CN113090658A

CN113090658A - Radial bearing and air suspension centrifugal compressor

Info

Publication number: CN113090658A
Application number: CN202010022427.7A
Authority: CN
Inventors: 张治平; 刘华; 陈玉辉; 钟瑞兴; 刘胜
Original assignee: Gree Electric Appliances Inc of Zhuhai
Current assignee: Gree Electric Appliances Inc of Zhuhai
Priority date: 2020-01-09
Filing date: 2020-01-09
Publication date: 2021-07-09

Abstract

The invention discloses a radial bearing and an air suspension centrifugal compressor, relates to the field of compressors, and aims to optimize the structure of the radial bearing. The radial bearing comprises a bearing sleeve, a bearing base and a graphite piece. The bearing sleeve includes a through bore. The bearing base comprises a cylinder body arranged on the inner wall of the through hole and a bearing bush connected with the cylinder body through a connecting part; the connecting part is configured to enable the bearing bush to move relative to the connecting part of the cylinder and the bearing bush under the action of external force. The graphite piece is arranged on one side of the bearing bush far away from the cylinder body. According to the radial bearing provided by the technical scheme, the bearing bush can not be separated from the substrate due to the connection between the bearing bush and the substrate, and a certain inclination can be generated relative to the substrate when the bearing bush is stressed in the working process of the radial bearing, so that the damping of the radial bearing can be adjusted to meet the working requirement of the radial bearing.

Description

Radial bearing and air suspension centrifugal compressor

Technical Field

The invention relates to the field of compressors, in particular to a radial bearing and an air suspension centrifugal compressor.

Background

The static pressure gas bearing supports a rotor system through a pressure gas film between a bearing and a rotor, wherein gas enters a gap between the bearing and the rotor through small holes (laser micropores and porous holes) on the surface of the bearing, and the pressure is increased due to the fact that the gap (0.02-0.05mm) between the rotor and the bearing is small, and the gas is extruded after entering the gap, so that the rotor is supported. Because the gas friction coefficient is small, the static pressure gas bearing is a bearing basically without friction and with small loss.

The static pressure gas bearing is divided into a single-small-hole throttling type, a multi-small-hole throttling type, a micro-groove throttling type, a micropore throttling type and a porous material throttling type by adopting different throttling modes, wherein the porous static pressure gas bearing utilizes a novel porous material as a bearing surface, thousands of small holes are distributed on the porous material, the pressure distribution is uniform, a lubricating gas film with good consistency can be obtained, and a good rotor supporting effect is achieved.

The porous static pressure gas bearing has both dynamic pressure and static pressure effects, when no external gas source is provided, because the rotor is generally arranged in an eccentric mode, a wedge-shaped area is generated between the rotor and the bearing in the running process of the rotor, and therefore gas is brought into the wedge-shaped area to form a gas film. However, since the inner surface of the bearing of the porous static pressure gas bearing is a graphite layer, the bearing inevitably rubs against the bearing in the start-stop stage of the rotor, and the porous surface is seriously damaged at this time, and the bearing mainly exerts a dynamic pressure effect at this time. When an external air source is provided, the bearing air supply gas enters the porous holes through the air holes and finally permeates into the gap between the bearing and the rotor, so that the load is supported, and the bearing mainly exerts a static pressure effect. Therefore, when the whole rotor system is in normal operation, the bearing actually exerts the dynamic pressure effect and the static pressure effect at the same time.

At present, a common porous static pressure gas bearing adopts a single oil wedge structure, the direct rigidity coefficients Kxx and Kyy of the bearing are increased along with the increase of the rotating speed, and the direct damping coefficients Cxx and Cyy are reduced along with the increase of the rotating speed. Because the dynamic pressure effect has a far greater influence on the dynamic characteristics of the bearing than the static pressure effect when the rotating speed is high, the higher the rotating speed is, the stronger the wedge effect and the dynamic pressure effect of the air film are, and the larger the bearing capacity of the bearing is. In this case, it is more difficult to change the thickness distribution of the gas film formed, and the bearing exhibits a greater rigidity. In addition, under the high-speed working condition, the gas in the bearing clearance is compressed and extruded out of the bearing rotor system, the kinematic viscosity of the gas film is reduced, and therefore the damping coefficient of the bearing is reduced, the damping is reduced, and therefore the damping performance of the bearing is greatly reduced. At this time, the amplitude of the rotor will increase and eventually exceed the clearance (0.02-0.05mm) between the bearing and the rotor, thereby rubbing against the bearing and destroying the bearing, which affects the life and reliability of the whole machine.

