollers, fixed bearing pads and tiltable bearing pads on the cylindrical bearing housing, the fixed bearing pad is fixed to the bearing housing, and the pad fulcrum is fixed at the pin hole on the outer surface of the bearing housing The regulator can be used to fine-tune the gap between the rotor and the tilting bearing bush to ensure a good oil film thickness. The strict separation of the three avoids excessive wear and seizure of the bearing caused by roller slipping and being squeezed under impact load, effectively extending the life of the bearing. lifespan. Another example is a sliding radial-sliding thrust combined bearing disclosed by Zhang Guoyuan et al. (Application No.: CN 112128236 A). This invention combines the radial bearing and the thrust bearing, and the structure of the radial bearing is the same as the above-mentioned patent The main structure of the thrust bearing is that the mirror plate is fixed on the end face of the rotor, the thrust bearing seat of the double circular platform is installed at the lower end of the radial bearing seat, and the tiltable pad is installed on the second circular platform, and its structure is a cylindrical structure with an inclination angle. , and the mirror plate can form a wedge-shaped oil film to improve the performance of the bearing. Compared with the prior art, the invention effectively improves the service life of the bearing.

On the other hand, for the development of new structures for plain bearings, solutions are used to modify the surface features of the bearing or the associated rotor, ie surface modification. One is grooved or micro-textured on the bearing ID, and the other is modified (grooved or micro-textured) on the bearing mating rotor surface. However, the first solution is for sliding bearings for smaller diameter rotors, such as air radial sliding bearings, it is difficult to realize slotting or texturing at the inner diameter, and in high-speed operation, the clearance of the bearing needs to be designed more precisely , otherwise it is very easy to cause bearing instability under high-speed working conditions; the second solution is not easy to realize in actual engineering, because the design of the rotor and the bearing belong to different departments in practice, and the bearing as the basic component cannot make a contribution to the design of the rotor. Requirements; In addition, the modification of the rotor surface may affect the overall strength of the rotor, which may even affect the safety and stability of the rotor operation.

For the first solution, many researchers have proposed a new bearing structure, such as the application number CN113431844A, the patent titled "A High-Speed Spiral Groove Small Hole Segment Hydrostatic Gas Bearing Device" discloses an outer bearing structure. The dynamic and static pressure gas bearing is provided with an air supply hole and a small hole restrictor, and the inner side is provided with a spiral groove and an axial micro-through groove. The dynamic and static pressure gas bearing described in this invention can meet the purpose of avoiding dry friction and improving the stability of the rotor during the start and stop stages. When the rotor is running at high speed, it can stop the continuous high-pressure gas supply from the outside, and use the rotation of the journal to press the gas into the spiral groove. In order to improve the overall performance of the bearing; however, the spiral groove of this bearing is located on the inner side, and the axial micro-through groove is located in the middle section of the inner side of the bearing, which is difficult to process. Another example is the patent No. CN 110242671 A, the invention patent titled "a conical foil dynamic pressure air bearing" discloses a conical bearing with radial foils applied, and its structure changes the hollow cylinder into a hollow cone body and install radial foils on the outside. This invention can bear radial force and axial force at the same time and has a large bearing capacity, but it does not point out the matching relationship between the bearing and the rotor, and cannot form an effective oil film thickness when the rotor starts and stops, resulting in excessive frictional resistance , affecting the stability of the rotor.

In recent years, some researchers have proposed surface modification methods for improving the performance of sliding bearings, and some theoretical progress has been made. Based on the bearing model, the bearing capacity was calculated by the hydrodynamic method, and the influence law of the shape and depth of the micro-texture on the bearing capacity of the aerodynamic bearing was obtained. The research results show that the surface micro-texture has a certain influence on the bearing capacity of the aerodynamic bearing. [Ding Hao, Gao Qiang, Feng Wei, Liu Baoguo, Li Xingyu. The effect of surface micro-texture on the load-carrying performance of aerodynamic bearings [J]. Bearings, 2022, 10:105-110.]. This kind of method of improving bearing performance through surface modification has attracted more and more attention from researchers, and it is also an important direction for the development of bearing technology.

