Dynamic pressure gas radial bearings, compressors, air conditioners and vehicles

Abstract

The present invention discloses a dynamic pressure gas radial bearing, a compressor and a vehicle. The dynamic pressure gas radial bearing includes a shell, at least two elastic support structures and at least two corrugated foils, wherein the shell includes an axial hole with a central axis. The hole wall of the axial hole includes at least two wedge-shaped grooves arranged in sequence in the circumferential direction, and the depth of the wedge-shaped grooves gradually decreases in the rotation direction around the central axis. At least two elastic support structures are correspondingly arranged in the at least two wedge-shaped grooves. At least two corrugated foils are correspondingly installed on at least two elastic support structures. When the dynamic pressure gas radial bearing of the present invention is subjected to an impact load, the elastic support structure participates in the deformation, absorbs part of the vibration impact, avoids deformation of the high-pressure gas film area of ​​the dynamic pressure gas radial bearing, and ensures the wedge-shaped convergence area required for the operation of the dynamic pressure gas radial bearing, so as to ensure the dynamic pressure effect of the dynamic pressure gas radial bearing when subjected to an impact load.

Description

Technical Field

[0001] The invention relates to a dynamic pressure gas radial bearing, a compressor, an air conditioner and a vehicle. Background Art

[0002] Hydrogen fuel cell vehicles have the advantages of high power performance, fast hydrogen refueling, and long driving range. As a new energy vehicle, they have great development potential. Air compressors provide high-pressure gas sources for fuel cell systems. Common types include centrifugal air compressors, screw air compressors, and scroll air compressors. Compared with screw air compressors, centrifugal air compressors have higher speeds and energy efficiency, can provide high-pressure ratio gas sources, and can significantly improve the power density and overall performance of fuel cell stacks.

[0003] Foil dynamic pressure gas radial bearing is a kind of dynamic pressure sliding bearing. It has the advantages of low friction loss, high speed, good high temperature stability, and no need for lubricating oil. It is very suitable for use in high-speed centrifugal air compressors. Summary of the invention

[0004] The inventors have discovered that the foil dynamic pressure gas radial bearing in the prior art cannot support the rotor when subjected to impact loads. To address this problem, the present invention provides a dynamic pressure gas radial bearing, a compressor, an air conditioner and a vehicle to enhance the dynamic pressure effect of the dynamic pressure gas radial bearing when subjected to impact loads.

[0005] A first aspect of the present invention provides a dynamic pressure gas radial bearing, comprising:

[0006] The housing comprises an axial hole having a central axis, wherein a hole wall of the axial hole comprises at least two wedge-shaped grooves arranged sequentially in a circumferential direction, and the depth of the wedge-shaped grooves gradually decreases in a rotation direction around the central axis;

[0007] At least two elastic support structures are correspondingly arranged in the at least two wedge-shaped grooves; and

[0008] At least two corrugated foils are correspondingly mounted on at least two elastic supporting structures.

[0009] In some embodiments, the stiffness of the elastic support structure is greater than the stiffness of the bump foil.

[0010] In some embodiments, the elastic support structure is a wedge-shaped structure, the bottom surface of the elastic support structure fits with the bottom surface of the wedge-shaped groove, and the thickness of the elastic support structure is the same as the depth of the wedge-shaped groove, so that in the rotation direction around the central axis, the distance between the top surface of the elastic support structure and the central axis remains unchanged.

[0011] In some embodiments, the elastic support structure includes a first end and a second end in a rotation direction around a central axis, the thickness of the first end is greater than the thickness of the second end, and the difference between the thickness of the first end and the thickness of the second end is in the range of [0.05mm, 0.2mm].

[0012] In some embodiments, the resilient support structure comprises rubber.

[0013] In some embodiments, the dynamic pressure gas radial bearing includes three elastic support structures and three corrugated foils, the hole wall of the shaft hole includes three wedge-shaped grooves, the three elastic support structures are correspondingly arranged in the three wedge-shaped grooves, and the three corrugated foils are correspondingly arranged on the three elastic support structures.

