Thrust bearings and air suspension centrifugal compressors

Abstract

The present invention discloses a thrust bearing and an air-suspended centrifugal compressor, which relate to the field of compressors and are used to optimize the structure of the thrust bearing. The thrust bearing comprises a first seat body, a second seat body and a graphite part. The first seat body comprises a first through hole. The second seat body comprises a base plate fixedly connected to the bearing base and a bearing shell connected to the base plate through a connecting portion; the base plate is provided with a second through hole connected to the first through hole; the connecting portion is constructed to enable the bearing shell to move relative to the base plate under the action of an external force. The graphite part is installed on the side of the bearing shell away from the base plate. The thrust bearing provided by the above technical solution has a connection between the bearing shell and the base plate, which can prevent the bearing shell from separating from the base plate, and also enables the bearing shell to tilt to a certain extent relative to the base plate when subjected to force during the operation of the thrust bearing, thereby enabling the damping of the thrust bearing to be adjusted to meet the requirements of the operation of the thrust bearing.

Description

Technical Field

[0001] The invention relates to the field of compressors, and in particular to a thrust bearing and an air-suspended centrifugal compressor. Background Art

[0002] A centrifugal compressor is an air-conditioning compressor that uses high-speed impeller rotation to generate centrifugal force to compress gas. Currently, the conventional types include fixed frequency, variable frequency, magnetic suspension, and air suspension centrifugal compressors. Among them, air suspension centrifugal compressors have become the future development trend of centrifugal compressors due to their simple structure, oil-free, friction-free, and low cost.

[0003] Since the centrifugal compressor is a device that compresses refrigerant, the forces on both ends of the rotor are not the same, so the rotor will inevitably move forward or backward. At this time, a thrust bearing needs to be arranged in the rotor system to balance the forward or backward force of the rotor. The force condition and working state will be directly affected by the terminal equipment, so the role of the thrust bearing is crucial.

[0004] The air suspension compressor uses gas bearings to support its rotor system. Currently, gas bearings are mainly divided into dynamic pressure gas bearings and static pressure gas bearings. The dynamic pressure gas bearing is a self-acting pressure-type flexible bearing that operates on a layer of lubricating gas film formed by itself. Its principle is the dynamic pressure principle. The static pressure gas bearing is a kind of bearing that supports the rotor system through a pressure gas film generated within a small gap range. The gas enters the gap through small holes on the surface of the bearing (laser micropores, porous holes). Since the gap (0.02-0.05mm) is small, the gas is squeezed after entering the gap, causing the pressure to increase, thereby playing a supporting role. Since the gas friction coefficient is small, the static pressure gas bearing is a basically frictionless and low-loss bearing.

[0005] Hydrostatic gas bearings are divided into single-hole throttling type, multi-hole throttling type, micro-groove throttling type, micropore throttling type, and porous material throttling type hydrostatic gas bearings according to the different throttling methods they adopt. Among them, the porous hydrostatic gas bearing uses a new type of porous material as the bearing surface. There are thousands of small holes distributed on the porous material, and its pressure distribution is uniform. It can also obtain a consistent lubricating gas film, which plays a good role in supporting the rotor.

[0006] When the porous static pressure gas bearing has both dynamic pressure and static pressure effects, when no external gas source is provided, since the general operating state of the rotor is not completely on the center line of the bearing, a wedge-shaped area will be generated between the thrust plate and the thrust bearing during the operation of the rotor, and the gas will be brought into the wedge-shaped area to form an air film. However, since the inner surface of the porous static pressure gas bearing is a graphite layer, it will inevitably rub against the bearing during the start and stop phases of the rotor. At this time, the porous surface will be severely damaged, and the bearing will mainly play a dynamic pressure effect. When an external gas source is provided, the bearing supply gas enters the porous through the pores and eventually penetrates into the gap between the bearing and the thrust plate, thereby supporting the load. At this time, the bearing mainly plays a static pressure effect. Therefore, when the entire rotor system is operating normally, the bearing actually plays both dynamic pressure and static pressure effects at the same time, and its load-bearing capacity will be better.