In summary, in view of the new structural requirements and theoretical research progress of sliding bearings, it is necessary to develop solutions that are easier to manufacture and improve their overall performance.

Contents of the invention

In order to overcome the above-mentioned shortcomings of the prior art, the object of the present invention is to provide a drum-shaped double-cone dynamic and static pressure radial sliding bearing, which can form a stable lubricating film and the bearing can withstand Certain bidirectional axial load, strong static pressure and dynamic pressure effects, good stability and dynamic performance.

In order to achieve the above object, the technical scheme adopted in the present invention is:

A drum-shaped double-cone dynamic and static pressure radial sliding bearing, including a bearing outer ring and a bearing inner ring, and the bearing outer ring is in clearance fit with the bearing inner ring;

The bearing inner ring is composed of a hollow cylinder and two hollow truncated cones, the lower bottom surfaces of the two hollow truncated cones are respectively connected to the two ends of the hollow cylinder; the two hollow truncated cones A divergent area gap is formed between the tapered surface of the cone 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;

On the outer surface of the bearing outer ring at a position corresponding to the static pressure bearing area, an air intake slot is opened, and a plurality of air intake throttling devices are uniformly distributed in the circumferential direction in the air intake slot.

In one embodiment, the minimum gap between the bearing outer ring and the bearing inner ring is 0.1-50 μm.

In one embodiment, the outer ring of the bearing is a hollow cylinder, and the air inlet groove is provided on the outer surface of the hollow cylinder along the circumferential direction; the center of the hollow cylinder and two hollow truncated cones The lines are coincident, and the 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 intake throttling device is a circular through hole, the axis of which is perpendicular to the axis of the outer ring of the bearing, the diameter ranges from 0.5 to 5 mm, and the length is 0.4 to 0.9 times the thickness of the outer ring of the bearing. And the length-to-diameter ratio ranges from 1 to 20, which satisfies the condition of short-haired detail flow.

In one embodiment, a rectangular pressure chamber is provided at the end of the air intake throttling device, and the depth of the rectangular pressure chamber is 0.5-5mm; the axial length is 1/9-2/9 of the bearing width, and the circumferential length The ratio to the axial length is 0.8 to 1.2.

In one embodiment, the tapered surface of the hollow truncated cone is uniformly distributed with multiple groups of modified groove structures or microtextures along the circumference, and the number of modified groove structures or microtextures on the two hollow truncated cones is same and symmetrical distribution.

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 μm to facilitate the formation of the dynamic pressure effect; the micro-texture is a combination of multiple rows of circles Shaped micro-pit, triangular micro-pit, square micro-pit or rectangular micro-pit, the total area of micro-texture accounts for 1/3-2/3 of the area of the cone slope, and the depth of the pit is 0.1-3mm, which helps to form local micro-pit in the micro-texture part static pressure effect.

In one embodiment, when the groove type of the modified groove structure is a spiral groove, there are multiple sets of spiral grooves; the spiral grooves on the two hollow truncated cones have opposite directions of rotation; when the inner ring of the bearing rotates counterclockwise , the rotation direction of the spiral grooves on the two hollow truncated cones is consistent with the fluid flow trend, which promotes fluid circulation and maintains the lubrication effect; when the inner ring of the bearing rotates clockwise, the spiral grooves on the two hollow truncated cones The direction of rotation is opposite to the trend of fluid flow, reducing the bearing flow and increasing the static pressure effect of the bearing.

In one embodiment, the axial lengths of the gap in the diverging region and the gap in the static pressure region are equal, and the taper of the hollow truncated cone is in the range of 0.5° to 10°. According to the external axial force it bears or increases The bearing flow is designed for the purpose of cooling the bearing. When the taper increases, the axial limit load that the bearing can withstand increases. At the same time, the gap in the divergent area of the bearing increases, which leads to an increase in the bearing flow and improves the bearing heat dissipation capacity; when the taper decreases , the radial limit load that the bearing can withstand increases, and at the same time, the clearance in the divergent area of the bearing decreases, resulting in a decrease in the bearing flow and thus reducing the heat dissipation capacity of the bearing.