The inventor finds that the existing porous static pressure gas bearing adopts a certain number of O-shaped rings arranged on the outer diameter of the bearing to provide extra damping, however, the vibration of the rotor is intensified at high rotating speed, the extra damping provided by the porous static pressure gas bearing cannot well eliminate the vibration, and the porous surface of the whole bearing is an integral block because the traditional porous static pressure gas bearing adopts a single oil wedge design mode, when the rotor accidentally collides with the bearing in the running process, the porous surface of a certain area can be failed, but the whole porous surface needs to be replaced, so that the whole material and the cost are wasted.

Disclosure of Invention

The invention provides a radial bearing and an air suspension centrifugal compressor, which are used for optimizing the structure of the radial bearing.

An embodiment of the present invention provides a radial bearing, including:

a bearing sleeve including a through hole;

the bearing base comprises a cylinder body arranged on the inner wall of the through hole and a bearing bush connected with the cylinder body; the bearing bush is constructed to move relative to the joint of the cylinder and the bearing bush under the action of external force; and

and the graphite piece is arranged on one side of the bearing bush, which is far away from the cylinder body.

In some embodiments, the connecting portion is elongated, the connecting portion is located at a middle of the bearing bush along an axial direction of the cylinder, and a length of the connecting portion in the axial direction of the cylinder is smaller than a length of the bearing bush in the axial direction of the cylinder.

In some embodiments, the connection portions of the connection portion and the cylinder and the connection portions of the connection portion and the bearing bush are all in smooth transition.

In some embodiments, the bearing sleeve is provided with a first inlet runner and the bearing base is provided with a second inlet runner; the first intake runner and the second intake runner are in communication; the first gas inlet flow channel and the second gas inlet flow channel are jointly used for guiding gas to the end face, facing the graphite piece, of the bearing bush.

In some embodiments, the first intake runner comprises:

the first air inlet penetrates through the thickness direction of the bearing sleeve; and

the annular groove is formed in the surface, facing the barrel, of the bearing sleeve and is communicated with the first air inlet hole.

In some embodiments, the second intake runner comprises:

the cylinder body and the bearing bush are jointly provided with the second air inlet hole communicated with the annular groove, and the second air inlet hole is communicated to the end face, deviating from the cylinder body, of the bearing bush.

In some embodiments, the number of the bearing bushes is at least two, and the two bearing bushes are distributed along the circumference of the cylinder.

In some embodiments, each of the bearing shells is provided with at least one second air inlet hole.

In some embodiments, a gap is formed between two adjacent bearing bushes along the circumferential direction of the cylinder.

In some embodiments, the surface of the bearing bush facing away from the cylinder body is fixedly connected with the graphite piece through a support rib.

In some embodiments, the supporting rib comprises a plurality of supporting ribs, and each supporting rib is concentrically arranged.

In some embodiments, the surface of the bearing bush facing away from the cylinder body is provided with a groove, and the support rib is installed in the groove.

The embodiment of the invention also provides a gas suspension centrifugal compressor which comprises the radial bearing provided by any technical scheme of the invention.

According to the radial bearing provided by the technical scheme, the bearing bush can not be separated from the substrate due to the connection between the bearing bush and the substrate, and a certain inclination can be generated relative to the substrate when the bearing bush is stressed in the working process of the radial bearing, so that the damping of the radial bearing can be adjusted to meet the working requirement of the radial bearing. Therefore, the radial bearing provided by the technical scheme has good self-adaptability, and because a double-layer air film can be formed, the damping performance is good, extra high damping can be provided for the radial bearing under the working condition of high rotating speed, and the stability, the self-adaptability and the reliability of the radial bearing are greatly improved. After the radial bearing provided by the embodiment of the invention is actually used, because the radial bearing structure has better self-adaptability and high damping characteristic, the defect of low damping of the static pressure radial bearing in a high rotating speed state can be well made up, and the tilting pad structure has good self-adaptability and replaceability, so that the rotating speed operation range of the porous static pressure gas radial bearing and the reliability of the static pressure gas radial bearing are improved.