[0007] The inventors found that the currently commonly used porous static pressure gas bearings mostly adopt a single oil wedge structure, the gap between the thrust plate and the thrust bearing is small (0.01mm-0.02mm), and the wedge angle between the two is generally small, so the dynamic pressure effect is weak. In addition, under high-speed conditions, the gas in the bearing gap is compressed and squeezed out of the bearing rotor system, and the kinematic viscosity of the gas film is reduced, which leads to a decrease in the damping coefficient of the bearing. The damping is reduced, so the shock absorption of the bearing will be greatly reduced, and at this time, the thrust plate is easy to rub against the bearing. Summary of the invention

[0008] The present invention provides a thrust bearing and an air-suspended centrifugal compressor, which are used to optimize the structure of the thrust bearing.

[0009] An embodiment of the present invention provides a thrust bearing, comprising:

[0010] A first seat body including a first through hole;

[0011] A second seat body comprises a base plate fixedly connected to the first seat body and a bearing bush connected to the base plate via a connecting portion; the base plate is provided with a second through hole connected to the first through hole; the connecting portion is configured to enable the bearing bush to move relative to the base plate under the action of an external force; and

[0012] A graphite piece is installed on a side of the bearing shell away from the base plate.

[0013] In some embodiments, the connecting portion is elongated, located in the middle of the bearing shell along the radial direction of the substrate, and the length of the connecting portion in the radial direction of the substrate is smaller than the length of the bearing shell in the radial direction of the substrate.

[0014] In some embodiments, the connection between the connection portion and the substrate and the connection between the connection portion and the bearing bush are both smoothly transitioned.

[0015] In some embodiments, the first base is provided with a first inlet flow channel, and the second base is provided with a second inlet flow channel; the first inlet flow channel and the second inlet flow channel are connected; the first inlet flow channel and the second inlet flow channel are used together to guide the gas to the end face of the bearing facing the graphite part.

[0016] In some embodiments, the first intake flow passage comprises:

[0017] A first air inlet hole, penetrating through the thickness direction of the first base; and

[0018] An annular groove is formed on a surface of the first base facing the substrate and is communicated with the first air inlet.

[0019] In some embodiments, the second intake flow passage comprises:

[0020] A clamping ring is mounted on the base plate, and the clamping ring is located in the annular groove; the clamping ring and the annular groove together form a flow channel; and

[0021] The second air inlet hole is commonly provided on the retaining ring, the connecting portion and the bearing shell, and the second air inlet hole is connected to the end surface of the bearing shell away from the base plate.

[0022] In some embodiments, the number of the bearing shells is at least two, and the two bearing shells are dispersedly arranged along the center of the base plate.

[0023] In some embodiments, each of the bearing shells is correspondingly provided with at least one of the second air inlet holes.

[0024] In some embodiments, there is a gap between two adjacent bearing shells.

[0025] In some embodiments, a support rib is installed on the surface of the bearing shell facing away from the substrate, and the support rib is fixedly connected to the graphite part.

[0026] In some embodiments, the support ribs include a plurality of support ribs, and each of the support ribs is arranged concentrically.

[0027] In some embodiments, a surface of the bearing shell facing away from the base plate is provided with a groove, and the supporting rib is installed inside the groove.

[0028] In some embodiments, the edge of the graphite piece is chamfered.

[0029] Another embodiment of the present invention provides an air-suspended centrifugal compressor, comprising a thrust bearing provided by any technical solution of the present invention.

