An axial air bearing, motor and air circulator

Abstract

The utility model discloses an axial air floatation bearing, motor and air circulation machine, axial air floatation bearing includes: bearing body, the middle part of bearing body is provided with through -hole, and bearing body at least one side interval setting has a plurality of bearing bush along the circumference, and bearing bush extends along the radial direction of bearing body, and forms bearing gas groove between adjacent bearing bush, and the height of bearing bush is higher than the height of bearing gas groove, and bearing bush has opposite first side and second side along the direction of rotation, and the first side of bearing bush is pressure outlet side, and the second side of bearing bush is pressure inlet side, and the pressure inlet side of bearing bush is arc setting, the utility model discloses a bearing bush pressure inlet side is set as arc, makes the high pressure area in the middle of bearing bush, has improved gas dynamic pressure effect obviously, makes gas film pressure distribution more concentrated to improve axial bearing capacity.

Description

Technical Field

[0001] This utility model relates to the field of bearing technology, and in particular to an axial air bearing, a motor, and an air circulator. Background Technology

[0002] Air circulators, as key equipment for achieving compressed air circulation and refrigeration, play a vital role in aerospace, refrigeration, and air conditioning industries. During the operation of an air circulator, the bearings, as the core components supporting the high-speed rotation of the rotor, directly affect the overall efficiency and reliability of the machine.

[0003] Conventional roller bearings have significant limitations in the application of air circulators: on the one hand, under high-speed operating conditions, roller bearings generate large centrifugal forces, which aggravates component wear; on the other hand, they require continuous lubrication to maintain normal operation, which not only increases the complexity of the system, but also easily generates a large amount of frictional heat during high-speed friction, which is extremely detrimental to the efficient operation of refrigeration equipment, and can easily lead to increased equipment temperature, increased energy consumption, or even failure.

[0004] To address the aforementioned issues, air suspension bearings, which operate without direct contact and exhibit hydrodynamic effects, have been widely adopted in air circulators due to their advantages of requiring no lubrication, low frictional loss, and high applicable speeds. Among these, the thrust bearing used for axial rotor fixation is a core component for the stable operation of the air circulator, and its performance is crucial to the safe and stable operation of the entire machine.

[0005] However, the load-bearing capacity of axial air bearings is influenced by a combination of factors, including the bearing's structural form, the rotor's operating speed, environmental pressure, and the physical properties of the lubricating fluid. In practical applications, effectively improving the load-bearing capacity of axial air bearings under complex operating conditions to meet the increasingly demanding performance requirements of air circulators has become a pressing challenge in the field of air bearing technology. Therefore, developing an axial air bearing structure with higher load-bearing capacity is of great significance for improving the overall performance of air circulators. Utility Model Content

[0006] The purpose of this invention is to provide an axial air bearing, a motor, and an air circulator, aiming to solve the problem of low load-bearing capacity of existing axial air bearings.

[0007] This utility model provides an axial air bearing, comprising: a bearing body, a through hole in the middle of the bearing body, a plurality of bearing bushes spaced circumferentially on at least one side of the bearing body, the bearing bushes extending radially along the bearing body, bearing air grooves formed between adjacent bearing bushes, the height of the bearing bushes being higher than the height of the bearing air grooves, the bearing bushes having a first side and a second side opposite to each other along the rotation direction, the first side of the bearing bush being a pressure outlet side, the second side of the bearing bush being a pressure inlet side, and the pressure inlet side of the bearing bush being arc-shaped.

[0008] Furthermore, the pressure outlet side of the bearing bush is planar.

[0009] Furthermore, the pressure inlet side is recessed in the direction of rotation of the bearing body.

[0010] Furthermore, the arc shape on the pressure inlet side is a polynomial-expressed arc shape.

[0011] Furthermore, the bearing bush extends from the through hole to the outer edge of the bearing body, and the bearing air groove extends from the through hole to the outer edge of the bearing body.

[0012] Furthermore, the top of the bearing bush is arc-shaped.

[0013] Furthermore, the other side of the bearing body is a flat surface.

[0014] Furthermore, the circumferential cross-sectional length of the bearing bush gradually increases from the inner side of the bearing body to the outer side of the bearing body.

[0015] This utility model embodiment also provides an electric motor, including: the above-mentioned axial air bearing.

[0016] This utility model embodiment also provides an air circulator, including: the motor described above.