In one embodiment, the inner hole of the inner ring of the bearing is in interference fit or transition fit with the shaft.

Compared with prior art, the beneficial effect of the present invention is:

1. The innovative structural scheme of the split type fluid lubricated sliding bearing adopted in the present invention can design reasonable throttling devices and groove parameters according to working conditions to increase the load bearing and air film stiffness. Specifically, at higher speeds, the spiral grooves or micro-textures distributed symmetrically on the two cone slopes of the inner ring of the bearing enhance the hydrodynamic pressure effect to improve the bearing and air film stiffness; at lower speeds, through the short hair details The flow and external higher air supply pressure are used to improve the static pressure effect of the fluid to achieve the improvement of the load-bearing performance and so on.

2. There is a micron-level gap between the inner ring and the outer ring of the present invention, and the pressure chamber is at the millimeter level, so that a more stable air film can be obtained and the bearing capacity of the bearing can be improved.

3. The truncated conical structure adopted by the inner ring of the present invention has a large gap at both ends during operation, which can effectively press the medium into the bearing, and can also bear the impact of axial force and radial force at the same time, improving the service life of the bearing.

Description of drawings

Figure 1 is a schematic diagram of the overall structure of the present invention.

Figure 2 is a front view of the bearing outer ring.

Figure 3 is a radial sectional view of the bearing outer ring.

Fig. 4 is a structural schematic diagram of the spiral groove inner ring of the bearing.

Fig. 5 is a structural schematic diagram of a triangular micro-textured inner ring of a bearing.

Detailed ways

The implementation of the present invention will be described in detail below in conjunction with the drawings and examples.

The invention forms a dynamic and static radial sliding bearing with a dynamic and static pressure effect by constructing a wedge-shaped gap, specifically a detachable dynamic and static radial sliding bearing with a drum-shaped double cone surface on the inner ring and a throttling device on the outer ring. The bearing carries the static characteristics and enhances the running dynamic characteristics.

Specifically, as shown in Figures 1 to 5, the drum-shaped double-cone dynamic and static pressure radial sliding bearing of the present invention includes a bearing outer ring 1 and a bearing inner ring 2, and the bearing outer ring 1 and the bearing inner ring 2 are in a clearance fit relationship , the bearing inner ring 2 is coaxially arranged in the bearing outer ring 1, and the inner hole of the bearing inner ring 2 is interference fit or transition fit with the shaft.

Wherein, the outer surface of the bearing outer ring 1 is provided with circumferential air intake grooves 1-1, and in the air intake grooves 1-1, a plurality of air intake throttling devices 1-2 are uniformly distributed along the circumferential direction.

The bearing inner ring 2 is composed of a hollow cylinder 2-1 and two symmetrical hollow truncated cones 2-2. The hollow truncated cone 2-2 refers to a frustum-shaped structure obtained by truncating a hollow cone. Here, "hollow" means that there is a through hole along the central axis. It is easy to understand that the central axis of the through hole is consistent with the central axis of the cone or the truncated cone. Similarly, the hollow cylinder 2-1 refers to a cylinder with an axial through hole, and it is easy to understand that the central axis of the through hole is consistent with the central axis of the cylinder. 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; obviously, the hollow part of the hollow cylinder 2-1 is the "through hole" and the two hollow truncated cones The hollow part of 2-2, that is, the "through hole" is equal in diameter and coaxial, that is, the centerlines of the hollow cylinder 2-1 and the two hollow truncated cones 2-2 coincide. Exemplarily, the 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. In the present invention, "lower bottom surface" refers to the larger bottom surface in the cross-sectional frustum-shaped structure. Correspondingly, the "upper bottom surface" refers to the smaller bottom surface of the truncated conical structure. 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 tapered surfaces of the two hollow truncated cones 2-2 and the inner surface of the bearing outer ring 1, and the outer surface of the hollow cylinder 2-1 A static pressure area gap is formed between the surface and the inner surface of the bearing outer ring 1 . Wherein, the air intake groove 1-1 corresponds to the position of the static pressure bearing area. The gap in the divergent area promotes the formation of the dynamic pressure effect during the rotation of the inner ring, and the gap in the static pressure area forms a static pressure effect when passing through the air intake throttling device. Therefore, during operation, the gap at both ends is large and the gap in the middle is small, which can effectively press the medium into the bearing, and can also bear the impact of axial force and radial force at the same time, which improves the service life of the bearing.

