Gas bearings and compressors

Abstract

The present disclosure relates to a gas bearing and a compressor. The gas bearing comprises: a bearing shell (10), having an inner cavity extending in an axial direction, the inner cavity comprising at least one static pressure mounting section (11b) and at least one dynamic pressure mounting section (11a) arranged in an axial direction; at least one porous material inner sleeve (20), respectively arranged in the at least one static pressure mounting section (11b); at least one elastic material layer (30), respectively arranged in the at least one dynamic pressure mounting section (11a); and at least one top foil (40), respectively arranged on the inner side of the at least one elastic material layer (30), wherein the inner diameter d2 of the at least one porous material inner sleeve (20) is smaller than the inner diameter d1 of the at least one top foil (40). The embodiment of the present disclosure can provide good support for rotors with a larger speed range and can meet the working requirements of harsh working conditions.

Description

Technical Field

[0001] The present disclosure relates to the field of bearings, and in particular to a gas bearing and a compressor. Background Art

[0002] Gas bearings are a type of bearing that uses gas as a lubricating medium and utilizes the dynamic pressure effect or static pressure effect of the gas fluid to form a lubricating gas film that supports the load. In related technologies, gas bearings can be divided into dynamic pressure gas bearings, static pressure gas bearings, and extrusion gas bearings according to the different mechanisms of lubricating gas film generation. Gas bearings are often selected as an ideal replacement for traditional oil bearings due to their advantages such as low friction loss, good stability, and low vibration. Especially in the fields of high-speed turbines, precision machine tool manufacturing, and space technology, gas bearings have very broad application prospects. Summary of the invention

[0003] The inventors have found that both the hydrodynamic gas bearings and the hydrostatic gas bearings in the related art have certain limitations. The hydrostatic gas bearings provide gas of a certain pressure through an external gas supply system, and then the gas is transmitted to the gap between the bearing and the rotor through a throttling structure, and then an air film is formed in the matching gap between the rotor and the bearing to support the rotor. However, when the rotor speed is high, the hydrostatic gas bearing cannot effectively absorb and suppress the vibration of the rotor due to the lack of a damping mechanism, resulting in reduced bearing stability, which limits the use of hydrostatic gas bearings in high-speed and high-line speed working environments.

[0004] The hydrodynamic gas bearing uses the wedge-shaped space formed between the rotor and the bearing surface to produce a wedge effect. As the rotor speed continues to increase, the surrounding gas is continuously dragged into the wedge-shaped space due to the viscosity of the gas, causing the air pressure in the wedge-shaped space to continue to increase. The hydrodynamic gas film can only be formed when the bearing speed reaches a certain value. However, during the start-up and stop of the rotor, due to insufficient speed, an effective lubricating gas film cannot be formed between the hydrodynamic gas bearing and the rotor, resulting in severe dry friction between the top foil of the bearing and the surface of the rotor. The bearing surface gradually suffers severe wear under the action of dry friction, thereby affecting the service life of the hydrodynamic gas bearing. In the later stage of wear, there may even be severe adhesive wear between the foil and the rotor.

[0005] In addition, for hydrostatic foil bearings, under some complex and harsh working conditions, such as in aircraft air conditioning compressors and vehicle-mounted oil-free air compressors, due to the extremely large gravitational acceleration during aircraft acceleration and the impact of instantaneous huge acceleration caused by changes in road conditions during vehicle operation, a force several times or even dozens of times greater than the rotor's gravity appears between the rotor and the hydrostatic foil bearing, causing severe plastic deformation of the hydrostatic foil bearing foil, thereby changing the fit clearance between the rotor and the bearing. This will directly lead to the inability of the gas bearing to form an effective air film during operation, causing the bearing to fail.

[0006] In view of this, the embodiments of the present disclosure provide a gas bearing and a compressor, which can provide good support for a rotor in a larger speed range and can meet the working requirements of harsh working conditions.