[0014] In some embodiments, the dynamic pressure gas radial bearing further comprises a top foil, which extends in the circumferential direction, and one end of the top foil is fixedly arranged on the shell, and the other end of the top foil is freely arranged, and the top foil overlaps the top surface of the corrugated foil.

[0015] A second aspect of the present invention provides a compressor, comprising a rotor and the above-mentioned dynamic pressure gas radial bearing, wherein the dynamic pressure gas radial bearing is used to support the rotor.

[0016] A third aspect of the present invention provides an air conditioner, comprising the above-mentioned compressor.

[0017] A fourth aspect of the present invention provides a vehicle comprising the above-mentioned compressor.

[0018] Based on the various aspects provided by the present invention, the dynamic pressure gas radial bearing includes a shell, at least two elastic support structures and at least two corrugated foils, wherein the shell includes an axial hole with a central axis. The hole wall of the axial hole includes at least two wedge-shaped grooves arranged in sequence in the circumferential direction, and the depth of the wedge-shaped grooves gradually decreases in the rotation direction around the central axis. At least two elastic support structures are correspondingly arranged in at least two wedge-shaped grooves. At least two corrugated foils are correspondingly installed on at least two elastic support structures. The dynamic pressure gas radial bearing of the present invention is provided with an elastic support structure between the shell and the corrugated foil. When the dynamic pressure gas radial bearing is subjected to an impact load, the elastic support structure participates in the deformation, absorbs part of the vibration shock, avoids deformation of the high-pressure gas film area of ​​the dynamic pressure gas radial bearing, and ensures the wedge-shaped convergence area required for the operation of the dynamic pressure gas radial bearing, so as to ensure the dynamic pressure effect of the dynamic pressure gas radial bearing when subjected to an impact load.

[0019] Further features and advantages of the present invention will become apparent from the following detailed description of exemplary embodiments of the present invention with reference to the attached drawings. BRIEF DESCRIPTION OF THE DRAWINGS

[0020] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of this application. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0021] Figure 1 It is a schematic structural diagram of a dynamic pressure gas radial bearing in related technology.

[0022] Figure 2 for Figure 1 Schematic diagram of the local enlarged structure of part I.

[0023] Figure 3 and Figure 4 for Figure 1 The schematic diagram of the dynamic pressure effect of a dynamic pressure gas radial bearing is shown.

[0024] Figure 5 Schematic diagram of the structure of a dynamic pressure gas radial bearing according to an embodiment of the present invention.

[0025] Figure 6 for Figure 5 Schematic diagram of the local enlarged structure of part II.

[0026] Figure 7 for Figure 5 Schematic diagram of the three-dimensional structure of the middle shell.

[0027] Figure 8 for Figure 7 A front view of the housing is shown. DETAILED DESCRIPTION

[0028] The following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the described embodiments are only part of the embodiments of the present invention, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and is by no means intended to limit the present invention and its application or use. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of the present invention.

[0029] Unless otherwise specifically stated, the relative arrangement of the parts and steps described in these embodiments, numerical expressions and numerical values ​​do not limit the scope of the present invention. At the same time, it should be understood that, for ease of description, the sizes of the various parts shown in the accompanying drawings are not drawn according to the actual proportional relationship. The technology, methods and equipment known to ordinary technicians in the relevant field may not be discussed in detail, but in appropriate cases, the technology, methods and equipment should be regarded as a part of the authorization specification. In all examples shown and discussed here, any specific value should be interpreted as being merely exemplary, rather than as a limitation. Therefore, other examples of exemplary embodiments may have different values. It should be noted that similar reference numerals and letters represent similar items in the following drawings, so once a certain item is defined in an accompanying drawing, it does not need to be further discussed in subsequent drawings.