Drawings

The accompanying drawings, which are included to provide a further understanding of the invention and are incorporated in and constitute a part of this application, illustrate embodiment(s) of the invention and together with the description serve to explain the invention without limiting the invention. In the drawings:

FIG. 1 is a schematic cross-sectional view of a radial bearing provided by an embodiment of the present invention;

FIG. 2 is a schematic sectional view A-A of FIG. 1;

FIG. 3 is a schematic cross-sectional view of a bearing sleeve of a radial bearing provided by an embodiment of the present invention;

FIG. 4 is a schematic cross-sectional view B-B of FIG. 3;

FIG. 5 is a schematic cross-sectional view of a bearing pedestal of a radial bearing provided by an embodiment of the present invention;

FIG. 6 is a schematic cross-sectional view C-C of FIG. 5;

FIG. 7 is an enlarged view of a portion D of FIG. 5;

FIG. 8 is a schematic structural diagram of a graphite member of a radial bearing provided in accordance with an embodiment of the present invention;

FIG. 9 is a top view of FIG. 8;

FIG. 10 is a schematic front view of a radial bearing and a rotating shaft relative to each other according to an embodiment of the present invention;

FIG. 11 is a schematic left side view of a radial bearing and a rotating shaft in accordance with an embodiment of the present invention;

fig. 12 is a schematic view of a use state of a radial bearing according to an embodiment of the present invention.

Detailed Description

The technical solution provided by the present invention will be explained in more detail with reference to fig. 1 to 12.

The embodiment of the invention provides a radial bearing, which comprises a bearing sleeve 1, a bearing base 2 and a graphite piece 3. The bearing sleeve 1 comprises a through hole 11, the rotary shaft 7 being mounted in the through hole 11. The bearing base 2 includes a cylinder 21 mounted on the inner wall of the through hole 11 and a bush 22 connected to the cylinder 21 through a connecting portion 23. The connecting portion 23 is configured to move the bearing bush 22 relative to the joint of the cylinder 21 and the bearing bush 22 by an external force. The graphite member 3 is mounted on the side of the bearing bush 22 remote from the cylinder 21.

The radial bearing is used for mounting the rotating shaft 7. The bearing sleeve 1 is used for mounting the bearing base 2, and the graphite piece 23 is mounted on the bearing base 2. The surface of the graphite piece 3 remote from the bearing base 2 serves as a surface for cooperation with the rotary shaft 7.

Referring to fig. 1 to 4, the bearing sleeve 1 is cylindrical, and the cylinder 21 is detachably connected to the bearing sleeve 1. The bearing base 2 is mounted on the inner wall of the first through hole 11. In some implementations, the bearing sleeve 1 is hot pressed with the barrel 21 by way of an interference fit. The reliability of the connection between the bearing sleeve 1 and the bearing base 2 can be better ensured through interference fit, and the bearing sleeve and the bearing base are prevented from moving relatively in the operation process to influence the reliability of the bearing.

Specifically, the radial bearing sleeve 1 is sleeved on the radial bearing base 2 in an interference fit mode, the connection reliability of the radial bearing sleeve 1 and the radial bearing base 2 can be better guaranteed through the interference fit, and the radial bearing sleeve and the radial bearing base are prevented from moving relatively in the operation process to influence the reliability of the radial bearing.

The graphite member 3 is attached to the bearing base 2. The shaft 7 is supported by the graphite member 3.