[0017] This utility model discloses an axial air bearing, a motor, and an air circulator. The axial air bearing includes: a bearing body with a through hole in the middle; multiple bearing bushes spaced circumferentially on at least one side of the bearing body; the bearing bushes extending radially along the bearing body; bearing air grooves formed between adjacent bearing bushes; the height of the bearing bushes being higher than the height of the bearing air grooves; and the bearing bushes having a first side and a second side opposite to each other along the rotation direction. The first side of the bearing bush is a pressure outlet side, and the second side of the bearing bush is a pressure inlet side, which is arc-shaped. By setting the pressure inlet side of the bearing bush to be arc-shaped, this utility model creates a high-pressure zone in the middle of the bearing bush, significantly improving the gas dynamic pressure effect and making the air film pressure distribution more concentrated, thereby improving the axial load-bearing capacity. Attached Figure Description

[0018] To more clearly illustrate the technical solutions of the embodiments of this utility model, the drawings used in the description of the embodiments will be briefly introduced below. Obviously, the drawings described below are some embodiments of this utility model. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0019] Figure 1 A first-view structural schematic diagram of an existing axial air bearing;

[0020] Figure 2 A schematic diagram of the structure of an existing axial air bearing from a second perspective;

[0021] Figure 3 This is a third-view structural schematic diagram of an existing axial air bearing;

[0022] Figure 4 This is a schematic diagram of the structure of an existing axial air bearing when rotated counterclockwise.

[0023] Figure 5 This is a schematic diagram of the axial air bearing in this embodiment;

[0024] Figure 6 This is a schematic diagram of the axial air bearing in this embodiment when it rotates counterclockwise;

[0025] Figure 7 The planar pressure contour map of an existing axial air bearing;

[0026] Figure 8 A diagram showing the height of an existing axial air bearing;

[0027] Figure 9 This is a planar pressure cloud diagram of the axial air bearing in this embodiment;

[0028] Figure 10 This is a diagram showing the height of the axial air bearing in this embodiment;

[0029] Figure 11 This is a curve showing the bearing pressure inlet shape of the axial air bearing in this embodiment;

[0030] Figure 12 This is a pressure distribution diagram along the arc direction of the bearing pressure inlet and outlet of the axial air bearing in this embodiment.

[0031] Explanation of the labels in the diagram:

[0032] 1. Bearing body; 2. Through hole; 3. Bearing bush; 4. Bearing air groove; 5. Pressure outlet side; 6. Pressure inlet side. Detailed Implementation

[0033] The technical solutions of the present utility model will be clearly and completely described below with reference to the accompanying drawings of the embodiments. Obviously, the described embodiments are only some embodiments of the present utility model, not all embodiments. Based on the embodiments of the present utility model, all other embodiments obtained by those skilled in the art without creative effort are within the protection scope of the present utility model.

[0034] It should be understood that, when used in this specification and the appended claims, the terms “comprising” and “including” indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0035] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the scope of the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0036] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination of one or more of the associated listed items and all possible combinations, and includes such combinations.

[0037] Please see Figures 1-4 , Figure 1 The structure of the axial bearing of the air circulator is shown. The axial bearing has 6 bearing shells and 6 bearing grooves arranged in an alternating manner. The dimensional parameters of the thrust bearing are shown in Table 1.

[0038] Table 1

[0039] value 100mm 54mm 30° 0.005mm 0.003mm 58000rpm

[0040] Where D1 is the outer diameter of the bearing, D2 is the inner diameter of the bearing, α is the installation angle of the bearing air groove and the bearing bush, and t is the height difference between the top of the bearing bush and the bottom of the bearing air groove.

[0041] Its working principle is as follows: When the shaft collar rotates at high speed, gas film is generated in the bearing and thrust plate due to the gas dynamic pressure effect. The gas around the bearing will flow into the space between the thrust plate and the bearing surface due to the viscosity. As the rotor speed increases, the gas film pressure will also increase, and the bearing surface load will also increase.

[0042] In this embodiment, the gas film thickness is 0.003 mm, the shaft rotation speed is 58,000 rpm, the bearing external pressure level is ambient atmospheric pressure, and the shaft collar rotation direction is counterclockwise.