[0030] For ease of description, spatially relative terms such as "above", "above", "on the upper surface of", "above", etc. may be used here to describe the spatial positional relationship between a device or feature and other devices or features as shown in the figure. It should be understood that spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation described in the figure. For example, if the device in the accompanying drawings is inverted, the device described as "above other devices or structures" or "above other devices or structures" will be positioned as "below other devices or structures" or "below other devices or structures". Thus, the exemplary term "above" may include both "above" and "below". The device may also be positioned in other different ways, and the spatially relative descriptions used here are interpreted accordingly.

[0031] like Figure 1 As shown, the related art dynamic pressure gas radial bearing comprises a housing 1, a top foil 3, a bump foil 4 and a fixing pin 5. The bump foil 4 is an elastic foil with a corrugated shape, one end of which is fastened to the housing 1 and the other end is freely arranged. Figure 1 The illustrated dynamic pressure gas radial bearing has multiple corrugated foils 4 on the circumference, three of which are shown in the figure. During operation, the elastic change of the corrugated shape of the corrugated foil 4 generates a supporting force, which provides the main stiffness and partial damping for the bearing. The top foil 3 is a long cylindrical foil, one end of which is fastened to the housing 1 by a fixing pin 5, and the other end is freely arranged. In addition, in the radial direction, one side of the top foil 3 is evenly overlapped on the top of each corrugation of the corrugated foil 4, and the friction force generated by the contact with the corrugated foil 4 provides another part of the damping for the bearing.

[0032] The working principle of the dynamic pressure gas radial bearing is the dynamic pressure effect, such as Figures 1 to 4 As shown, the rotor 2 is arranged in the shaft hole of the housing 1, and the rotor 2 is eccentric relative to the bearing under the action of gravity, thereby forming a Figure 1The wedge-shaped convergence area 6 and the wedge-shaped divergence area 7 are shown. When the rotor 2 rotates at a high speed along the rotation direction RD, the gas with a certain viscosity is continuously brought into the wedge-shaped convergence area 6, as shown in FIG. Figures 2 to 4 As shown in FIG. 1 , since the volume of the wedge-shaped convergence area 6 is limited and the volume becomes smaller and smaller along the rotation direction, a gas film gradient with a gradually increasing pressure value is formed in the wedge-shaped convergence area 6 along the rotation direction, as shown in FIG. Figure 2 The low-pressure air film area 8 and the high-pressure air film area 9 are shown, and the load is mainly borne by the high-pressure air film area 9. When the high-pressure air film area 9 is sufficient to balance the load of the rotor 2, the rotor 2 is completely separated from the bearing, and the process of the air film generation is called the dynamic pressure effect. On the contrary, for the wedge-shaped divergent area 7, since the volume of the wedge-shaped divergent area 7 increases along the rotation direction, the air film pressure value gradually decreases and cannot support the rotating shaft.

[0033] From the above principles and bearing structure, it can be seen that when the dynamic pressure gas radial bearing is working, a high-pressure gas film is formed by the dynamic pressure effect of the wedge-shaped convergence zone to support the rotor, so it is necessary to avoid letting the bearing work in the wedge-shaped divergence zone.

[0034] When the above-mentioned dynamic pressure gas radial bearing is used in hydrogen fuel cell vehicles, the following problems will occur. When the car is driving on an uneven road, it will vibrate violently. At this time, the dynamic pressure gas radial bearing is simultaneously subjected to impact loads. The air film pressure of the high-pressure air film area 9 itself is greater than the air film pressure of the low-pressure air film area 8. Therefore, the radial deformation of the waveform of the corrugated foil 4 corresponding to the high-pressure air film area 9 is greater than the waveform deformation of the corrugated foil corresponding to the low-pressure air film area 8. In addition, the impact load at this time may cause a large deformation of the corrugated foil 4 corresponding to the high-pressure air film area 9, thereby causing Figure 2 The wedge-shaped gap at the medium and high pressure air film area 9 is larger than the wedge-shaped gap at the low pressure air film area 8, so the wedge-shaped convergent area 6, which was originally a convergent shape, becomes a divergent shape, and a high pressure air film cannot be formed, and the rotor cannot be supported.