[0007] In one aspect of the present disclosure, there is provided a gas bearing, comprising:

[0008] The bearing shell has an inner cavity extending in the axial direction, wherein the inner cavity includes at least one static pressure installation section and at least one dynamic pressure installation section arranged in the axial direction;

[0009] at least one inner sleeve made of porous material, respectively disposed in the at least one static pressure mounting section;

[0010] at least one elastic material layer, respectively disposed in the at least one dynamic pressure mounting section; and

[0011] at least one top foil, respectively arranged inside the at least one elastic material layer,

[0012] The inner diameter d2 of the at least one porous material inner sleeve is smaller than the inner diameter d1 of the at least one top foil.

[0013] In some embodiments, the at least one elastic material layer has a thickness of 1.5 to 2.5 mm.

[0014] In some embodiments, the elastic material layer includes modified ethylene-propylene rubber with a peak elastic deformation not exceeding 0.5%.

[0015] In some embodiments, the at least one top foil comprises a plurality of top foils, the at least one elastic material layer comprises a plurality of elastic material layers corresponding one to the plurality of top foils, each top foil is located inside a corresponding elastic material layer and contacts the inner surface of the corresponding elastic material layer.

[0016] In some embodiments, the free end of each top foil overlaps the inner surface of the adjacent top foil, and the angle difference θ between the overlapping position and the fixed end of the adjacent top foil is 8°-10°.

[0017] In some embodiments, the at least one static pressure mounting segment includes at least two static pressure mounting segments, a portion of the at least two static pressure mounting segments is axially located on one side of the at least one dynamic pressure mounting segment, and another portion of the at least two static pressure mounting segments is axially located on the other side of the at least one dynamic pressure mounting segment.

[0018] In some embodiments, the at least one porous material inner sleeve includes at least two porous material inner sleeves, which are respectively arranged in the at least two static pressure mounting sections, and the at least two static pressure mounting sections have the same structure and size, and the at least two porous material inner sleeves have the same structure and size.

[0019] In some embodiments, the at least one static pressure mounting segment includes two static pressure mounting segments, and the at least one dynamic pressure mounting segment includes one dynamic pressure mounting segment, and the one dynamic pressure mounting segment is axially located between the two static pressure mounting segments.

[0020] In some embodiments, the difference between the inner diameter d1 of the at least one top foil and the inner diameter d2 of the at least one porous material inner sleeve is 7-10 μm.

[0021] In some embodiments, the outer wall of the bearing shell has at least one first annular groove and an air inlet hole, each static pressure mounting section of the bearing shell has an air outlet hole, the body of the bearing shell has an air supply flow channel connecting the air inlet hole and the air outlet hole, and the at least one first annular groove is configured as an annular sealing ring fixedly mounted in the first annular groove.

[0022] In some embodiments, the outer peripheral surface of the porous material inner sleeve has a plurality of airflow grooves, the plurality of airflow grooves are arranged at intervals along the axial direction, flow openings are provided between adjacent airflow grooves, and the air supply outlet is directly opposite to at least one of the plurality of airflow grooves.

[0023] In some embodiments, a depth of at least one of the plurality of air flow grooves is 0.3-0.5 mm.

[0024] In some embodiments, the width of the through-flow opening is the same as the width of each of the plurality of air flow slots.

[0025] In some embodiments, the air supply channel is a straight channel that passes through the body of the bearing shell, the air supply channel is parallel to the axis of the bearing shell, and sealing screw plugs are provided at both ends of the air supply channel.

[0026] In one aspect of the present disclosure, a compressor is provided, comprising the aforementioned gas bearing.

[0027] Therefore, according to the embodiment of the present disclosure, the porous material inner sleeve is arranged in the static pressure installation section of the inner cavity of the bearing shell, the elastic material layer and the top foil are arranged in the dynamic pressure installation section, and the inner diameter of the porous material inner sleeve is smaller than the inner diameter of the top foil. On the one hand, the gas bearing of the embodiment of the present disclosure can realize reliable support for the rotor through the static pressure radial bearing section corresponding to the porous material inner sleeve when the rotor is at a lower speed, and can provide support with higher stiffness and damping to the rotor through the elastic material layer and the top foil when the rotor is at a higher speed, so that the gas bearing of the embodiment of the present disclosure can provide good support for the rotor in a larger speed range, improve the service life and working stability; on the other hand, the radial extrusion force and circumferential friction force between the elastic material layer and the top foil can achieve excellent stiffness and damping, so as to effectively prevent the self-excited vibration of the rotor during high-speed operation, and at the same time can significantly resist the influence of huge impact and strong gravity field, so that its reliability is significantly improved. BRIEF DESCRIPTION OF THE DRAWINGS

[0028] The accompanying drawings, which constitute a part of the specification, illustrate embodiments of the present disclosure and, together with the description, serve to explain the principles of the present disclosure.