[0030] The thrust bearing provided by the above technical solution has a connection between the bearing shell and the base plate, which can prevent the bearing shell from separating from the base plate, and also ensure that when the bearing shell is subjected to force during the operation of the thrust bearing, it can tilt relative to the base plate to a certain extent, thereby enabling the damping of the thrust bearing to be adjusted to meet the working requirements of the thrust bearing. BRIEF DESCRIPTION OF THE DRAWINGS

[0031] 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:

[0032] Figure 1 A schematic diagram of the structure of a thrust bearing provided in an embodiment of the present invention;

[0033] Figure 2a for Figure 1 AA cross-sectional view of ;

[0034] Figure 2b for Figure 2a A local enlarged schematic diagram of N;

[0035] Figure 3 A schematic structural diagram of a first base of a thrust bearing provided in an embodiment of the present invention;

[0036] Figure 4 for Figure 3 BB cross-sectional view;

[0037] Figure 5 A schematic structural diagram of a second seat body of a thrust bearing provided in an embodiment of the present invention;

[0038] Figure 6 for Figure 5 Schematic diagram of CC cross-section;

[0039] Figure 7 for Figure 6 A local enlarged schematic diagram of D;

[0040] Figure 8 A schematic diagram of the substrate structure of the second base body provided in an embodiment of the present invention;

[0041] Fig. 9 A schematic structural diagram of a graphite component of a thrust bearing provided in an embodiment of the present invention;

[0042] Fig.10 for Fig. 9 EE cross-sectional diagram;

[0043] Fig.11 A schematic diagram of the principle of forming two layers of air films in a thrust bearing provided by an embodiment of the present invention;

[0044] Fig.12 A schematic diagram of the thrust bearing in use according to an embodiment of the present invention. DETAILED DESCRIPTION

[0045] Combine the following Figures 1 to 12 The technical solution provided by the present invention is described in more detail.

[0046] The embodiment of the present invention provides a thrust bearing 10, comprising a first seat body 1, a second seat body 2 and a graphite member 3. The first seat body 1 comprises a first through hole 12. The second seat body 2 comprises a base plate 21 fixedly connected to the first seat body 1 and a bearing bush 22 connected to the base plate 21 via a connecting portion 23; the connecting portion 23 is configured to enable the bearing bush 22 to move relative to the connection between the base plate 21 and the bearing bush 22 under the action of an external force. The graphite member 3 is mounted on a side of the bearing bush 22 away from the base plate 21.

[0047] See also Figures 1 to 4 The first base body 1 is roughly disc-shaped, and a first through hole 12 is provided in the middle of the first base body 1 , and the first through hole 12 is used to accommodate the end of the rotating shaft 6 .

[0048] See also Figure 2a and Figure 2b Specifically, the second base body 2 is fitted on one side of the first base body 1, and one side of the second base body 2 is fitted with one side of the first base body 1. The first base body 1 is provided with a first screw hole 11, and the second base body 2 is correspondingly provided with a second screw hole 26. Bolts are installed in the first screw hole 11 and the second screw hole 26 to achieve a detachable connection between the first base body 1 and the second base body 2. The first screw hole 11 and the second screw hole 26 play a locking role, and the bolt connection is easy to assemble and disassemble and has good reliability.

[0049] The specific implementation of the second seat body 2 is introduced below.

[0050] See also Figure 1 , Figure 2a , Figures 5 to 7 The base plate 21 is connected to the bearing shell 22 through a connecting portion 23 , which is located in the middle of the bearing shell 22 along the radial direction of the base plate 21 , and a length L1 of the connecting portion 23 in the radial direction of the base plate 21 is smaller than a length L2 of the bearing shell 22 in the radial direction of the base plate 21 .

[0051] The size of the connecting portion 23 is relatively small. The connecting portion 23 is used to connect the bearing 22 and the base plate 21. On the one hand, the bearing 22 and the base plate 21 are kept connected. During the operation of the thrust bearing 10, the bearing 22 will not be separated from the connecting portion 23, and the bearing 22 will not fall off. On the other hand, when the bearing 22 is subjected to the force of the gas, the bearing 22 can be tilted relative to the connecting portion 23 to a certain extent, that is, Fig.11The size of the middle wedge angle A changes, so that the structure of the first and second air films between the bearing bush 22 and the thrust plate 7 can be changed, such as Fig.11 As shown, the damping coefficient of the thrust bearing 10 is changed, so that the damping of the thrust bearing 10 can adapt to the needs of actual working conditions.