The first through hole 11 is used for mounting the rotating shaft 7. The bearing pedestal 2 is arranged on the inner wall of the first through hole 11, and the graphite piece 3 is arranged on the bearing pedestal 2. When the radial bearing does not work, the graphite piece 3 is contacted with the rotating shaft 7; in the working process, supporting gas is filled between the graphite piece 3 and the rotating shaft 7 so as to support the rotating shaft 7 in the working process.

The radial bearing provided by the technical scheme is a tiltable porous static pressure gas radial bearing structure, has good self-adaptability, and can be well adapted to the condition that the stress of the rotor of the compressor is changed under different working conditions. Under the high-speed state, the bearing bush 22 can be adjusted in a self-adaptive manner according to the stress condition, and an air film is formed between the outer surface of the bearing bush 22 and the inner surface of the bearing base 2 seat, and an air film is formed between the inner surface of the bearing bush 22 and the shaft diameter of the rotating shaft 7. The double-layer air film can dissipate certain vibration energy, so that the structure also has certain vibration absorption, and the phenomenon that the radial bearing is damped to descend under a high rotating speed state can be well solved.

The bearing bush 22 and the cylinder 21 are integrally machined, that is, the bearing bush 22 and the connecting part 23 are cut out from one cylinder 21 in a cutting mode, and the connecting part 23 has higher strength in the integral cutting mode. The connecting portion 23 is elongated. And the connecting part 23 is provided with a round angle which can well reduce stress concentration and prevent the connecting part 23 from being broken. Referring to fig. 5 to 7, a specific implementation of the bearing base 2 is described below.

The bearing base 2 includes a cylindrical body 21 and a bearing bush 22. The bearing bush 22 is connected to the cylinder 21, and the connection portion of the cylinder 21 and the bearing bush 22 is relatively small, as shown in fig. 7. On one hand, the connection ensures that the cylinder 21 and the bearing bush 22 are always in a connection state in the working process of the radial bearing, and the bearing bush 22 cannot fall off, fall off or shift. On the other hand, after the bearing bush 22 is stressed, the bearing bush 22 can change the inclination angle relative to the cylinder 21, and further the damping size and the stress balance of the radial bearing are realized.

Specifically, in some embodiments, the cylinder 21 and the bearing bush 22 are connected by the connecting portion 23, the connecting portion 23 is located at a middle portion of the bearing bush 22 along the axial direction of the cylinder 21, and a length L1 of the connecting portion 23 in the axial direction of the cylinder 21 is smaller than a length L2 of the bearing bush 22 in the axial direction of the cylinder 21.

The connecting portion 23 is small in size, the connecting portion 23 is adopted to connect the bearing bush 22 with the base plate 21, on one hand, the bearing bush 22 and the base plate 21 are kept in a connecting state, in the working process of the radial bearing, the bearing bush 22 cannot be separated from the connecting portion 23, and the bearing bush 22 cannot fall off. On the other hand, when the bearing bush 22 is subjected to the acting force of the gas, the bearing bush 22 may incline to a certain degree relative to the connecting portion 23, that is, the size of the wedge angle in fig. 11 changes, so that the air film structure between the bearing bush 22 and the rotating shaft 7 can be changed, as shown in fig. 11, and then the damping coefficient of the radial bearing is changed, so that the damping of the radial bearing can adapt to the requirement of the actual working condition.

The cylinder 21 and the bearing bush 22 are always connected together. The connecting part 23 between the cylinder 21 and the bearing bush 22 is relatively small in size, so that a certain gap exists between the cylinder 21 and the bearing bush 22, the gap-like bearing bush can obliquely swing around the connecting part 23 of the cylinder and the bearing bush when being subjected to gas acting force, and the inclination angle and the size of the bearing bush 22 are changed, so that damping self-adaptation is realized.

With continued reference to fig. 7, in some embodiments, the connection portions 23 and the cylinder 21 and the connection portions 23 and the bearing pads 22 are smoothly connected. The connecting part 23 and the cylinder 21 are in smooth transition, and the connecting part 23 and the bearing bush 22 are also in smooth transition. The smooth transition can well reduce stress concentration and prevent breakage.

Referring to fig. 8 and 9, the specific connection and implementation of the graphite pieces 3 will be described.