The axial lengths of the three gaps are the same, and the taper of the truncated cone is designed according to the actual working conditions, so as to obtain different gaps in divergent regions, so as to improve the mechanical properties and heat dissipation performance of the bearing.

In some embodiments of the present invention, the minimum gap between the bearing outer ring 1 and the bearing inner ring 2 is 0.1-50 μm, which is at the micron level.

In some embodiments of the present invention, the bearing outer ring 1 is a hollow cylinder, where the definition of the hollow cylinder is similar to that of the aforementioned hollow cylinder 2-1, that is, a cylinder with an axial through hole. The bearing inner ring 2 is coaxially located in the axial through hole. The number of air intake groove 1-1 is one, and can also be a plurality of symmetrical ones, and is provided on the outer surface of the hollow cylinder along the circumferential direction. The air intake throttling devices 1-2 are arranged in a single row, that is, all the air intake throttling devices 1-2 are on the same circumference, and are preferably evenly distributed. The number of air intake throttling devices 1-2 is generally 4-16, and the number value is designed according to the working condition of the bearing and structural parameters.

In some embodiments of the present invention, the air intake throttling device 1-2 is a circular through hole, the axis of which is perpendicular to the axis of the bearing outer ring 1, the diameter ranges from 0.5 to 3mm, and the length is the thickness of the bearing outer ring 1 0.4-0.9 times of that, and the length-to-diameter ratio ranges from 1 to 20, satisfying the condition of short-haired detail flow.

In some embodiments of the present invention, a rectangular pressure chamber 1-3 is further provided at the end of the air intake throttling device 1-2. The pressure chambers 1-3 communicate with each other, and the axis of the air intake throttling device 1-2 coincides with the geometric centerline of the rectangular pressure chamber 1-3. Rectangular pressure chamber 1-3 means that its section along the vertical axis is rectangular or approximately rectangular, and its cavity depth (that is, the radial length) is mm, ranging from 0.5 to 5mm; the axial length is 1/9 of the bearing width ～2/9, the ratio of the circumferential length to the axial length is 0.8～1.2. The micron-level gap between the inner and outer rings and the millimeter-level cavity depth of the pressure chamber can obtain a more stable air film and improve the bearing capacity of the bearing. Specifically, the deep cavity parameter design can be reasonably carried out in combination with the static pressure bearing characteristics of the bearing.

In some embodiments of the present invention, the tapered surface of the hollow truncated cone 2-2 is evenly distributed along the circumferential direction with multiple groups of modified groove structures 2-2-1 or other micro-textures, and the two hollow truncated cones The number of modified groove structures 2-2-1 or micro-textures on 2-2 is the same and distributed symmetrically.

In some embodiments of the present invention, the groove type of the modified groove structure 2-2-1 is a spiral groove, a rectangular groove or a triangular groove, and the number of grooves is 4 to 16, which are in the micron order and range from 0.1 to 10 μm. Contribute to the formation of dynamic pressure effect; the micro-texture is a multi-row combination of circular micro-pit, triangular micro-pit, square micro-pit or rectangular micro-pit, etc., the total area of the micro-texture accounts for 1/3 to 2/3 of the area of the cone slope , The depth of the pit is 0.1-3mm, which helps to form a local static pressure effect in the micro-textured part.