[0052] The thrust bearing 10 provided by the above technical solution has good adaptability and high damping characteristics, so the thrust bearing 10 can well solve the disadvantage of low damping of the hydrostatic thrust bearing under high speed state. In addition, since the above technical solution can increase the wedge angle A between the thrust bearing 10 and the thrust plate, the dynamic pressure effect of the hydrostatic gas thrust bearing 10 can be increased to improve the bearing capacity; and the tiltable structure of the bearing shell 22 has good adaptability and replaceability, thereby improving the speed operating range of the porous hydrostatic gas bearing and the reliability of the hydrostatic gas bearing. The direct stiffness coefficient of the bearing increases with the increase of the speed, and it is difficult to change its stiffness under high speed state. In actual operation, as the speed changes, the bearing stiffness required by the rotor system changes, and generally increases with the increase of the speed, especially when a variable frequency motor is used and the speed needs to be changed frequently. The thrust bearing 10 with a multi-oil wedge structure will adapt well to the working conditions. The specific reason is: due to the adaptability of the inclination angle of the bearing shell 22, the wedge angle between the thrust bearing 10 and the thrust plate 7 will also increase. At this time, the dynamic pressure effect will be enhanced, thereby improving the bearing capacity of the thrust bearing 10.

[0053] like Figure 7 As shown, the connection between the connection part 23 and the base plate 21 and the bearing bush 22 is smoothly transitioned. The bearing bush 22 and the base plate 21 are connected by the connection part 23, and the connection part 23 is designed with rounded corners, which can well reduce stress concentration and prevent fracture.

[0054] See also Figure 1 and Figure 5 In some embodiments, the number of the bearing shells 22 is at least two, and the two bearing shells 22 are dispersedly arranged along the center of the base plate 21 .

[0055] Each bearing bush 22 is installed independently and does not affect each other. In some embodiments, four bearing bushes 22 are provided as an example.

[0056] The number of graphite pieces 3 is the same as that of bearing bushes 22. The graphite pieces 3 are specifically porous graphite blocks.

[0057] Each bearing bush 22 is independently mounted with a graphite piece 3. When some blocks of the graphite piece 3 are worn, the worn graphite piece 3 can be easily replaced, avoiding the disadvantage that a certain area of ​​the bearing needs to be replaced as a whole, saving raw materials and costs. The above technical solution can easily replace the graphite piece 3, so that the graphite surface of the thrust bearing 10 has good replaceability, increasing the service life of the thrust bearing 10 and saving costs.

[0058] See also Fig. 9 In some embodiments, the edge of the graphite piece 3 is provided with a chamfer 31. The graphite piece 3 is designed with a chamfer 31, which forms a sealant-proof area with the groove 25, thereby making the sealant have a good fixing and sealing effect.

[0059] In some embodiments, each bearing bush 22 is correspondingly provided with at least one second air inlet hole 52. The second air inlet hole 52 guides the gas in the annular groove 42 to the position where the graphite piece 3 is located.

[0060] In some embodiments, there is a gap P between two adjacent bearing shells 22. The gap P makes the structures of the bearing shells 22 independent and does not affect the inclination angle of each other.

[0061] See also Figure 5 In some embodiments, a support rib 24 is installed on the surface of the bearing bush 22 away from the base plate 21, and the support rib 24 is fixedly connected to the graphite member 3. Figure 5 As shown, there are a plurality of support ribs 24, each support rib 24 being spaced a certain distance apart. The support ribs 24 connect the bearing bush 22 and the graphite member 3 together.