The graphite member 3 is specifically of an arc-shaped sheet structure. The center of the graphite piece 3 is collinear with the center of the bearing sleeve 1.

The number of graphite pieces 3 is the same as the number of bearing pads 22, and each bearing pad 22 is provided with one graphite piece 3.

Above-mentioned technical scheme, graphite spare 3 can conveniently be replaced, has avoided certain regional damage of journal bearing and need change whole journal bearing's drawback, has saved raw materials and cost, has increased journal bearing's life.

In some embodiments, the surface of the bearing shell 22 facing away from the cylinder 21 is fixedly connected to the graphite element 3 by means of the support ribs 6. The support rib 6 is, for example, plural.

The support ribs 6 are, for example, glued to the graphite part 3, so that after the graphite part 3 is mounted in place, there is a certain gap between the graphite part 3 and the bearing shell 22, so that gas can penetrate into the graphite part 3.

In some embodiments, the support rib 6 comprises a plurality of support ribs 6, and each support rib 6 is concentrically arranged. Each support rib 6 is arranged concentrically. The structure makes the structure of the radial bearing more balanced.

Every graphite piece 3 all is fixed with many brace rods 6, and brace rod 6 not only plays the supporting role for graphite piece 3's installation is more firm, still makes to have the clearance between graphite piece 3 and the axle bush 22, makes gas can permeate the cavity at pivot 7 place smoothly via graphite piece 3.

Referring to fig. 5 and 6, in some embodiments, the surface of the bearing shell 22 facing away from the cylinder 21 is provided with a groove 25, and the support rib 6 is mounted inside the groove 25. The support ribs 6 have gaps 61 between each other so that the continuity of the concave regions of the grooves 25 is not affected and the regions of each groove 25 are still connected.

The graphite member 3 is provided with support ribs 6, and gaps 61 are provided between the support ribs 6. The support ribs 6 mainly serve to support the graphite piece 3 and prevent the graphite piece from being broken under pressure, and the gaps 61 serve to conduct the grooves 25 so that the gas is uniformly distributed in the grooves 25.

During the operation of the radial bearing, the groove 25 plays a role of accommodating external air, so that the external air is gathered in the groove 25 and then enters the position of the rotating shaft 7 along the small holes of the porous graphite block 3 to realize the support of the rotating shaft 7 by the air. The grooves 25 are mainly used for adhering the graphite piece 3 to the bearing bush 22, and the gas can uniformly enter the graphite piece 3, so that the bearing stability of the radial bearing is improved.

Graphite spare 3 pastes on recess 25 for epoxy type plastics generally through sealed glue to graphite spare 3 extra is provided with the chamfer structure, and this chamfer structure can form the region of placing sealed glue with recess 25 department, thereby makes sealed glue play fixed and sealed effect well.

The implementation of the intake runners is described below.

Referring to fig. 5 and 6, in some embodiments, the bearing sleeve 1 is provided with a first inlet flow channel 4 and the bearing base 2 is provided with a second inlet flow channel 5. The first intake runner 4 and the second intake runner 5 are communicated; the first inlet flow channel 4 and the second inlet flow channel 5 together serve to guide the gas to the end face of the bearing shell 22 facing the graphite part 3. The gas then permeates through the pores of the graphite piece 3 into the space indicated by the gas film in fig. 11.

In some embodiments, the first intake runner 4 includes a first intake hole 41 and an annular groove 42. The first intake ports 41 penetrate the thickness direction of the bearing sleeve 1. The annular groove 42 opens on the surface of the bearing sleeve 1 facing the cylinder 21 and communicates with the first air intake hole 41.

The first intake holes 41 are, for example, one. According to the technical scheme, the external air of the radial bearing can enter the annular groove 42 of the bearing sleeve 1 through the first air inlet hole 41 and finally respectively enter each bearing bush 22, so that the defect that the same number of air supply holes are required to be formed in the whole compressor due to the fact that a plurality of air supply holes are formed in the radial bearing support is avoided.