[0043] This embodiment adjusts the planar orientation of the bearing pressure inlet, transforming it from a straight line to an arc. The specific structural design is shown below:

[0044] Please see Figure 4 and Figure 5 This embodiment provides an axial air bearing, including: a bearing body 1, a through hole 2 in the middle of the bearing body 1, a plurality of bearing bushes 3 are arranged circumferentially on at least one side of the bearing body 1, the bearing bushes 3 extend radially along the bearing body 1, a bearing air groove 4 is formed between adjacent bearing bushes 3, the height of the bearing bushes 3 is higher than the height of the bearing air groove 4, the bearing bushes 3 have a first side and a second side opposite to each other in the rotation direction, the first side of the bearing bushes 3 is a pressure outlet side 5, the second side of the bearing bushes 3 is a pressure inlet side 6, and the pressure inlet side 6 of the bearing bushes 3 is arc-shaped.

[0045] In this embodiment, by setting the pressure inlet side 6 of the bearing bush 3 to an arc shape, a high-pressure zone is formed in the middle of the bearing bush 3, which significantly improves the gas dynamic pressure effect, makes the gas film pressure distribution more concentrated, and thus improves the axial bearing capacity.

[0046] Please see Figures 7-10 The results show a comparison of bearing surface pressure before and after optimization. Before optimization, the surface pressure distribution of bearing shell 3 was relatively even, but the pressure level was low, with the highest value being 1.59 atm (Atmospheric pressure, atm). After optimization, the area with higher surface pressure of bearing shell 3 was distributed in the middle of bearing shell 3, with the highest pressure level being 2.59 atm, while the radial pressure values ​​on both sides of bearing shell 3 were lower.

[0047] The optimized inlet pressure curve is as follows: Figure 11 As shown in the figure. The x-axis represents the difference between the inner and outer diameters (r), and the y-axis represents the arc height along the normal direction (r).

[0048] In this embodiment, the pressure outlet side 5 of the bearing bush 3 is set as a plane.

[0049] The planar design of the pressure outlet side 5 reduces airflow separation and turbulence, allowing gas to diffuse smoothly at the end of the bearing bush 3 and reducing the risk of gas film fluctuations. The bearing bush 3 and the air groove are evenly distributed circumferentially. Combined with the design of the gas film thickness (0.003mm) and installation angle (30°), the gas is accelerated and compressed at the pressure inlet side 6 of the bearing bush 3 before being stably released through the planar outlet side, forming a high-pressure gas film to support the rotor's axial load. This structure, through the synergistic effect of the planar pressure outlet side 5 and the arc-shaped pressure inlet side 6, optimizes the gas flow path, improves gas film rigidity and dynamic stability, and is suitable for applications with stringent precision and reliability requirements, such as air circulators and high-speed rotating equipment.

[0050] In this embodiment, the pressure inlet side 6 is recessed in the direction of rotation of the bearing body 1.

[0051] The pressure inlet side 6 of the bearing shell 3 is recessed towards the rotation direction of the bearing body 1, forming a recessed profile that matches the rotor's rotation direction (e.g., counterclockwise). The arc-shaped profile of this recessed structure smoothly transitions from the bottom of the bearing gas groove 4 to the top of the bearing shell 3, forming a flow-guiding surface facing the incoming flow. This recessed structure facing the rotation direction can more effectively capture and guide viscous gas into the convergent gap between the bearing shell 3 and the thrust disc, significantly improving the gas film pressure build-up efficiency and maximum pressure value through enhanced gas dynamic pressure effect, thereby optimizing the bearing's load-bearing performance.

[0052] Furthermore, the arc shape of the pressure inlet side 6 is a polynomial-expressed arc shape.

[0053] Specifically, the pressure inlet shape curve is expressed by a fourth-order polynomial, and its expression is:

[0054] y=A+B1*x^1+B2*x^2+B3*x^3+B4*x^4

[0055] Where the x-axis represents the difference between the inner and outer diameters (r), the y-axis represents the arc height along the normal direction (r), and the parameters of each polynomial in the expression are shown in Table 2:

[0056] Table 2

[0057] A 0.01882±0.0016 B1 1.13906±0.00104 B2 -0.07766±1.89572E-4 B3 0.00167±1.25767E-5 B4 -1.95497E-5±2.73206E-7

[0058] This polynomial curve optimizes the curvature distribution on the inlet side of the bearing bush 3, accelerating and compressing the gas along the arc-shaped surface upon entry, forming a more concentrated high-pressure gas film region and significantly enhancing the dynamic pressure effect. Simultaneously, the mathematical expression of the arc shape allows for precise control of the gas flow path, reducing the risk of turbulence and gas film separation. Combined with the gas film thickness (0.003mm), the bearing bush 3 mounting angle (30°), and the uniform distribution of the bearing bush 3 and the air grooves (e.g., 6 bearing bushes and 6 air grooves), it further improves the uniformity and dynamic stability of the gas film pressure distribution. This design, through precise control of the polynomial arc shape, overcomes the performance limitations of traditional straight-line or simple curve designs, making it suitable for applications with stringent requirements for load-bearing capacity and stability, such as air circulators and high-speed rotating equipment.

[0059] The optimized pressure curves for the pressure inlet and outlet are as follows: Figure 12 As shown, the bearing 3 is under zero pressure at the beginning and end of the arc length. The pressure reaches its maximum value about 10.61 mm from the inner diameter in the middle of the arc length, with a peak pressure of 2.59 atm. As shown in Table 3, the integral value of the axial force obtained is 427.68 N, while it was 332.28 N before optimization, and the axial force is increased by about 28.7%.

[0060] Table 3

[0061] Physical pressure (N) 332.28 427.68

[0062] In this embodiment, the bearing bush 3 extends from the through hole 2 to the outer edge of the bearing body 1, and the bearing air groove 4 extends from the through hole 2 to the outer edge of the bearing body 1.

[0063] The bearing bush 3 extends radially outward from the edge of the through hole 2 in the middle of the bearing body 1 to the outer edge of the bearing body 1, forming a through structure to ensure that it can participate in the formation and transmission of gas pressure throughout the entire radial range. The bearing gas groove 4 between adjacent bearing bushes 3 also extends radially from the edge of the through hole 2 to the outer edge of the bearing body 1, maintaining the same radial extension range as the bearing bush 3. This allows gas to flow and depressurize throughout the entire range from the inner diameter to the outer diameter of the bearing. Combined with the arc-shaped pressure inlet structure of the bearing bush 3, this further optimizes the pressure distribution of gas in the radial direction of the bearing.

[0064] In some embodiments, the top of the bearing 3 is flat.

[0065] The planar design of the bearing bush 3 simplifies the surface structure, reducing the risk of local turbulence and gas film separation during gas flow. Combined with the layout of the bearing bush 3 and the bearing gas groove 4, it allows the gas to be radially accelerated and compressed on the surface of the bearing bush 3, forming a stable high-pressure gas film region. The bearing bush 3 has a pressure inlet side 6 (using a fourth-order polynomial arc design) and a pressure outlet side 5 (planar setting) along the rotation direction. The planar top and the arc structure on the inlet side work together to optimize the airflow path and enhance the dynamic pressure effect. This structure reduces manufacturing complexity through the homogenization design of the planar top. Simultaneously, combined with the gas film thickness, the mounting angle of the bearing bush 3, and the uniform distribution of the bearing bush 3, it ensures uniform gas film pressure distribution and high dynamic stability, making it suitable for applications with stringent requirements for load-bearing capacity and process adaptability, such as air circulators and high-speed rotating equipment.

[0066] In some embodiments, the top of the bearing 3 is arc-shaped.

[0067] The top of the bearing bush 3 is arc-shaped, and this arc-shaped surface smoothly connects with the arc-shaped pressure inlet side 6 and the plane of the pressure outlet side 5 of the bearing bush 3, forming a continuous gas flow channel. When the rotor drives the bearing ring to rotate at high speed, the arc-shaped structure at the top of the bearing bush 3 can guide the gas to flow smoothly along the curved surface, reducing the flow resistance of the gas on the surface of the bearing bush 3. Combined with the polynomial arc design of the pressure inlet side 6, a more uniform and stable pressure distribution is formed on the surface of the bearing bush 3. The pressure value in the middle area of ​​the bearing bush 3 is higher than the pressure value on both sides in the radial direction, which helps to improve the overall load-bearing performance of the bearing.

[0068] In this embodiment, the other side of the bearing body 1 is a flat surface.