[0035] In view of this, an embodiment of the present invention provides a dynamic pressure gas radial bearing to improve the dynamic pressure effect of the dynamic pressure gas radial bearing when subjected to impact load.

[0036] refer to Figures 5 to 8 In some embodiments, the hydrodynamic gas radial bearing comprises a housing 1, at least two elastic support structures 10 and at least two bump foils 4, wherein the housing 1 comprises an axial hole having a central axis. The hole wall of the axial hole comprises at least two wedge-shaped grooves 11 arranged sequentially in the circumferential direction, and the depth of the wedge-shaped grooves 11 gradually decreases in the rotation direction RD rotating around the central axis. At least two elastic support structures 10 are correspondingly arranged in at least two wedge-shaped grooves 11. At least two bump foils 4 are correspondingly mounted on at least two elastic support structures 10.

[0037] The dynamic pressure gas radial bearing is provided with an elastic support structure 10 between the shell 1 and the corrugated foil 4. When the dynamic pressure gas radial bearing is subjected to an impact load, the elastic support structure 10 participates in the deformation, absorbs part of the vibration impact, avoids the deformation of the high-pressure gas film area of ​​the dynamic pressure gas radial bearing, ensures the wedge-shaped convergence area required for the operation of the dynamic pressure gas radial bearing, and ensures the dynamic pressure effect of the dynamic pressure gas radial bearing when subjected to an impact load.

[0038] In order to make the elastic support structure 10 inoperative when the dynamic pressure gas radial bearing is in normal working state, in some embodiments, the stiffness of the elastic support structure 10 is greater than the stiffness of the corrugated foil 4. When the dynamic pressure gas radial bearing works in a non-vibration environment, for example, a vehicle equipped with the dynamic pressure gas radial bearing is driving on a flat road, the elastic support structure 10 does not work to ensure the normal operation of the dynamic pressure gas radial bearing; when the dynamic pressure gas radial bearing works in a vibration environment, for example, a vehicle equipped with the dynamic pressure gas radial bearing is driving on an uneven road, the elastic support structure 10 participates in deformation and absorbs part of the vibration impact.

[0039] Here, the depth of the wedge-shaped groove 11 mentioned in the above description is further explained. Figure 7 As shown, before the wedge-shaped groove 11 is formed, the inner surface of the shaft hole of the housing 1 is a surface of revolution A around the central axis. The depth of the wedge-shaped groove 11 mentioned here refers to the radial distance between the bottom surface of the wedge-shaped groove 11 and the surface of revolution A of the shaft hole of the housing 1. In other words, "the depth of the wedge-shaped groove 11 gradually decreases in the rotation direction RD of rotating around the central axis" can also be described as "the distance between the bottom surface of the wedge-shaped groove 11 and the central axis gradually decreases in the rotation direction RD of rotating around the central axis".

[0040] Figure 7 and Figure 8 It is exemplarily shown that three wedge-shaped grooves 11 are arranged on the inner surface of the shaft hole of the housing 1. An axial through groove is arranged on the revolving surface A between adjacent wedge-shaped grooves 11.

[0041] In some embodiments, reference Figure 6 , the elastic support structure 10 is a wedge-shaped structure. The bottom surface of the elastic support structure 10 fits with the bottom surface of the wedge-shaped groove 11, and the thickness of the elastic support structure 10 is the same as the depth of the wedge-shaped groove 11, so that in the rotation direction RD around the central axis, the distance between the top surface of the elastic support structure 10 and the central axis remains unchanged. In other words, the cross-sectional shape of the elastic support structure 10 is the same as the cross-sectional shape of the wedge-shaped groove 11, so that the elastic support structure 10 can be arranged in the wedge-shaped groove 11 in a shape-matched manner, so that the deformation capacity at the inlet of the wedge-shaped convergence zone is higher than the deformation capacity at the outlet of the wedge-shaped convergence zone. When the bearing is subjected to an impact load, the dynamic pressure effect is further enhanced, thereby increasing the air film pressure and playing a role in supporting the rotor.

