Dynamic pressure gas radial bearing

Abstract

The utility model relates to a dynamic pressure gas radial bearing, relates to the technical field of dynamic pressure gas bearings, and is used for solving the problem that the dynamic pressure gas radial bearing is not suitable for bidirectional rotation of a rotor. Comprising a bearing shell in which a shaft hole is formed; the elastic supporting assembly is arranged on the inner hole wall of the shaft hole in the circumferential direction of the shaft hole, and the two ends of the elastic supporting assembly are limited in the bearing shell in the circumferential direction; a rotor is rotatably arranged in the elastic supporting assembly, a wedge-shaped gap is formed between the inner wall face of the elastic supporting assembly and the outer wall face of the rotor, and when the rotor rotates clockwise or anticlockwise, the two ends of the elastic supporting assembly are subjected to rotor tangential force and gas film tangential force to generate elastic deformation, so that the elastic supporting assembly is in a tightened state. According to the utility model, when the rotor rotates bidirectionally, the elastic support groups are in a tightened state, so that the deformation of the wedge-shaped gap is controlled within an allowable deformation range. Therefore, the bidirectional suspension function of the dynamic pressure gas radial bearing on the rotor is realized.

Description

Technical Field

[0001] The utility model relates to the technical field of dynamic pressure gas bearings, in particular to a dynamic pressure gas radial bearing. Background Art

[0002] The hydrodynamic gas bearing uses gaseous medium to suspend the rotor. It has a series of advantages such as oil-free, high speed, low vibration, and high temperature resistance. It is a new generation of high-precision bearing technology and is mainly used in high-speed centrifugal separators, low-temperature refrigeration centrifugal compressors, micro gas turbines, air compressors, turbochargers, etc. The hydrodynamic gas radial bearing is a type of hydrodynamic gas bearing, which is generally used in pairs to support the shaft to make centripetal rotational motion.

[0003] In actual use, bidirectional operation of the rotor (rotating in a clockwise or counterclockwise direction) is difficult to avoid, such as the presence of back electromotive force when the motor is started, the reverse phase sequence of the electronic three-phase power line, and the backflow of air when the centrifugal compressor surges severely. Some products even need to change the direction of rotation themselves, such as the spindle steering of machine tools and the travel of three-coordinate detection equipment.

[0004] In the prior art, when the rotor in the dynamic pressure gas radial bearing rotates counterclockwise, the bearing can work normally. However, when the rotor rotates clockwise, the bearing may fail due to its own structure and cannot work normally, resulting in the dynamic pressure gas radial bearing being unable to be used in the application scenario of the rotor rotating in both directions.

[0005] In other words, the conventional dynamic pressure gas radial bearing has the problem of not being applicable to the bidirectional rotation of the rotor. Utility Model Content

[0006] The utility model provides a dynamic pressure gas radial bearing, which can be used to solve the problem that the dynamic pressure gas radial bearing cannot be used for the bidirectional rotation of the rotor.

[0007] The utility model provides a dynamic pressure gas radial bearing, comprising:

[0008] a bearing shell having a shaft hole disposed therein; and

[0009] An elastic support component is arranged on the inner hole wall of the shaft hole along the circumference of the shaft hole, and two ends of the elastic support component are circumferentially confined in the bearing shell;

[0010] Among them, a rotor is arranged in the elastic support component, and a wedge-shaped gap is formed between the inner wall surface of the elastic support component and the outer wall surface of the rotor. When the rotor rotates in a clockwise or counterclockwise direction, the two ends of the elastic support component are subjected to the action of force and elastically deform, so that the elastic support component is in a taut state. When the elastic support component is in a taut state, the elastic deformation amount of the inner wall surface is within a preset deformation amount, and the wedge-shaped gap is within a preset gap range.

[0011] In one embodiment, when the rotor rotates in a counterclockwise direction, one end of the elastic support assembly is in a stretched state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support assembly is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, so that the elastic support assembly is in a taut state; when the rotor rotates in a clockwise direction, one end of the elastic support assembly is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support assembly is in a stretched state due to the tangential force of the rotor and the tangential force of the air film, so that the elastic support assembly is in a taut state.

[0012] In one embodiment, the dynamic pressure gas radial bearing includes a plurality of elastic support components, and the plurality of elastic support components are arranged in the shaft hole at intervals along the circumferential direction of the shaft hole.