[0029] The present disclosure may be more clearly understood from the following detailed description with reference to the accompanying drawings, in which:

[0030] Figure 1 is a schematic structural diagram of some embodiments of the gas bearing according to the present disclosure;

[0031] Figure 2 is a schematic structural diagram of some embodiments of the gas bearing according to the present disclosure from an axial perspective;

[0032] Figure 3 yes Figure 2 AA cross-section diagram of ;

[0033] Figure 4 is a schematic longitudinal cross-sectional view of an exploded structure along the axial direction of some embodiments of the gas bearing disclosed herein;

[0034] Figure 5 yes Figure 2 An enlarged schematic diagram of the middle circle B;

[0035] Figure 6 It is a schematic diagram of the three-dimensional structure of the inner sleeve of the porous material in some embodiments of the gas bearing disclosed in the present invention.

[0036] It should be understood that the size of each part shown in the accompanying drawings is not drawn according to the actual proportional relationship. In addition, the same or similar reference numerals represent the same or similar components. DETAILED DESCRIPTION

[0037] Various exemplary embodiments of the present disclosure will now be described in detail with reference to the accompanying drawings. The description of the exemplary embodiments is merely illustrative and is in no way intended to limit the present disclosure and its application or use. The present disclosure can be implemented in many different forms and is not limited to the embodiments described herein. These embodiments are provided to make the present disclosure thorough and complete and to fully express the scope of the present disclosure to those skilled in the art. It should be noted that unless otherwise specifically stated, the relative arrangement of the components and steps, the composition of the materials, the numerical expressions and the numerical values ​​set forth in these embodiments should be interpreted as being merely exemplary and not as limiting.

[0038] The words "first", "second" and similar words used in this disclosure do not indicate any order, quantity or importance, but are only used to distinguish different parts. The words "include" or "comprise" and similar words mean that the elements before the word include the elements listed after the word, and do not exclude the possibility of including other elements. "Up", "down", "left", "right" and the like are only used to indicate relative positional relationships. When the absolute position of the described object changes, the relative positional relationship may also change accordingly.

[0039] In the present disclosure, when a specific device is described as being located between a first device and a second device, there may or may not be an intermediate device between the specific device and the first device or the second device. When a specific device is described as being connected to other devices, the specific device may be directly connected to the other device without an intermediate device, or may not be directly connected to the other device but have an intermediate device.

[0040] All terms (including technical terms or scientific terms) used in the present disclosure have the same meanings as those understood by ordinary technicians in the field to which the present disclosure belongs, unless otherwise specifically defined. It should also be understood that terms defined in general dictionaries, such as general dictionaries, should be interpreted as having meanings consistent with their meanings in the context of the relevant technology, and should not be interpreted in an idealized or extremely formal sense, unless explicitly defined herein.

[0041] Technologies, methods, and equipment known to ordinary technicians in the relevant art may not be discussed in detail, but where appropriate, the technologies, methods, and equipment should be considered as part of the specification.

[0042] Figure 1 Schematic diagram of the structure of some embodiments of the gas bearing according to the present disclosure. Figure 2 It is a schematic structural diagram of some embodiments of the gas bearing according to the present disclosure from an axial perspective. Figure 3 yes Figure 2 Schematic diagram of the AA section. Figure 4 1 is a schematic longitudinal cross-sectional view of an exploded structure of some embodiments of a gas bearing according to the present disclosure along the axial direction. Figure 5 yes Figure 2 Enlarged schematic diagram of the middle circle B.