[0062] Since the thrust bearing 10 includes a plurality of graphite pieces 3, each graphite piece 3 is not a whole structure, but is separate and independent. When friction occurs to the graphite piece 3, only the worn graphite piece 3 is replaced, and other graphite pieces 3 do not need to be replaced. Therefore, the manufacturing cost and material waste are greatly reduced.

[0063] See also Figure 5 In some embodiments, a groove 25 is provided on the surface of the bearing bush 22 facing away from the substrate 21, and the support rib 24 is installed inside the groove 25. The support rib 24 does not affect the continuity of the concave area of ​​the groove 25, and each area of ​​each groove 25 is still connected. The support rib 24 is mainly used to support the graphite part 3 to prevent it from breaking when subjected to a large load. The groove 25 is mainly used to stick the graphite part 3 to the bearing bush 22, and to allow the gas to enter the graphite part 3 evenly.

[0064] In some embodiments, the support ribs 24 include a plurality of support ribs 24, and each support rib 24 is arranged concentrically. This structure makes the structure of the thrust bearing 10 more balanced.

[0065] The following describes how to implement the intake air duct.

[0066] See also Figures 3 to 8 In some embodiments, the first seat body 1 is provided with a first inlet flow channel 4, and the second seat body 2 is provided with a second inlet flow channel 5; the first inlet flow channel 4 and the second inlet flow channel 5 are connected; the first inlet flow channel 4 and the second inlet flow channel 5 are used together to guide the gas to the end surface of the bearing bush 22 facing the graphite member 3. Then the gas penetrates through the graphite member 3 to Fig.11 The space indicated by the first layer of air membrane.

[0067] like Figure 1 and Figure 5 As shown, there is a gap between two adjacent bearing bushes 22, and each bearing bush 22 is installed independently. A graphite part 3 is installed on each bearing bush 22. The gap between each bearing bush 22 and the substrate 21 is connected to the cavity where the second through hole 27 is located. Therefore, the gas that penetrates into the first layer of air film will also penetrate into the space where the bearing bush 22 and the substrate 21 are located, that is, the area where the second layer of air film is located. From then on, a layer of air film is formed on both sides of the bearing bush 22 of the thrust bearing 10, and two layers of air film are formed as a whole.

[0068] The porous static pressure gas thrust bearing 10 provided by the above technical solution has good adaptability and can well adapt to the changes in rotor force of the compressor under different working conditions. Specifically, under high speed conditions, the bearing 22 can adjust the tilt angle adaptively according to the force conditions, and the outer surface of the bearing 22 (that is, the surface of the bearing 22 facing the substrate 21) and the inner surface of the substrate 21 form a first air film. A second air film is formed between the inner surface of the bearing 22 (that is, the surface of the bearing 22 facing the shaft 6) and the shaft diameter of the shaft 6. The double-layer air film can dissipate a certain amount of vibration energy. In addition, the thrust bearing 10 provided by the above technical solution also has a certain shock absorption property, which can well solve the phenomenon of decreased bearing damping under high speed conditions.

[0069] The thrust bearing 10 provided by the above technical solution has better damping properties because it can form a double-layer air film. Under conditions of high speed, it can provide additional high damping to the bearing, greatly improving the stability and adaptability of the bearing. Since the bearing shell is tiltable, during actual operation, the wedge angle between the thrust bearing 10 and the thrust plate 7 will increase, and the dynamic pressure effect will be enhanced.

[0070] See also Figure 1 , Figure 2a as well as Figure 8 The first inlet channel 4 includes a first inlet hole 41 and an annular groove 42. The first inlet hole 41 penetrates the thickness direction of the first base body 1. The annular groove 42 is formed on the surface of the first base body 1 facing the substrate 21 and communicates with the first inlet hole 41.

[0071] The number of the first air supply hole 41 is, for example, one, and the first air supply hole 41 is used to pass external bearing gas into the thrust bearing 10 .

[0072] The annular groove 42 is mainly used to evenly distribute the external gas to the four second air supply holes 52, and then enter the groove 25, and then fill the entire groove 25 through the through groove opened on the groove 25, and finally penetrate from the graphite part 3 into the gap between the thrust bearing 10 and the thrust plate to form an air film to bear the load.