[0042] The thickness of the elastic support structure 10 mentioned here refers to the distance from the top surface to the bottom surface of the elastic support structure 10 in the radial direction. Figure 5 and Figure 6 As shown, after the elastic supporting structure 10 is installed in the wedge-shaped groove 11 , the top surface of the elastic supporting structure 10 is flush with the rotation surface A.

[0043] refer to Figure 6 In some embodiments, the elastic support structure 10 includes a first end and a second end in a rotation direction RD rotating around a central axis. The thickness D1 of the first end is greater than the thickness D2 of the second end, and the difference between the thickness D1 of the first end and the thickness D2 of the second end is in the range of [0.05mm, 0.2mm]. Since D1 is greater than D2, the deformation capacity of the elastic support structure 10 at the inlet of the wedge-shaped convergence zone is higher than that at the outlet of the wedge-shaped convergence zone. Therefore, when the bearing is subjected to an impact load, the deformable amount at the inlet of the wedge-shaped convergence zone is greater, which further enhances the dynamic pressure effect of the wedge-shaped convergence zone 6, thereby increasing the air film pressure, which is equivalent to improving the ability of the bearing to support the rotor.

[0044] In some embodiments, the extension length of the elastic support structure 10 in the circumferential direction is the same as the extension length of the bump foil 4 in the circumferential direction.

[0045] In some embodiments, the elastic support structure 10 is a sheet-like part with elastic deformation capability, which is disposed between the bump foil 4 and the housing 1 to support all waveforms on the bump foil 4. Since rubber has good damping effect and can absorb vibration shock, in some embodiments, the elastic support structure 10 includes rubber.

[0046] Since the elastic support structure 10 needs to be installed on a high temperature resistant dynamic pressure gas radial bearing, the elastic support structure 10 also needs to have high temperature resistance. For example, the elastic support structure 10 can be fluororubber, nitrile rubber, etc.

[0047] In some embodiments, reference Figure 5 The dynamic pressure gas radial bearing also includes a top foil 3, which extends in the circumferential direction, and one end of the top foil 3 is fixedly set on the shell 1, and the other end of the top foil 3 is freely set, and the top foil 3 is overlapped on the top surface of the wave foil 4.

[0048] exist Figure 5 In the illustrated embodiment, the dynamic pressure gas radial bearing includes a top foil 3, which is overlapped on the top surface of three bump foils 4. In other embodiments not shown in the drawings, the dynamic pressure gas radial bearing may also include at least two top foils, which are arranged corresponding to the at least two bump foils.

[0049] In some embodiments, the present invention further provides a compressor, including a rotor 2 and the above-mentioned dynamic pressure gas radial bearing, wherein the above-mentioned dynamic pressure gas radial bearing supports the rotor 2.

[0050] An embodiment of the present invention further provides an air conditioner, comprising the above-mentioned compressor.

[0051] An embodiment of the present invention further provides a vehicle, comprising the above-mentioned compressor.

[0052] According to the following Figures 5 to 8 The structure of the dynamic pressure gas radial bearing according to a specific embodiment of the present invention is further described.

[0053] like Figure 5 and Figure 6 As shown, the dynamic pressure gas radial bearing of this embodiment includes a housing 1, a top foil 3, a wave foil 4, a fixing pin 5, a wedge-shaped convergent area 6, a wedge-shaped divergent area 7, a low-pressure air film area 8, a high-pressure air film area 9 and an elastic support structure 10.

[0054] like Figure 7 and Figure 8 As shown, the housing 1 has an axial hole. Specifically, the housing 1 is a hollow rotating part. The inner wall of the axial hole of the housing 1 includes a plurality of axial through grooves arranged in the circumferential direction, and the axial through grooves are used to assemble and fix the top foil 3 or the bump foil 4. Specifically, as Figure 7 As shown, the three first axial through grooves 12 are used to install and fix one end of the bump foil 4. The second axial through groove 13 is used to install and fix one end of the top foil 3.