In some embodiments of the present invention, when the groove type of the modified groove structure 2-2-1 is a spiral groove, there are multiple sets of spiral grooves, and the form can be various types of logarithms, involutes, expansion lines, etc.; The helical grooves on the two hollow truncated cones 2-2 have opposite directions of rotation, that is, the helical grooves on the two hollow truncated cones 2-2 are symmetrical about the center plane of the bearing width. In the embodiment, the left side of the cone The spiral groove is left-handed, and the right-hand spiral groove is right-handed. When the bearing inner ring 2 rotates counterclockwise, the helical grooves on the two hollow truncated cones 2-2 are in the same direction as the fluid flow trend, which promotes fluid circulation and maintains the lubrication effect; when the bearing inner ring 2 rotates clockwise , the direction of rotation of the spiral grooves on the two hollow truncated cones 2-2 is opposite to the flow trend of the fluid, reducing the bearing flow rate and improving the static pressure effect of the bearing.

In some embodiments of the present invention, the axial lengths of the divergent area gap and the static pressure area gap are equal, and the taper range of the hollow truncated cone 2-2 is about 0.5-10°, according to the external axial force it bears Or design for the purpose of increasing bearing flow to achieve bearing cooling. Specifically: when the taper increases, the axial limit load that the bearing can withstand increases, and at the same time, the gap in the divergent area of the bearing increases, resulting in an increase in the flow of the bearing and thereby improving the heat dissipation capacity of the bearing; when the taper decreases, the radial load that the bearing can withstand The increase of ultimate load and the reduction of clearance in the divergent area of the bearing lead to the reduction of bearing flow and thus reduce the heat dissipation capacity of the bearing.

The following are two specific embodiments of the present invention.

Example 1:

For high-speed and heavy-duty applications, a drum-shaped double-cone dynamic and static pressure radial bearing is proposed. The following is a further detailed description in conjunction with the accompanying drawings:

Referring to Fig. 1, the present invention includes a bearing outer ring 1 and a bearing inner ring 2, wherein:

Bearing outer ring 1, the structure of which is shown in Figure 2 and Figure 3, is provided with an air intake groove 1-1, an air intake throttling device 1-2 and a rectangular pressure chamber 1-3.

The bearing outer ring 1 is a hollow cylinder, and an air intake groove 1-1 is provided on the outer surface of the hollow cylinder along the circumferential direction, and a plurality of single-row air intake throttling devices 1-2 are evenly distributed in the groove, some of which are A rectangular pressure chamber 1-3 is provided at the end of the flow device 1-2. In this embodiment, the outer diameter of the outer ring is 60 mm, the inner diameter is 50 mm, the thickness is 5 mm, the width is 9 mm, and the depth of the air inlet groove is 1 mm.

The single-row air intake throttling device 1-2 is located in the air intake slot 1-1, as shown in Figure 2, is evenly distributed along the circumference, and all the centers of circles are located on the center line of the air intake slot; the number is 8, the length is 3mm, and the diameter The value is 0.5mm, and the length-to-diameter ratio is 6, which meets the parameter range of the short hair detail flow structure device.

Rectangular pressure chamber 1-3, as shown in Figure 3, its upper end communicates with air intake throttle device 1-2, which can further enhance the static pressure effect at the tail of the throttle device, and the axis of air intake throttle device is aligned with the geometric centerline of the pressure chamber Coincident, the axis of the air intake throttling device is perpendicular to the axis of the hollow cylinder, and the end connects the gap between the outer ring and the inner ring to provide sufficient liquid for the bearing to meet the lubrication requirements of the bearing; combined with the static pressure bearing characteristics of the bearing, the pressure chamber The cavity depth is designed to be 1 mm; the deep cavity section is a rectangular cross-section structure, the circumferential length of the pressure chamber is 2.4 mm, the axial length is 2 mm, and the ratio between the two is 1.2.