[0073] The external airflow enters the annular groove 42 through the first air inlet hole 41; then enters each second air inlet flow channel 5 from the annular groove 42. The gas enters the area where each bearing 22 is located along the second air inlet flow channel 5 to form the two layers of air film described above. The annular groove 42 can avoid setting too many flow channels on the base plate 21, reduce the impact of setting too many flow channels on the overall structure of the base plate 21, reduce the complexity of the structure of the base plate 21, and reduce the defects caused by the need to open the same number of air supply holes on the entire compressor due to the opening of multiple air supply holes on the first base body 1.

[0074] See also Figures 2a to 4 , Figure 6 The second inlet flow channel 5 includes a snap ring 51 and a second air inlet hole 52. The snap ring 51 is mounted on the substrate 21, and the snap ring 51 is located in the annular groove 42. The snap ring 51 and the annular groove 42 together form a flow channel, and this structure is well sealed to prevent gas leakage. The snap ring 51, the connecting portion 23 and the bearing shell 22 are jointly provided with a second air inlet hole 52 connected to the annular groove 42, and the second air inlet hole 52 is connected to the end surface of the bearing shell 22 away from the substrate 21.

[0075] See also Figure 2a and Figure 2b The snap ring 51 protrudes from the surface of the base plate 21 for fitting with the first seat body 1, and the snap ring 51 is located in the annular groove 42. The snap ring 51 does not contact the bottom of the annular groove 42, and there is a certain distance between the snap ring 51 and the annular groove 42, which enables the snap ring 51 and the annular groove 42 to form a gas delivery channel M together, as shown in FIG. Figure 2b As shown, the possibility of gas leakage in the annular groove 42 is reduced.

[0076] The first seat body 1 and the base plate 21 are connected by installing the retaining ring 51 in the annular groove 42 to circulate gas. The specific process is that the bearing supply gas enters the annular groove 42 through the first air inlet 41 of the first seat body 1, and then flows from the annular groove 42 into the supply hole 226. By designing the annular groove 42, it is possible to avoid opening multiple holes on the first seat body 1, which would cause the complexity of the compressor peripheral gas path. The graphite part 3 is attached to the groove 25 by a sealant (generally epoxy resin plastic).

[0077] The second air inlet hole 52 passes through the clamp ring 51 , the connecting portion 23 and the bearing bush 22 , so that the gas can enter the position where the graphite component 3 is located through the second air inlet hole 52 .

[0078] As described above, a plurality of bearings 22 are mounted on the second seat body 2 of the above structure, thereby forming a multi-oil wedge tiltable structure, and each bearing 22 is independently designed with a groove 25 connected to the second inlet flow channel 5. The graphite member 3 is also designed to be uniformly formed into several pieces, which are pasted inside the groove 25 by means of a sealant. After the gas enters the first seat body 1 through the first inlet hole 41 on the first seat body 1, it enters the second inlet hole 52 of the bearing 22 on the second seat body 2 through the annular groove 42 opened on the first seat body 1 and finally enters the groove 25 of the bearing 22.

[0079] As described above, the thrust bearing 10 includes four independent bearing shells 22, and each set of bearing shells 22 needs to be supplied with air separately, so it needs to have four air supply holes. The use of the annular groove 42 can allow external gas to enter the bearing shells 22 by only opening a first air inlet hole 41 on the first seat body 1, thereby avoiding increasing the complexity of the external air path.

[0080] An embodiment of the present invention further provides an air-suspended centrifugal compressor, comprising the thrust bearing 10 provided by any technical solution of the present invention.

[0081] In the description of the present invention, it is necessary to understand that the terms "center", "longitudinal", "lateral", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside" and the like indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore cannot be understood as a limitation on the protection content of the present invention.