[0013] In one embodiment, the bearing shell is provided with two first axial grooves along its axial extension, and the two ends of the elastic support assembly are respectively arranged in the two first axial grooves along the axial direction of the bearing shell, and the two first axial grooves are respectively adapted to the two ends of the elastic support assembly to limit the circumferential movement of the elastic support assembly.

[0014] In one embodiment, the first axial groove includes a first mounting groove and a second mounting groove, and the elastic support assembly includes:

[0015] A top foil, two ends of which are respectively arranged in the two first mounting grooves, and a wedge-shaped gap is formed between the inner wall surface of the top foil and the outer wall surface of the rotor; and

[0016] The two ends of the corrugated foil are respectively arranged in the two second mounting grooves, and the corrugated foil is arranged in the top foil to support the top foil;

[0017] Among them, when the rotor rotates in the counterclockwise direction, one end of the top foil and the corrugated foil in the same direction is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support component and the corrugated foil in the same direction is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates in the clockwise direction, one end of the top foil and the corrugated foil in the same direction is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support component and the corrugated foil in the same direction is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

[0018] In one embodiment, the top foil comprises:

[0019] a top foil body, which forms a wedge-shaped gap with the outer wall surface of the rotor; and

[0020] Two top foil connection parts are respectively arranged at two ends of the top foil body, and the two top foil connection parts are respectively arranged in the two first installation grooves;

[0021] Among them, when the rotor rotates counterclockwise, one of the top foil connecting parts is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other top foil connecting part is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates clockwise, one of the top foil connecting parts is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other top foil connecting part is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

[0022] In one embodiment, the wedge-shaped gap includes a wedge-shaped convergent section and a regulating air film bearing area connected to the wedge-shaped convergent section, and the top foil body includes:

[0023] An arc segment, which forms a regulating air film bearing area with the outer wall surface of the rotor; and

[0024] Two broken line segments are respectively arranged at two ends of the arc segment, and a wedge-shaped convergent section is formed between the broken line segment and the outer wall surface of the rotor;

[0025] The wedge-shaped convergent section is used for air intake, and the regulating air film bearing area is used for forming an air film for suspending the rotor.

[0026] In one embodiment, the polyline segment includes:

[0027] a first top foil fold adjacent to the air inlet of the bearing shell; and

[0028] A second top foil folded edge, one end of which is connected to the first top foil folded edge, and the other end of the second top foil folded edge is connected to one end of the arc segment;

[0029] There is a first convergence angle θ1 between the first top foil folded edge and the outer wall surface of the rotor, there is a second convergence angle θ2 between the second top foil folded edge and the outer wall surface of the rotor, and the first convergence angle θ1 is greater than the second convergence angle θ2.

[0030] In one embodiment, the bump foil comprises:

[0031] a bump foil body, which contacts the top foil body and is used to support the top foil body; and

[0032] Two corrugated foil connecting parts are respectively arranged at two ends of the corrugated foil body, and the two corrugated foil connecting parts are respectively arranged in the two second mounting grooves;

[0033] Among them, when the rotor rotates counterclockwise, one of the corrugated foil connecting parts is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other corrugated foil connecting part is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates clockwise, one of the corrugated foil connecting parts is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other corrugated foil connecting part is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

[0034] In one embodiment, the bump foil body comprises:

[0035] A first corrugated support segment, which contacts the arc segment and is used to support the arc segment; and

[0036] A second corrugated support segment, which is respectively arranged at both ends of the first corrugated support segment, and the second corrugated support segment is used to support the second top foil folding edge; and

[0037] The third corrugated support segment is arranged on one end of the second corrugated support segment away from the first corrugated support segment. The third corrugated support segment contacts the first top foil folded edge and is used to support the first top foil folded edge.

[0038] In one embodiment, the bump foil connection portion comprises:

[0039] one or more first foil load bearing beams; and

[0040] one or more second corrugated foil stress beams spaced apart from the first corrugated foil stress beams; and

[0041] One or more corrugated foil elastic beams, which are arranged between the first corrugated foil stress beam and the second corrugated foil stress beam;

[0042] The first corrugated foil stress beam and the second corrugated foil stress beam can be elastically deformed by the rotor tangential force and the air film tangential force, so as to enhance the elastic support strength of the inner wall surface of the corrugated foil.

[0043] In one embodiment, the profile of the bump foil connecting portion is in an "N"-shaped configuration, an "M"-shaped configuration, or a "U"-shaped configuration.