[0055] And if Figure 7 and Figure 8 As shown, the inner wall of the axial hole of the housing 1 also includes a wedge-shaped groove 11 for assembling and positioning the elastic support structure 10. The elastic support structure 10 is placed in liquid nitrogen before cold assembly, and the temperature is reduced to -50°C and assembled into the wedge-shaped groove 11 of the housing 1, thereby improving the compactness of the structure of the entire bearing assembly.

[0056] like Figure 5 and Figure 6 As shown, one end of the bump foil 4 is installed in the first axial through groove 12, and the other end is freely arranged, and the bump foil 4 is arranged on the elastic support structure 10, the top foil 3 is overlapped on the top surface of the bump foil 4, and a matching gap is formed between the surface of the top foil 3 and the rotor 2, that is, Figure 5 The wedge-shaped convergence area 6 and the wedge-shaped divergence area 7 are shown. When working, the rotor 2 rotates at a high speed under the action of the electromagnetic field, continuously bringing the gas into the wedge-shaped convergence area 6 and the wedge-shaped divergence area 7, forming the following Figure 6 A high-pressure air film area 9 and a low-pressure air film area 8 are shown.

[0057] The dynamic pressure gas radial bearing of this embodiment supports the bump foil 4 by setting an elastic support structure 10 between the bump foil 4 and the shell 1. When the dynamic pressure gas radial bearing works in a large vibration environment, the elastic support structure 10 can deform to absorb the vibration impact, thereby avoiding large deformation of the bump foil 4 in the high-pressure gas film area 9, and ensuring the wedge-shaped convergence structure required for the normal operation of the dynamic pressure gas radial bearing.

[0058] In terms of deformation capacity, a better design is that the stiffness of the elastic support structure 10 is greater than the stiffness of the corrugated foil 4. The advantage of such a design is that when the dynamic pressure gas radial bearing operates in a non-vibration environment or a small vibration environment, the elastic support structure 10 basically does not participate in the deformation. At this time, the bearing operates in the designed wedge-shaped convergence zone 6 and does not deviate from the design working condition. When the gas radial bearing operates in a large vibration environment, the bearing is subjected to a large impact load, and the load reaches the deformation range of the elastic support structure 10. At this time, the elastic support structure 10 participates in the deformation. Therefore, in summary, the design in which the structural stiffness of the elastic support structure 10 is greater than the structural stiffness of the corrugated foil 4 can make the bearing work in both vibration and non-vibration environments.

[0059] Furthermore, the elastic support structure 10 of the present invention is configured as a wedge-shaped structure along the rotation direction. On the bearing housing side, the wedge-shaped structure matches the wedge-shaped groove 11; on the rotor side, the wedge-shaped structure matches the wedge-shaped convergence area 6 of the bearing; the elastic support structure 10 is structurally shown as follows: Figure 6 The thickness at the inlet of the wedge-shaped convergence zone is shown as D1, and the thickness at the outlet of the wedge-shaped convergence zone is D2. D1 should be greater than D2, and the value is generally 0.05mm≤D1-D2≤0.20mm. Since D1 is greater than D2, the deformation capacity of the elastic support structure 10 at the inlet of the wedge-shaped convergence zone is higher than that at the outlet of the wedge-shaped convergence zone. Therefore, when the bearing is subjected to an impact load, the deformation amount at the inlet of the wedge-shaped convergence zone is greater, further enhancing the dynamic pressure effect of the wedge-shaped convergence zone 6, thereby increasing the air film pressure, which is equivalent to improving the ability of the bearing to support the rotor.

[0060] To match the distribution of the corrugated foil, the elastic support structure 10 of this embodiment is also evenly distributed at multiple locations on the circumference, which are shown as three locations in the figure. Because the air film pressure of the hydrodynamic bearing in the wedge-shaped convergence area 6 is greater than the air film pressure in the wedge-shaped divergence area 7, the pressure difference will drive the bearing to vortex when working, that is, in addition to "revolving" around its own central axis, the rotor also "rotates" along the central axis of the bearing. Generally, the "rotation" speed is 0.4 to 0.5 times that of the "revolution". The "rotation" phenomenon is called rotor vortex. When the rotor vortexes, the wedge-shaped convergence area 6 and the wedge-shaped divergence area 7 also change. Therefore, evenly distributing the elastic support structure 10 at multiple locations along the circumferential direction can adapt to the vortex characteristics of the rotor.