[0082] Finally, it should be noted that the above embodiments are only used to illustrate the technical solutions of the present invention, rather than to limit it. Although the present invention has been described in detail with reference to the aforementioned embodiments, those skilled in the art should understand that they can still modify the technical solutions described in the aforementioned embodiments, or make equivalent replacements for some of the technical features therein, but these modifications or replacements do not make the essence of the corresponding technical solutions deviate from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A thrust bearing, characterized in that: include: A first seat body (1) comprising a first through hole (12); The second seat body (2) comprises a base plate (21) fixedly connected to the first seat body (1) and a bearing bush (22) connected to the base plate (21) via a connecting portion (23); the base plate (21) is provided with a second through hole (27) connected to the first through hole (12); the connecting portion (23) is configured to enable the bearing bush (22) to move relative to the base plate (21) under the action of an external force; as well as A graphite member (3) mounted on a side of the bearing bush (22) away from the base plate (21); Wherein, the first seat body (1) is provided with a first intake air passage (4), and the second seat body (2) is provided with a second intake air passage (5); The first inlet flow channel (4) comprises an annular groove (42), and the annular groove (42) is formed on a surface of the first seat body (1) facing the substrate (21); The second inlet flow passage (5) comprises: a clamping ring (51) mounted on the base plate (21), and the clamping ring (51) is located in the annular groove (42); the clamping ring (51) and the annular groove (42) together form a flow channel; and A second air inlet hole (52), wherein the retaining ring (51), the connecting portion (23) and the bearing shell (22) are jointly provided with the second air inlet hole (52) which is connected to the annular groove (42), and the second air inlet hole (52) is connected to the end surface of the bearing shell (22) facing away from the base plate (21).

2. The thrust bearing according to claim 1, characterized in that: The connecting portion (23) is elongated, the connecting portion (23) is located in the middle of the bearing shell (22) along the radial direction of the base plate (21), and the length of the connecting portion (23) in the radial direction of the base plate (21) is smaller than the length of the bearing shell (22) in the radial direction of the base plate (21).

3. The thrust bearing according to claim 2, characterized in that: The connection between the connection portion (23) and the base plate (21) and the connection between the connection portion (23) and the bearing bush (22) are both smoothly transitioned.

4. The thrust bearing according to claim 2, characterized in that: The first intake flow channel (4) and the second intake flow channel (5) are connected; the first intake flow channel (4) and the second intake flow channel (5) are used together to guide the gas to the end surface of the bearing bush (22) facing the graphite part (3).

5. The thrust bearing according to claim 4, characterized in that: The first intake flow passage (4) further comprises: A first air inlet hole (41) extending through the thickness direction of the first seat body (1); The annular groove (42) is in communication with the first air inlet hole (41).

6. The thrust bearing according to claim 1, characterized in that: The number of the bearing bushes (22) is at least two, and the two bearing bushes (22) are dispersedly arranged along the center of the base plate (21).

7. The thrust bearing according to claim 6, characterized in that: Each of the bearing shells (22) is correspondingly provided with at least one of the second air inlet holes (52).

8. The thrust bearing according to claim 6, characterized in that: There is a gap between two adjacent bearing shells (22).

9. The thrust bearing according to claim 1, characterized in that: A support rib (24) is mounted on the surface of the bearing shell (22) facing away from the base plate (21), and the support rib (24) is fixedly connected to the graphite part (3).

10. The thrust bearing according to claim 9, characterized in that: The support ribs (24) include a plurality of support ribs, and each of the support ribs (24) is arranged concentrically.

11. The thrust bearing according to claim 9, characterized in that: A groove (25) is provided on the surface of the bearing shell (22) facing away from the base plate (21), and the supporting rib (24) is installed inside the groove (25).

12. The thrust bearing according to claim 1, characterized in that The edge of the graphite piece (3) is provided with a chamfer (31).

13. An air-suspended centrifugal compressor, characterized in that: Including the thrust bearing described in any one of claims 1 to 12.

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