The bearing inner ring 2, as shown in Fig. 4, includes a hollow cylinder 2-1 and a hollow truncated cone 2-2, and the hollow truncated cone 2-2 is provided with a modified groove structure 2-2-1.

Specifically, the bearing inner ring 2 is composed of a hollow cylinder 2-1 and a pair of symmetrical hollow truncated cones 2-2. coincide with the two bottom surfaces of the hollow cylinder 2-1 respectively, the two ends of the inner ring are the upper bottom surfaces of the two hollow truncated cones 2-2, and the two conical slopes are used to form a divergent gap area; the hollow cylinder 2-1 It is located in the middle of the small ends of the cones on both sides to form a static pressure bearing area; the inner diameter of the inner ring and the shaft have an interference fit, so that the inner ring rotates with the rotor. The outer diameter of the inner ring is 50mm and the inner diameter is 40mm.

There is a gap fit between the bearing inner ring 2 and the bearing outer ring 1, and three gaps are formed between the bearing outer ring and the inner ring, which are the divergent area gaps formed by the left and right tapered outer sides of the inner ring and the inner diameter of the outer ring; the middle part The hydrostatic zone clearance formed between the outer diameter of the inner ring and the inner diameter of the outer ring. The gap in the divergent area promotes the formation of the dynamic pressure effect during the rotation of the inner ring, and the gap in the static pressure area forms a static pressure effect when passing through the air intake throttling device. The axial lengths of the three gaps are all the same, and are all taken as 3 mm, and the gap in the static pressure area is taken as 5 μm.

The taper of the cone is 3°; the size of the taper directly affects the divergence gap formed by the left and right taper outer divergence gap areas of the inner ring and the inner diameter of the outer ring. In this embodiment, the bearing is in a high-speed and heavy-load situation. The deformation of the bearing structure and the temperature rise may exceed the standard caused by too high. When designing the truncated conical taper, it is necessary to ensure that the bearing has good heat dissipation performance. Therefore, the existence of the taper can increase the bearing flow rate and reduce the bearing temperature rise. At the same time, changing the taper of the cone will obtain different bearing performance, that is, increasing the taper, the axial load that the drum-shaped double-cone dynamic and static pressure radial bearing can carry increases; reducing the taper, the drum-shaped double-cone dynamic and static pressure The axial load of the radial bearing is reduced; for this reason, the taper of the truncated cone is considered to be 3°.

On the outer surface of the truncated cone, multiple groups of modified groove structures 2-2-1 are evenly distributed along the circumference, and the modified grooves are multiple groups of spiral grooves, and the grooves on the left and right sides of the cone have opposite directions of rotation (that is, two hollow truncated cones 2 The spiral groove on -2 is symmetrical with respect to the center plane of the bearing width), the spiral groove on the left side of the cone is left-handed, and the right spiral groove is right-handed; when the bearing inner ring 2 rotates counterclockwise, the spiral grooves on the left and right cone sides The direction of rotation is consistent with the trend of fluid flow, which promotes fluid circulation and maintains the lubrication effect; when the bearing inner ring 2 rotates clockwise, the direction of rotation of the spiral grooves on the side of the left and right cones is opposite to the trend of fluid flow, reducing the flow rate of the bearing and increasing the static pressure of the bearing Effect: In this embodiment, the number of modified grooves on the side of the cone is 16, the groove depth is 1 μm, and the helix angle is 45°; the width of the spiral groove is 2 mm.

Example 2:

Below in conjunction with the accompanying drawings, taking the sliding bearing for the main shaft of a wind power generating set as an example, the present invention will be further described in detail:

Referring to Fig. 1, the present invention includes a bearing outer ring 1 and a bearing inner ring 2, wherein:

Bearing outer ring 1, the structure of which is shown in Figure 2 and Figure 3, is provided with an air intake groove 1-1, an air intake throttling device 1-2 and a rectangular pressure chamber 1-3.