The bearing sleeve 1 is provided with a first air inlet 41, which is mainly used to introduce external air into the radial bearing. The outside air flow enters the radial bearing from the first air intake hole 41 and then flows toward the annular groove 42. The gas flows in the annular groove 42 and is then supplied to the respective second inlet flow channels 5. Each bearing shell 22 is supplied with air separately, i.e. each bearing shell 22 is provided with a second inlet flow channel 5 separately. The plurality of second intake runners 5 are uniformly distributed along the circumferential direction of the first through hole 11, and the bearing shoes 22 are also uniformly distributed along the circumferential direction of the first through hole 11, so that the stress of each bearing shoe 22 is substantially equalized. The final supporting force for the rotating shaft 7 is also relatively uniform in the circumferential direction.

The bearing sleeve 1 is further provided with an annular groove 42, and the annular groove 42 is mainly used for allowing outside air to enter the groove 25 through the four second air inlet holes 52 which are uniformly distributed and then filling the whole groove 25 through the through groove of the graphite member 3. Then, the graphite piece 3 permeates into a gap between the radial bearing and the rotor to form an air film to support the rotor. Because each set of bearing bush 22 needs to supply air respectively, four air supply holes need to be formed in the bearing bush 22, and the external air can be conducted and enter the bearing bush 22 only under the condition that the bearing sleeve 1 is provided with one first air inlet hole 41 by adopting an annular air path mode, so that the complexity of increasing the external air path is avoided.

Referring to fig. 5, in some embodiments, the second intake runner 5 includes a second intake hole 52, the cylinder 21 and the bearing bush 22 are jointly provided with the second intake hole 52 communicated with the annular groove 42, and the second intake hole 52 is communicated to an end surface of the bearing bush 22 facing away from the cylinder 21, that is, an end surface of the graphite member 3 facing the bearing bush 22.

The outside air flow enters the radial bearing from the first air intake hole 41 and then flows toward the annular groove 42. The gas flows in the annular groove 42 and is then supplied to the respective second gas intake holes 52. Each bearing shell 22 is supplied with air separately, i.e. each bearing shell 22 is provided with a second air inlet hole 52 separately. The plurality of second air intake holes 52 are uniformly distributed along the circumferential direction of the first through hole 11, and the bearing shells 22 are also uniformly distributed along the circumferential direction of the first through hole 11, so that the stress of each bearing shell 22 is substantially equalized. The final supporting force for the rotating shaft 7 is also relatively uniform in the circumferential direction.

In some embodiments, the number of the bearing pads 22 is at least two, and the two bearing pads 22 are distributed along the circumference of the cylinder 21. The bearing bushes 22 are independently installed without affecting each other. In some embodiments, four bearing shells 22 are provided.

In some embodiments, at least one second air intake hole 52 is provided for each bearing shoe 22. The second inlet holes 52 direct the gas to the position where the graphite piece 3 is located.

In some embodiments, four bearing pads 22 are uniformly distributed on the bearing base 2, which is only illustrated and does not mean that there are only four bearing pads. The corresponding graphite pieces 3 and the bearing bushes 22 are equal in number, and the graphite blocks of the structure can be well replaced. When the performance of a certain graphite piece 3 on the bearing bush 22 is reduced, the graphite piece can be well replaced without replacing all the graphite pieces 3, the service life of the radial bearing is prolonged, and the cost can be well reduced.

Referring to fig. 1 and 5, in some embodiments, a gap 26 is provided between two adjacent bearing pads 22 along the circumference of the cylinder 21.

After the gas enters the space where the rotating shaft 7 is located, the gas flows around due to the existence of the gap 26, and finally, the gas in the through hole 11 is communicated with each other.

The radial bearing that above-mentioned technical scheme provided, the adoption designs into bearing base 2 the many oil wedges inclinable structure that has the even axle bush 22 of polylith, and the independent design has the air cavity on every axle bush 22, graphite member 3 is equally by several even blocks of monolithic structural design, paste on recess 25 through sealed glue, radial bearing gas enters into the air hole that axle bush 22 and finally enters into in the recess 25 of axle bush 22 through the annular gas circuit of seting up on bearing sleeve 1 behind the air hole that bearing sleeve 1 entered into bearing sleeve 1 on the bearing sleeve 1.