[0044] In one embodiment, the hydrodynamic gas radial bearing also includes an elastic adjustment member disposed in the bearing shell, which is used to radially compress the arc segment toward the central axis of the shaft hole to increase the wedge-shaped convergence section and adjust the length of the gas flow channel in the air film bearing area.

[0045] In one embodiment, the bearing shell is provided with a second axial groove extending along the axial direction thereof, and the elastic adjustment member is provided in the second axial groove along the axial direction of the bearing shell.

[0046] In one embodiment, the top foil connection comprises:

[0047] a first top foil load bearing beam; and

[0048] A second top foil stress beam, which is spaced apart from the first top foil stress beam; and

[0049] A top foil elastic beam, which is arranged between the first top foil stress beam and the second top foil stress beam;

[0050] The first top foil stress beam and the second top foil stress beam can be elastically deformed by the tangential force of the rotor and the tangential force of the air film, so as to enhance the elastic support strength of the top foil.

[0051] In one embodiment, the top foil connection portion has an "N" shaped configuration or an "M" shaped configuration or a "U" shaped configuration as its profile.

[0052] Compared with the prior art, the advantage of the utility model is that the two ends of the elastic support assembly are confined in the bearing shell along the circumferential direction. In this way, when the rotor rotates in the elastic support assembly in the clockwise or counterclockwise direction, the rotor tangential force generated by the rotation of the rotor itself and the air film tangential force generated when the air film moves can be applied to the two ends of the elastic support assembly, causing it to elastically deform in the circumferential direction. Thereby, the elastic support assembly is tightened. In addition, the deformation resistance of the inner wall surface of the elastic support assembly when subjected to the air film pressure is enhanced, thereby ensuring that when the rotor rotates at high speed, the elastic deformation amount of the inner wall surface after being subjected to pressure can be controlled within the preset deformation amount, that is, the deformation amount of the wedge-shaped gap is controlled within the allowable deformation range, thereby ensuring that the air film for suspending the rotor can be continuously formed in the wedge-shaped gap, thereby realizing the bidirectional suspension function of the dynamic pressure gas radial bearing for the rotor. BRIEF DESCRIPTION OF THE DRAWINGS

[0053] The present invention will be described in more detail below based on embodiments and with reference to the accompanying drawings.

[0054] Figure 1 It is a schematic diagram of the structural composition of a dynamic pressure gas radial bearing in the prior art;

[0055] Figure 2 It is a working principle diagram of a dynamic pressure gas radial bearing in the prior art;

[0056] Figure 3 It is a schematic diagram of the three-dimensional structure of the dynamic pressure gas radial bearing in the first embodiment of the utility model;

[0057] Figure 4 yes Figure 3 Longitudinal section view of a medium dynamic pressure gas radial bearing (rotor rotates counterclockwise);

[0058] Figure 5 yes Figure 3 Longitudinal section view of the medium dynamic pressure gas radial bearing (rotor rotates in clockwise direction);

[0059] Figure 6 yes Figure 4 A partial enlarged view of point A in the middle;

[0060] Figure 7 yes Figure 4 A partial enlarged view of point B in the middle (the bearing is in working condition);

[0061] Figure 8 yes Figure 3 Schematic diagram of the three-dimensional structure of the middle bearing shell;

[0062] Fig. 9 yes Figure 3 Schematic diagram of the three-dimensional structure of the medium wave foil;

[0063] Fig.10 yes Figure 3 Schematic diagram of the three-dimensional structure of the middle top foil;

[0064] Fig.11 yes Figure 3 Schematic diagram of the three-dimensional structure of the elastic adjustment member (F1 and F2 are its force directions);

[0065] Fig.12 yes Figure 4 A partial enlarged view of point B in the middle (the bearing is in the stopped state).

[0066] Reference numerals:

[0067] 10. bearing shell; 12. first axial groove; 121. first mounting groove; 122. second mounting groove; 13. second axial groove; 20. elastic support assembly; 21. top foil; 211. top foil body; 2111. arc segment; 2112. fold line segment; 2113. first top foil folding edge; 2114. second top foil folding edge; 212. top foil connecting portion; 2121. first top foil stress beam; 2122. top foil elastic beam; 2123. second top foil stress beam; 22. corrugated foil; 221. corrugated foil body; 2 211, first corrugated support section; 2212, second corrugated support section; 2213, third corrugated support section; 222, corrugated foil connecting portion; 2221, first corrugated foil load-bearing beam; 2222, corrugated foil elastic beam; 2223, second corrugated foil load-bearing beam; 31, wedge-shaped convergence section; 311, first wedge-shaped convergence area; 312, second wedge-shaped convergence area; 32, regulating air film bearing area; 40, elastic adjustment part; 100, rotor; 10', bearing shell; 21', top foil; 22', corrugated foil; 100', rotor. DETAILED DESCRIPTION

[0068] The utility model will be further described below in conjunction with the accompanying drawings.