[0043] refer to Figure 1-Figure 5 In some embodiments, the gas bearing comprises: a bearing shell 10, at least one porous material inner sleeve 20, at least one elastic material layer 30 and at least one top foil 40. The bearing shell 10 has an inner cavity extending in the axial direction, and the inner cavity comprises at least one static pressure installation section 11b and at least one dynamic pressure installation section 11a arranged in the axial direction.

[0044] At least one porous material inner sleeve 20 is respectively arranged in the at least one static pressure installation section 11b. At least one elastic material layer 30 is respectively arranged in the at least one dynamic pressure installation section 11a. At least one top foil 40 is respectively arranged inside the at least one elastic material layer 30.

[0045] This embodiment achieves excellent stiffness and damping through the radial squeezing force and circumferential friction force between the elastic material layer and the top foil, thereby effectively preventing the self-excited vibration of the rotor during high-speed operation, and at the same time being able to significantly resist the influence of huge impacts and strong gravity fields, thereby significantly improving its reliability. Compared with the risk of permanent plastic deformation and failure of the corrugated foil used in the related art under huge impacts or strong gravity fields, this embodiment only undergoes elastic deformation even if it is subjected to huge impacts or works under strong gravity fields during operation, thereby greatly improving the working stability.

[0046] refer to Figure 3 , the inner diameter d2 of the at least one porous material inner sleeve 20 is smaller than the inner diameter d1 of the at least one top foil 40. This design enables the porous material inner sleeve to support the rotor in the low-speed stage of the rotor, so that the rotor can float smoothly in the low-speed stage. Compared with the hydrodynamic radial bearing in the related art, it can avoid the serious dry friction between the hydrodynamic radial bearing section and the rotor surface in the low-speed stage of the rotor. In addition, the matching structure of the elastic material layer and the top foil can support the rotor with higher rigidity and damping in the high-speed stage of the rotor. Compared with the hydrostatic radial bearing in the related art, it can avoid the stability problem of the hydrostatic radial bearing section in the high-speed stage of the rotor. In this way, the rotor can be further suspended in the full speed range of operation, thereby greatly extending the service life of the gas bearing and the stable reliability of operation.

[0047] In other words, by setting the inner diameter d2 of the porous material inner sleeve 30 to be smaller than the inner diameter d1 of the top foil 40, the action sequence of the hydrostatic radial bearing section corresponding to the porous material inner sleeve and the dynamic radial bearing section corresponding to the top foil under different rotor speeds can be achieved, thereby fully utilizing the performances of the dynamic radial bearing and the hydrostatic radial bearing under different rotor speed conditions, and better compensating for the respective shortcomings of the hydrostatic radial bearing and the hydrostatic radial bearing in the related technologies.

[0048] In some embodiments, at least one static pressure installation section 11b includes at least two static pressure installation sections 11b. A portion of the at least two static pressure installation sections 11b is axially located on one side of the at least one dynamic pressure installation section 11a, and another portion of the at least two static pressure installation sections 11b is axially located on the other side of the at least one dynamic pressure installation section 11a. This arrangement facilitates the assembly of the elastic material layer, the top foil, and the porous material inner sleeve in the inner cavity of the bearing shell, reduces the difficulty of assembly, and easily ensures the bearing accuracy.

[0049] It should be noted that two adjacent dynamic pressure foil groups can also be regarded as a dynamic pressure foil group that is longer in the axial direction, and two adjacent porous material inner sleeves can also be regarded as a porous material inner sleeve that is longer in the axial direction. In this way, the above arrangement can be regarded as a gas bearing with a combination of static pressure-dynamic pressure-static pressure. In other embodiments, the gas bearing can also adopt a combination of dynamic pressure-static pressure, or a combination of dynamic pressure-static pressure-dynamic pressure, etc. The gas bearing in this embodiment based on the static pressure-dynamic pressure-static pressure combination of the integrated bearing shell is easier to assemble, has a more compact structure, and is easier to ensure precision.