The structure of the bearing outer ring 1 is exactly the same as that of Embodiment 1 except that various structural parameters are different. In this embodiment, the outer diameter of the outer ring is 800 mm, the inner diameter is 700 mm, the thickness is 50 mm, the width is 90 mm, and the depth of the air intake groove is 10 mm. The medium provided externally must be high-pressure lubricating oil to ensure a good lubricating film for the bearing.

The single-row air intake throttling device 1-2 is located in the air intake slot 1-1, as shown in Figure 2, is evenly distributed along the circumference, and all circle centers are located on the center line of the air intake slot; the number is 12, and two adjacent throttles The devices are separated by 30°. The length is 30mm, the diameter is 3mm, and the ratio of the length to the diameter is 10, which meets the parameter range of the short hair detail flow structure device.

Rectangular pressure chamber 1-3, as shown in Figure 3, its upper end communicates with air intake throttle device 1-2 to further enhance the static pressure effect at the tail of the throttle device, and the axis of air intake throttle device coincides with the geometric centerline of the pressure chamber , the axis of the air intake throttling device is perpendicular to the axis of the hollow cylinder, and the end connects the gap between the outer ring and the inner ring to provide sufficient liquid for the bearing to meet the lubrication requirements of the bearing; combined with the static pressure bearing characteristics of the bearing, the pressure chamber The depth is designed to be 10mm; the section of the deep cavity is a rectangular section structure, the circumferential length is 12mm, the axial length is 10mm, and the ratio between the two is 1.2.

Bearing inner ring 2, the structure of which is shown in Figure 4, includes a hollow cylinder 2-1 and a hollow truncated cone 2-2, and on the hollow truncated cone 2-2, the modified groove structure 2-2 is replaced by a micro-texture -1.

Specifically, the bearing inner ring 2 is composed of a hollow cylinder 2-1 and a pair of symmetrical hollow truncated cones 2-2. coincide with the two bottom surfaces of the hollow cylinder 2-1 respectively, the two ends of the inner ring are the upper bottom surfaces of the two hollow truncated cones 2-2, and the two conical slopes are used to form a divergent gap area; the hollow cylinder 2-1 It is located in the middle of the small ends of the cones on both sides to form a static pressure bearing area; the inner diameter of the inner ring is transitionally matched with the main shaft, so that the inner ring rotates with the main shaft. The outer diameter of the inner ring is 700mm and the inner diameter is 650mm.

There is a clearance fit between the bearing inner ring 2 and the bearing outer ring 1, and three gaps are formed between the bearing outer ring and the inner ring. The axial lengths of the three gaps are all the same, all of which are 30 mm, and the gap in the static pressure area is 20 μm. In this embodiment, the bearing bears a very heavy load, so sufficient oil film thickness is required to ensure the normal operation of the bearing.

The taper of the cone is 0.5°; since the main force of the main shaft bearing of the wind turbine is the weight of the wind 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, changing the taper of the cone Different bearing performance will be obtained, increasing the taper, the axial load that the drum-shaped double-cone dynamic and static radial bearing can carry increases; reducing the taper, the maximum diameter that the drum-shaped double-cone dynamic and static radial bearing can carry The axial load increases while the axial load decreases. In order to improve the bearing capacity of the bearing, the taper of the truncated cone is designed to be 0.5° according to the ratio of the radial limit load to the axial limit load

On the outer surface of the truncated cone, multiple groups of microtexture 2-2-1 are evenly distributed along the circumference. The microtexture is a double row of triangular micropit, with 16 groups distributed on each side. The sides of the left and right cones are symmetrical, and the triangle is an equilateral triangle. , the side length is 10mm, the area occupied is 2/3 of the entire side area, and the groove depth is 2mm; the triangular micro-texture is used to improve the bearing capacity and at the same time, a local static pressure effect can be formed on the side of the truncated cone.