[0069] It should be noted that if Figure 1 As shown, the prior art dynamic pressure gas radial bearing includes a bearing shell 10', a top foil 21' and a corrugated foil 22'. One end of the corrugated foil 22' and the top foil 21' are generally overlapped together and then welded to the bearing shell 10', which is called the fixed end; the other ends of the corrugated foil 22' and the top foil 21' are freely placed, which is called the free end, and the top foil 21' overlaps the top of each corrugation of the corrugated foil. The working principle of the dynamic pressure gas radial bearing is as follows Figure 2 As shown, the rotor 100' is eccentric relative to the bearing under the action of gravity, and then forms a wedge-shaped gap with the inner surface of the bearing. When the shaft is rotating at high speed, gas with a certain viscosity is continuously brought into the wedge-shaped gap, and the continuous entry of gas causes the gas film to generate a certain pressure. When the gas film force is sufficient to balance the shaft load, the shaft and the bearing are completely separated. In the above process, the bearing shell 10' plays a supporting role, the top foil 21' cooperates with the rotor 100' to form a gap and a working surface with a relative motion speed, and the corrugated foil 22' is an elastic foil with a corrugated shape, which provides partial stiffness and damping for the bearing.

[0070] The above process is also called the dynamic pressure effect, which is the working principle of all dynamic pressure gas radial bearings. However, whether the dynamic pressure effect can be formed is closely related to the bearing structure and the rotor direction.

[0071] by Figure 1 Take the structure as an example to illustrate:

[0072] When the bearing is working, the rotation direction of the rotor 100' must be counterclockwise as shown in the figure, that is, the direction of the rotor must be from the free end of the corrugated foil (or top foil) to the fixed end, so that under the action of the rotor 100', the circumferential tangential force on the corrugated foil 22' (or top foil) is also directed from the free end to the fixed end, so that the corrugated foil 22' (or top foil 21') is compressed and tightened in the circumferential direction. The corrugated foil 22' in the tightened state can give full play to the supporting role of the waveform, thereby providing support for the rotor. On the other hand, if Figure 1 The direction of the rotor is clockwise. At this time, under the action of the circumferential force of the rotor, the circumferential force on the bump foil 22' (or the top foil 21') is directed from the fixed end to the free end, so that the bump foil 22' (or the top foil 21') is stretched in the circumferential direction and relaxes, which aggravates the deformation of the bump foil (at this time, in addition to being deformed by the load of the rotor, the bump foil 22' is also stretched by the circumferential force of the rotor), causing the stiffness of the bump foil 22' to greatly deviate from the design value, which may lead to bearing failure in severe cases.

[0073] It can be seen from the above that the dynamic pressure gas radial bearing in the prior art is limited by its own structure and cannot be applied to the bidirectional rotation of the rotor.

[0074] Embodiment 1

[0075] like Figures 3 to 5As shown, the utility model provides a dynamic pressure gas radial bearing, which includes a bearing shell 10 and an elastic support assembly 20. The bearing shell 10 is provided with an axial hole therein; the elastic support assembly 20 is provided on the inner hole wall of the axial hole along the circumference of the axial hole, and the two ends of the elastic support assembly 20 are circumferentially limited in the bearing shell 10; the rotor 100 is rotatably provided in the elastic support assembly 20, and a wedge-shaped gap is formed between the inner wall surface of the elastic support assembly 20 and the outer wall surface of the rotor 100. When the rotor 100 rotates in a clockwise or counterclockwise direction, the two ends of the elastic support assembly 20 are subjected to the tangential force of the rotor and the tangential force of the air film and elastically deform, so that the elastic support assembly 20 is in a taut state. When the elastic support assembly 20 is in a taut state, the elastic deformation amount of the inner wall surface after being subjected to pressure can be controlled within a preset deformation amount, so that an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap.