[0050] refer to Figure 3 and Figure 4 In some embodiments, the at least one porous material inner sleeve 30 includes at least two porous material inner sleeves 30, which are respectively arranged in the at least two static pressure installation sections 11b. The at least two static pressure installation sections 11b have the same structure and size, and the at least two porous material inner sleeves 30 have the same structure and size. This structure can balance the force of the gas bearing to obtain better working stability.

[0051] exist Figure 3 and Figure 4 In the embodiment, the at least one static pressure mounting section 11b includes two static pressure mounting sections 11b, and the at least one dynamic pressure mounting section 11a includes one dynamic pressure mounting section 11a, and the one dynamic pressure mounting section 11a is axially located between the two static pressure mounting sections 11b. The structure of this gas bearing has high working stability, and the small number of sections can simplify assembly. In addition, the small number of sections of this gas bearing makes the overall axial width relatively small, so that it is easier to ensure assembly accuracy and is not easy to be worn.

[0052] In the above embodiment, the difference between the inner diameter d1 of at least one top foil 40 and the inner diameter d2 of the at least one porous material inner sleeve 30 is preferably 7-10 μm. This value range enables the dynamic pressure radial bearing section corresponding to the top foil to obtain a relatively suitable air film thickness, which can reduce the wear risk of the rotor and the dynamic pressure radial bearing section on the one hand, and reduce the risk of instability caused by vibration of the dynamic pressure radial bearing section when the rotor rotates at high speed on the other hand.

[0053] refer to Figure 2 and Figure 5 In some embodiments, the thickness of at least one elastic material layer 30 is 1.5 to 2.5 mm. This value range allows the dynamic pressure radial bearing segment to obtain a suitable air film thickness, which can provide a good buffering effect and reduce the difficulty of processing, and control the deformation through a suitable thickness to meet the bearing load capacity requirements.

[0054] from Figure 5 As can be seen in the figure, the elastic material layer 30 can be fixed on the inner wall of the bearing shell 10 by the adhesive layer 33. The material of the elastic material layer 30 may include a polymer elastic material, such as modified ethylene propylene rubber with a peak elastic deformation of no more than 0.5%, so as to meet the requirements of excellent elasticity while also meeting the requirements of hardness and deformation.

[0055] In some embodiments, the at least one top foil 40 includes a plurality of top foils 40, and the at least one elastic material layer 30 includes a plurality of elastic material layers 30 corresponding to the plurality of top foils 40. Each top foil 40 is located inside the corresponding elastic material layer 30 and contacts the inner surface of the corresponding elastic material layer 30. Figure 2 and Figure 5 In the embodiment, three top foils 40 and three elastic material layers 30 form a three-section overlapping structure. The three top foils are installed in the same direction, and the fixed ends of the top foils are inserted into the fixed wire grooves on the inner wall of the bearing shell and fixed with a fixing block. This fixing method generates self-pretensioning through the bending back tension of the top foil of the foil, so that the foils have a pretensioning effect.

[0056] refer to Figure 5 In some embodiments, the free end of each top foil overlaps the inner surface of the adjacent top foil, and the angle difference θ between the overlap position and the fixed end of the adjacent top foil is 8° to 10°. Figure 5 In the embodiment, the plurality of elastic material layers 30 include a first elastic material layer 31 and a second elastic material layer 32. The plurality of top foils 40 include a first top foil 41 and a second top foil 42.

[0057] The first elastic material layer 31 and the second elastic material layer 32 are adjacent in the circumferential direction, and the corresponding first top foil 41 and the second top foil 42 are also adjacent in the circumferential direction. The fixed end 42b of the second top foil 42 is inserted into the fixed wire groove of the inner wall of the bearing shell and fixed by the fixing block 43, and the free end extends in the counterclockwise circumferential direction. The free end of the first top foil 41 also extends in the counterclockwise circumferential direction and overlaps the inner surface of the second top foil 42. The angle difference θ of the overlapping position 41a relative to the fixed end 42b of the second top foil 42 is 8° to 10°. This angle difference is conducive to the formation of a wedge-shaped air film and also minimizes or avoids excessive wear of the free end of the top foil.