[0069] One side of the bearing body 1 is a working surface with an alternating arrangement of bearing bush 3 and air grooves, while the other side is a flat surface. This flat surface design allows for direct contact with the external support structure or equipment housing, simplifying the installation process and enhancing structural rigidity. The flat surface on the other side reduces stress concentration during assembly, preventing localized deformation due to installation errors. Simultaneously, the planar contact improves the force transmission efficiency between the bearing body 1 and the external support surface. This design maintains the gas flow performance of the bearing bush 3 and air groove working surface while reducing manufacturing complexity and improving the overall system stability and reliability through the flat surface design on the other side.

[0070] In this embodiment, the circumferential cross-sectional length of the bearing bush 3 gradually increases from the inner side of the bearing body 1 to the outer side of the bearing body 1.

[0071] The circumferential cross-sectional length of the bearing bush 3 gradually increases from the inner side of the bearing body 1 to the outer side, with the shortest circumferential cross-sectional length at the inner side corresponding to the through hole 2 in the middle of the bearing body 1. Extending radially outward to the outer edge of the bearing body 1, the circumferential cross-sectional length of the bearing bush 3 gradually increases, forming a circumferential dimension structure with a gradient increase in the radial direction. This design, by extending the contact area of ​​the outer bearing bush 3, allows the gas to form a longer acceleration path in the radial direction when flowing on the surface of the bearing bush 3, enhancing the dynamic pressure effect and increasing the concentration of gas film pressure. Simultaneously, the height of the bearing bush 3 is higher than the gas groove, and combined with the design of the gas film thickness and installation angle, a more stable high-pressure zone is formed in the area where the cross-sectional length of the outer bearing bush 3 increases, optimizing the axial load distribution. This structure, through the gradual design of the circumferential cross-sectional length, improves gas flow efficiency, reduces the risk of gas film separation, and works synergistically with the uniform distribution of the bearing bush 3 and the gas groove, as well as the arc-shaped design of the fourth-order polynomial pressure inlet side 6, significantly improving the dynamic stability and load capacity of the bearing.

[0072] This embodiment also provides a motor, including: the axial air bearing described in the above embodiment.

[0073] This embodiment also provides an air circulator, including: the motor described in the above embodiment.

[0074] The various embodiments in this specification are described in a progressive manner, with each embodiment focusing on its differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For the apparatus disclosed in the embodiments, since it corresponds to the method disclosed in the embodiments, the description is relatively simple; relevant parts can be referred to in the method section. It should be noted that those skilled in the art can make various improvements and modifications to this utility model without departing from its principles, and these improvements and modifications also fall within the protection scope of the claims of this utility model.

[0075] It should also be noted that, in this specification, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusivity.

[0076] The term "comprises" implies that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Unless otherwise specified, an element defined by the phrase "comprises a..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

Claims

1. An axial air bearing, characterized in that, include: The bearing body has a through hole in the middle. At least one side of the bearing body is provided with a plurality of bearing bushes spaced apart circumferentially. The bearing bushes extend radially along the bearing body. A bearing air groove is formed between adjacent bearing bushes. The height of the bearing bushes is higher than the height of the bearing air grooves. The bearing bushes have a first side and a second side opposite to each other along the rotation direction. The first side of the bearing bushes is a pressure outlet side, and the second side of the bearing bushes is a pressure inlet side. The pressure inlet side of the bearing bushes is arc-shaped.

2. The axial air bearing according to claim 1, characterized in that, The pressure outlet side of the bearing bush is planar.

3. The axial air bearing according to claim 1, characterized in that, The pressure inlet side is recessed in the direction of rotation of the bearing body.

4. The axial air bearing according to claim 3, characterized in that, The arc shape on the pressure inlet side is expressed as a polynomial.

5. The axial air bearing according to claim 1, characterized in that, The bearing bush extends from the through hole to the outer edge of the bearing body, and the bearing air groove extends from the through hole to the outer edge of the bearing body.

6. The axial air bearing according to claim 1, characterized in that, The top of the bearing bush is arc-shaped.

7. The axial air bearing according to claim 1, characterized in that, The other side of the bearing body is a flat surface.

8. The axial air bearing according to claim 1, characterized in that, The circumferential cross-sectional length of the bearing bush gradually increases from the inner side of the bearing body to the outer side of the bearing body.

9. An electric motor, characterized in that, include: The axial air bearing as described in any one of claims 1-8.

10. An air circulator, characterized in that, include: The motor as described in claim 9.

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