Claims (10)

1. a drum-shaped double-cone dynamic and static pressure radial sliding bearing, is characterized in that, comprises bearing outer ring (1) and bearing inner ring (2), described bearing outer ring (1) and described bearing inner ring ( 2) Clearance fit; 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 both ends of the hollow cylinder (2-1); a divergent area is formed between the tapered surfaces of the two hollow truncated cones (2-2) and the inner surface of the bearing outer ring (1) A gap, 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); At the position corresponding to the static pressure bearing area on the outer surface of the bearing outer ring (1), air intake grooves (1-1) are provided, and the air intake grooves (1-1) are evenly distributed along the circumferential direction There are multiple air intake throttling devices (1-2). 2. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1, characterized in that the minimum gap between the bearing outer ring (1) and the bearing inner ring (2) is 0.1- 50 μm. 3. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1, characterized in that, the bearing outer ring (1) is a hollow cylinder, and the air inlet groove (1-1) is along the circumferential direction Set on the outer surface of the hollow cylinder; the centerlines of the hollow cylinder (2-1) and the two hollow truncated cones (2-2) coincide, and the two hollow truncated cones (2-2) ) are equal to and attached to the two bottom surfaces of the hollow cylinder (2-1) respectively. 4. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1 is characterized in that, the air inlet throttling device (1-2) is a circular through hole, and its axis is in line with the outer ring of the bearing (1-2). ) is perpendicular to the axis, the diameter ranges from 0.5 to 5 mm, the length is 0.4 to 0.9 times the thickness of the bearing outer ring (1), and the ratio of length to diameter is in the range of 1 to 20, satisfying the short hair fine flow condition. 5. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1, characterized in that, a rectangular pressure chamber (1-3) is provided at the end of the air intake throttling device (1-2), and the rectangular pressure chamber (1-3) is The depth of the pressure chamber (1-3) is 0.5-5mm; the axial length is 1/9-2/9 of the bearing width, and the ratio of the circumferential length to the axial length is 0.8-1.2. 6. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1, characterized in that, the conical inclined surface of the hollow truncated cone (2-2) is uniformly distributed along the circumferential direction with multiple sets of modified groove structures (2-2-1) or microtexture, the modified groove structures (2-2-1) or microtextures on the two hollow truncated cones (2-2) have the same number and symmetrical distribution. 7. The drum-shaped double-cone dynamic and static pressure 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 depth of the groove is 0.1-10 μm to facilitate the formation of the dynamic pressure effect; the micro-texture is a combination of multiple rows of circular micro-pit, triangular micro-pit, square micro-pit or rectangular micro-pit, the total area of the micro-texture accounts for the area of the cone slope 1/3 to 2/3 of the pit depth is 0.1 to 3mm, which helps to form a local static pressure effect in the micro-textured part. 8. The drum-shaped double-cone dynamic and static pressure 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, how many spiral grooves are there? group; the spiral grooves on the two hollow truncated cones (2-2) rotate in opposite directions; when the bearing inner ring (2) rotates counterclockwise, the spiral grooves on the two hollow truncated cones (2-2) The direction of rotation is consistent with the trend of fluid flow, which promotes fluid circulation and maintains the lubrication effect; when the inner ring of the bearing (2) rotates clockwise, the direction of rotation of the spiral grooves on the two hollow truncated cones (2-2) is consistent with that of the fluid The flow trend is opposite, reducing the bearing flow and increasing the bearing static pressure effect. 9. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1 is characterized in that, the axial lengths of the diverging region gap and the static pressure region gap are equal, and the hollow truncated cone (2- 2) The range of taper is 0.5-10°. It is designed according to the external axial force it bears or for the purpose of increasing the bearing flow to achieve bearing cooling. When the taper increases, the axial limit load that the bearing can bear increases. When the taper is small, the radial limit load that the bearing can withstand increases, and at the same time, the clearance in the divergent area of the bearing decreases, resulting in a decrease in the bearing flow rate and thus reducing Bearing cooling capacity. 10. The drum-shaped double-cone dynamic and static pressure radial sliding bearing according to claim 1, characterized in that the inner hole of the inner ring of the bearing (2) is in interference fit or transition fit with the shaft.

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