Another embodiment of the present invention provides an air-suspension centrifugal compressor, including the radial bearing provided in any one of the technical solutions of the present invention.

In the description of the present invention, it is to be understood that the terms "central", "longitudinal", "lateral", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", etc., indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience in describing the present invention and for simplicity in description, and do not indicate or imply that the referenced devices or elements must have a particular orientation, be constructed and operated in a particular orientation, and thus, are not to be considered as limiting the scope of the present invention.

Finally, it should be noted that: the above examples are only intended to illustrate the technical solution of the present invention, but not to limit it; although the present invention has been described in detail with reference to the foregoing embodiments, it will be understood by those of ordinary skill in the art that: it is to be understood that modifications may be made to the technical solutions described in the foregoing embodiments, or equivalents may be substituted for some of the technical features thereof, but such modifications or substitutions do not depart from the spirit and scope of the technical solutions of the embodiments of the present invention.

Claims

1. A radial bearing, comprising:

a bearing sleeve (1) comprising a through hole (11);

the bearing base (2) comprises a cylinder body (21) arranged on the inner wall of the through hole (11) and a bearing bush (22) connected with the cylinder body (21) through a connecting part (23); the bearing bush (22) is configured to be movable relative to the connection of the cylinder (21) and the bearing bush (22) under the action of external force; and

and the graphite piece (3) is arranged on one side of the bearing bush (22) far away from the cylinder (21).

2. The radial bearing according to claim 1, wherein the connecting portion (23) is elongated, the connecting portion (23) is located at a middle of the bearing shell (22) in an axial direction of the cylinder (21), and a length of the connecting portion (23) in the axial direction of the cylinder (21) is smaller than a length of the bearing shell (22) in the axial direction of the cylinder (21).

3. Radial bearing according to claim 2, wherein the junction of the connection portion (23) and the cylinder (21) and the junction of the connection portion (23) and the bearing shell (22) are rounded off.

4. Radial bearing according to claim 2, characterized in that the bearing sleeve (1) is provided with a first inlet flow channel (4), the bearing base (2) being provided with a second inlet flow channel (5); the first intake runner (4) and the second intake runner (5) are in communication; the first gas inlet channel (4) and the second gas inlet channel (5) are jointly used for guiding gas to the end face, facing the graphite piece (3), of the bearing shell (22).

5. The radial bearing of claim 4, wherein the first inlet flow channel (4) comprises:

a first air intake hole (41) that penetrates the thickness direction of the bearing sleeve (1); and

the annular groove (42) is formed in the surface, facing the barrel body (21), of the bearing sleeve (1) and is communicated with the first air inlet hole (41).

6. Radial bearing according to claim 5, wherein the second inlet flow channel (5) comprises:

the cylinder body (21) and the bearing bush (22) are provided with the second air inlet hole (52) communicated with the annular groove (42), and the second air inlet hole (52) is communicated to the end face, facing the graphite piece (3), of the bearing bush (22).

7. The radial bearing according to claim 6, wherein the number of the bearing shells (22) is at least two, and the two bearing shells (22) are arranged in a distributed manner along the circumference of the cylinder (21).

8. Radial bearing according to claim 7, characterized in that each bearing shell (22) is provided with at least one second air inlet hole (52).

9. The radial bearing according to claim 7, characterized in that a gap is provided between two adjacent bearing shells (22) in the circumferential direction of the cylinder (21).

10. Radial bearing according to claim 1, characterized in that the surface of the bearing shell (22) facing away from the cylinder (21) is fixedly connected to the graphite part (3) by means of support ribs (6).

11. Radial bearing according to claim 10, wherein the support rib (6) comprises a plurality of support ribs, each support rib (6) being concentrically arranged.

12. Radial bearing according to claim 10, characterized in that the surface of the bearing shell (22) facing away from the cylinder (21) is provided with a groove (25), the support bar (6) being mounted inside the groove (25).

13. An air-bearing centrifugal compressor comprising the radial bearing according to any one of claims 1 to 12.