[0058] refer to Figure 3 and Figure 4 In some embodiments, the outer wall of the bearing housing 10 has at least one first annular groove 12 and an air supply inlet 13, each static pressure mounting section 11b of the bearing housing 10 has an air supply outlet 15, the body of the bearing housing 10 has an air supply flow passage 14 connecting the air supply inlet 13 and the air supply outlet 15, and the at least one first annular groove 12 is configured as an annular sealing ring fixedly sleeved in the first annular groove 12. These first annular grooves 12 can increase the damping of the gas bearing and can play an airtight role through the annular sealing ring. In some embodiments, the material of the bearing housing 10 includes a relatively lightweight aluminum alloy material.

[0059] The porous material inner sleeve 20 is located radially inside the static pressure installation section 11b of the bearing housing 10. An external gas source can pass high-pressure gas from the outside of the bearing housing 10 to the outside of the porous material inner sleeve 20 through the gas supply inlet hole 13 via the gas supply flow channel 14 and the gas supply outlet hole 15, and the gas film is uniformly applied to the rotor inside the porous material inner sleeve 20 through the porous material. In some embodiments, the porous material includes porous graphite.

[0060] exist Figure 3 and Figure 4 In the embodiment, the air supply passage 14 is a straight passage that penetrates the body of the bearing housing 10, the air supply passage 14 is parallel to the axis of the bearing housing 10, and sealing screw plugs 16 are provided at both ends of the air supply passage 14. The air passage structure of the bearing housing 10 is easier to process and form.

[0061] The at least one first annular groove 12 includes a plurality of first annular grooves 12 spaced apart in the axial direction. A portion and another portion of the plurality of first annular grooves 12 are respectively located on both sides of the gas supply inlet hole 13 in the axial direction. For example, two first annular grooves 12 may be respectively located on both sides of the gas supply inlet hole 13 in the axial direction of the gas bearing, which improves the airtight effect and also makes the damping of the gas bearing consistent in the axial direction.

[0062] Figure 6Schematic diagram of the three-dimensional structure of the porous material inner sleeve in some embodiments of the gas bearing disclosed in the present invention. Figure 4 and Figure 6 In some embodiments, the outer circumferential surface of the porous material inner sleeve 20 has a plurality of airflow grooves 21, the plurality of airflow grooves 21 are arranged at intervals along the axial direction, a flow opening 22 is provided between adjacent airflow grooves 21, and the air supply outlet 15 faces at least one of the plurality of airflow grooves 21. The airflow grooves 21 can form a plurality of airflow channels with the bearing housing 10, so that the high-pressure gas can be uniformly discharged along the inner surface of the porous material inner sleeve 20, thereby providing a more uniform support for the rotor.

[0063] exist Figure 6 In the embodiment, the width of the through-flow opening 22 is the same as the width of each of the plurality of air flow grooves 21, so that the high pressure gas is more evenly distributed. In addition, the depth of at least one of the plurality of air flow grooves 21 is 0.3-0.5 mm.

[0064] Any of the above-mentioned gas bearings of the present disclosure can be used in various types of equipment using rotors, such as compressors. Therefore, an embodiment of the present disclosure provides a compressor, comprising any of the above-mentioned gas bearings.

[0065] So far, various embodiments of the present disclosure have been described in detail. In order to avoid obscuring the concept of the present disclosure, some details known in the art are not described. Based on the above description, those skilled in the art can fully understand how to implement the technical solution disclosed here.

[0066] Although some specific embodiments of the present disclosure have been described in detail by way of examples, it should be understood by those skilled in the art that the above examples are for illustration only and are not intended to limit the scope of the present disclosure. It should be understood by those skilled in the art that the above embodiments may be modified or some technical features may be replaced by equivalents without departing from the scope and spirit of the present disclosure. The scope of the present disclosure is defined by the appended claims.