[0061] In summary, the dynamic pressure gas radial bearing of this embodiment is provided with a wedge-shaped elastic support structure to improve the dynamic pressure effect of the bearing when subjected to impact loads. Moreover, the dynamic pressure gas radial bearing can take into account both non-vibration and vibration conditions of the vehicle.

[0062] Finally, it should be noted that the above embodiments are only used to illustrate the technical solution of the present invention rather than to limit it. Although the present invention has been described in detail with reference to the preferred embodiments, ordinary technicians in the field should understand that the specific implementation methods of the present invention can still be modified or some technical features can be replaced by equivalents without departing from the spirit of the technical solution of the present invention, which should be included in the scope of the technical solution for protection of the present invention.

Claims

1. A dynamic pressure gas radial bearing, characterized in that: include: A housing (1) comprises an axial hole having a central axis, wherein a hole wall of the axial hole comprises at least two wedge-shaped grooves (11) arranged sequentially in a circumferential direction, and in a rotation direction (RD) around the central axis, the depth of the wedge-shaped grooves (11) gradually decreases; At least two elastic support structures (10) are arranged correspondingly in the at least two wedge-shaped grooves (11), the elastic support structures (10) are wedge-shaped structures, the bottom surface of the elastic support structure (10) is in contact with the bottom surface of the wedge-shaped groove (11), and the thickness of the elastic support structure (10) is the same as the depth of the wedge-shaped groove (11); and At least two corrugated foils (4) are mounted on the at least two elastic supporting structures (10) respectively.

2. The dynamic pressure gas radial bearing according to claim 1, characterized in that: The rigidity of the elastic support structure (10) is greater than the rigidity of the corrugated foil (4).

3. The dynamic pressure gas radial bearing according to claim 1, characterized in that: In the rotation direction (RD) around the central axis, the distance between the top surface of the elastic support structure (10) and the central axis remains unchanged.

4. The dynamic pressure gas radial bearing according to claim 3, characterized in that: The elastic support structure (10) comprises a first end and a second end in a rotation direction around the central axis, the thickness of the first end is greater than the thickness of the second end, and the difference between the thickness of the first end and the thickness of the second end is in the range of [0.05 mm, 0.2 mm].

5. The dynamic pressure gas radial bearing according to claim 1, characterized in that: The elastic supporting structure (10) comprises rubber.

6. The dynamic pressure gas radial bearing according to claim 1, characterized in that: The dynamic pressure gas radial bearing includes three elastic support structures and three corrugated foils, the hole wall of the axial hole includes three wedge-shaped grooves, the three elastic support structures are correspondingly arranged in the three wedge-shaped grooves, and the three corrugated foils are correspondingly arranged on the three elastic support structures.

7. The dynamic pressure gas radial bearing according to any one of claims 1 to 6, characterized in that: The dynamic pressure gas radial bearing further comprises a top foil (3), the top foil (3) extending in the circumferential direction, one end of the top foil (3) being fixedly arranged on the housing (1), the other end of the top foil (3) being freely arranged, and the top foil (3) being overlapped on the top surface of the corrugated foil (4).

8. A compressor, comprising a rotor (2) and a dynamic pressure gas radial bearing supporting the rotor (2), characterized in that: The dynamic pressure gas radial bearing is a dynamic pressure gas radial bearing according to any one of claims 1 to 7, and when the compressor is running, the rotor (2) rotates along the rotation direction (RD).

9. An air conditioner, characterized in that: Comprising the compressor of claim 8.

10. A vehicle, characterized in that: Comprising the compressor of claim 8.

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