[0076] In the above arrangement, the two ends of the elastic support component 20 are confined in the bearing shell 10 along the circumferential direction. In this way, when the rotor 100 rotates in the elastic support component 20 in the clockwise or counterclockwise direction, the rotor tangential force generated by the rotation of the rotor 100 itself and the air film tangential force generated when the air film moves can be applied to the two ends of the elastic support component 20, causing it to elastically deform in the circumferential direction. Thereby, the elastic support component 20 is tightened. In addition, the anti-deformation ability of the inner wall surface of the elastic support component 20 when subjected to the air film pressure is enhanced, so as to ensure that when the rotor 100 rotates at high speed, the elastic deformation amount of the inner wall surface after being subjected to pressure can be controlled within the preset deformation amount, that is, the deformation amount of the wedge-shaped gap is controlled within the allowable deformation range, thereby ensuring that the air film used to suspend the rotor 100 can be continuously formed in the wedge-shaped gap, thereby realizing the bidirectional suspension function of the dynamic pressure gas radial bearing for the rotor 100.

[0077] It should be noted that, in this embodiment, whether the rotor 100 rotates in the clockwise or counterclockwise direction, both ends of the elastic support assembly 20 are subjected to circumferential force to produce elastic deformation, so that the elastic support assembly 20 is tightened. This ensures that the inner wall surface of the elastic support assembly 20 has sufficient anti-deformation ability. Thereby ensuring that the deformation amount of the wedge-shaped gap is controlled within the allowable deformation range, and then ensuring that an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap, so as to realize the bidirectional (clockwise or counterclockwise rotation) suspension function of the dynamic pressure gas radial bearing for the rotor 100. This avoids the problem of failure of the dynamic pressure gas radial bearing caused by the clockwise rotation of the rotor 100 in the prior art. Thereby improving the stability and reliability of the dynamic pressure gas radial bearing during operation. At the same time, its adaptability is also improved.

[0078] Specifically, in one embodiment, when the rotor 100 rotates in the counterclockwise direction, one end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a stretched state, and the other end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a compressed state, so that the elastic support component 20 is in a taut state. In this way, when the rotor 100 rotates in the counterclockwise direction, the elastic support component 20 is in a taut state, and its inner wall surface has sufficient anti-deformation ability. When the rotor 100 rotates in the clockwise direction, one end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a compressed state, and the other end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a stretched state, so that the elastic support component 20 is in a taut state. In this way, when the rotor 100 rotates in the clockwise direction, the elastic support component 20 is in a taut state.

[0079] In the above arrangement, no matter the rotor 100 rotates counterclockwise or clockwise, the elastic support assembly 20 can be in a taut state, providing sufficient elastic support force for the rotor 100 and the air film. This ensures that the deformation of the wedge-shaped gap is controlled within the allowable deformation range, thereby ensuring that an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap, thereby realizing the bidirectional suspension function of the dynamic pressure gas radial bearing for the rotor 100.

[0080] Specifically, Figures 3 to 5 As shown, in one embodiment, the dynamic pressure gas radial bearing includes three elastic support components 20, and the three elastic support components 20 are arranged in the shaft hole at intervals along the circumferential direction of the shaft hole.

[0081] Specifically, Figure 8 As shown, in one embodiment, the bearing shell 10 is provided with two first axial grooves 12 extending along its axial direction, and the two ends of the elastic support assembly 20 are respectively provided in the two first axial grooves 12 along the axial direction of the bearing shell 10, and the two first axial grooves 12 are respectively adapted to the two ends of the elastic support assembly 20, and are used to limit the circumferential movement of the elastic support assembly 20. In this way, the elastic support assembly 20 can be inserted into the first axial groove 12 along the axial direction of the bearing shell 10, and the elastic support assembly 20 installed in the first axial groove 12 can also be taken out along the axial direction of the bearing shell 10. Thereby, the disassembly and assembly efficiency of the elastic support assembly 20 is improved.