Claims

1. A gas bearing, It is characterized in that include: The bearing shell (10) has an inner cavity extending in the axial direction, wherein the inner cavity comprises at least one static pressure installation section (11b) and at least one dynamic pressure installation section (11a) arranged in the axial direction; At least one porous material inner sleeve (20) is respectively arranged in the at least one static pressure installation section (11b); At least one elastic material layer (30) is respectively arranged in the at least one dynamic pressure installation section (11a); and at least one top foil (40), respectively arranged inside the at least one elastic material layer (30), The inner diameter d2 of the at least one porous material inner sleeve (20) is smaller than the inner diameter d1 of the at least one top foil (40); the at least one top foil (40) comprises a plurality of top foils (40); the free end (41a) of each top foil (40) overlaps the inner surface of an adjacent top foil (40); and the angle difference θ between the overlap position of each top foil (40) and the fixed end (42b) of the adjacent top foil (40) is 8°-10°.

2. The gas bearing according to claim 1, It is characterized in that The thickness of the at least one elastic material layer (30) is 1.5-2.5 mm.

3. The gas bearing according to claim 1, It is characterized in that The material of the elastic material layer (30) includes modified ethylene-propylene rubber with a peak elastic deformation amount not exceeding 0.5%.

4. The gas bearing according to claim 1, It is characterized in that The at least one elastic material layer (30) comprises a plurality of elastic material layers (30) corresponding one-to-one to the plurality of top foils (40), each top foil (40) being located inside a corresponding elastic material layer (30) and in contact with an inner surface of the corresponding elastic material layer (30).

5. The gas bearing according to claim 1, It is characterized in that The at least one static pressure mounting section (11b) comprises at least two static pressure mounting sections (11b), a portion of the at least two static pressure mounting sections (11b) being axially located on one side of the at least one dynamic pressure mounting section (11a), and another portion of the at least two static pressure mounting sections (11b) being axially located on the other side of the at least one dynamic pressure mounting section (11a).

6. The gas bearing according to claim 1, It is characterized in that The at least one porous material inner shaft sleeve (20) comprises at least two porous material inner shaft sleeves (20), which are respectively arranged in the at least two static pressure installation sections (11b); the at least two static pressure installation sections (11b) have the same structure and size, and the at least two porous material inner shaft sleeves (20) have the same structure and size.

7. The gas bearing according to claim 1, It is characterized in that The at least one static pressure mounting section (11b) comprises two static pressure mounting sections (11b), and the at least one dynamic pressure mounting section (11a) comprises one dynamic pressure mounting section (11a), wherein the one dynamic pressure mounting section (11a) is axially located between the two static pressure mounting sections (11b).

8. The gas bearing according to claim 1, It is characterized in that The difference between the inner diameter d1 of the at least one top foil (40) and the inner diameter d2 of the at least one porous material inner sleeve (20) is 7-10 μm.

9. The gas bearing according to claim 1, It is characterized in that The outer wall of the bearing shell (10) has at least one first annular groove (12) and an air supply inlet hole (13); each static pressure mounting section (11b) of the bearing shell (10) has an air supply outlet hole (15); the body of the bearing shell (10) has an air supply flow channel (14) communicating with the air supply inlet hole (13) and the air supply outlet hole (15); and the at least one first annular groove (12) is configured as an annular sealing ring fixedly sleeved in the first annular groove (12).

10. The gas bearing according to claim 9, It is characterized in that The outer peripheral surface of the porous material inner sleeve (20) has a plurality of airflow grooves (21), the plurality of airflow grooves (21) are arranged at intervals along the axial direction, and flow openings (22) are provided between adjacent airflow grooves (21), and the air supply outlet (15) is directly opposite to at least one of the plurality of airflow grooves (21).

11. The gas bearing according to claim 10, It is characterized in that The depth of at least one of the plurality of air flow grooves (21) is 0.3-0.5 mm.

12. The gas bearing according to claim 10, It is characterized in that The width of the flow opening (22) is the same as the width of each of the plurality of air flow grooves (21).

13. The gas bearing according to claim 9, It is characterized in that The air supply channel (14) is a straight channel that penetrates the body of the bearing shell (10); the air supply channel (14) is parallel to the axis of the bearing shell (10); and sealing screw plugs (16) are provided at both ends of the air supply channel (14).

14. A compressor, It is characterized in that include: A gas bearing according to any one of claims 1 to 13.

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