[0082] Specifically, Figures 2 to 6 as well as Figure 8As shown, in one embodiment, the first axial groove 12 includes a first mounting groove 121 and a second mounting groove 122. The elastic support assembly 20 includes a top foil 21 and a wave foil 22. The top foil 21, whose two ends are respectively arranged in the two first mounting grooves 121, forms a wedge-shaped gap between the inner wall surface of the top foil 21 and the outer wall surface of the rotor 100; the wave foil 22, whose two ends are respectively arranged in the two second mounting grooves 122, is arranged in the top foil 21 to support the top foil 21; when the rotor 100 rotates in the counterclockwise direction, one end of the top foil 21 and the wave foil 22 in the same direction is subjected to the rotor tangential force and the air film tangential force and is in a tensile state, and the other end of the elastic support assembly 20 and the wave foil 22 in the same direction is subjected to the rotor tangential force and the air film tangential force and is in a compressed state. When the rotor 100 rotates in the counterclockwise direction, one end of the top foil 21 and the bump foil 22 in the same direction is in a stretched state due to the rotor tangential force and the air film tangential force, and the other end of the elastic support assembly 20 and the bump foil 22 in the same direction is in a compressed state due to the rotor tangential force and the air film tangential force. In this way, the elastic support assembly 20 is tightened by the receptor deformation at both ends of the top foil 21 and the bump foil 22. This ensures that no matter whether the rotor 100 rotates in the clockwise or counterclockwise direction, an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap, thereby realizing the bidirectional suspension function of the dynamic pressure gas radial bearing for the rotor 100.

[0083] Specifically, Fig.10 As shown, in one embodiment, the top foil 21 includes a top foil body 211 and two top foil connecting parts 212. The top foil body 211 forms a wedge-shaped gap with the outer wall of the rotor 100; the two top foil connecting parts 212 are respectively arranged at the two ends of the top foil body 211, and the two top foil connecting parts 212 are respectively arranged in the two first mounting grooves 121; when the rotor 100 rotates in the counterclockwise direction, one of the top foil connecting parts 212 is in a tensile state due to the rotor tangential force and the air film tangential force, and the other top foil connecting part 212 is in a compressed state due to the rotor tangential force and the air film tangential force; when the rotor 100 rotates in the clockwise direction, one of the top foil connecting parts 212 is in a compressed state due to the rotor tangential force and the air film tangential force, and the other top foil connecting part 212 is in a tensile state due to the rotor tangential force and the air film tangential force.

[0084] In the above arrangement, the top foil 21 is in a tensioned state through the deformation of the two top foil connecting parts 212, thereby enhancing the elastic support strength of the top foil 21, thereby ensuring that the bidirectional suspension function of the dynamic pressure gas radial bearing can be realized later.

[0085] Specifically, Figure 6 and Fig.10As shown, in one embodiment, the top foil connection part 212 includes a first top foil stress beam 2121, a second top foil stress beam 2123 and a top foil elastic beam 2122. The second top foil stress beam 2123 is spaced apart from the first top foil stress beam 2121; the top foil elastic beam 2122 is disposed between the first top foil stress beam 2121 and the second top foil stress beam 2123; the first top foil stress beam 2121 and the second top foil stress beam 2123 can be elastically deformed by the rotor tangential force and the air film tangential force to enhance the elastic support strength of the top foil 21.

[0086] Specifically, Figure 4 and Figure 5 As shown, in one embodiment, the wedge-shaped gap includes a wedge-shaped convergent section 31 and a regulating air film bearing area 32 connected to the wedge-shaped convergent section 31, and the top foil body 211 includes an arc segment 2111 and two fold line segments 2112. Among them, the arc segment 2111 forms the regulating air film bearing area 32 with the outer wall surface of the rotor 100; the two fold line segments 2112 are respectively arranged at the two ends of the arc segment 2111, and the wedge-shaped convergent section 31 is formed between the fold line segment 2112 and the outer wall surface of the rotor 100; the wedge-shaped convergent section 31 is used for air intake, and the regulating air film bearing area 32 is used to form an air film for suspending the rotor 100.

[0087] Specifically, Figure 4 and Figure 5 As shown, in one embodiment, the fold line segment 2112 includes a first top foil fold 2113 and a second top foil fold 2114. The first top foil fold 2113 is close to the air inlet of the bearing housing 10; the second top foil fold 2114 has one end connected to the first top foil fold 2113, and the other end of the second top foil fold 2114 is connected to one end of the arc segment 2111; there is a first convergence angle θ1 (the angle formed by the first top foil fold 2113 and the outer circle of the rotor 100) between the first top foil fold 2113 and the outer wall of the rotor 100, and there is a second convergence angle θ2 (the angle formed by the second top foil fold 2114 and the outer circle of the rotor 100) between the second top foil fold 2114 and the outer wall of the rotor 100, and the first convergence angle θ1 is greater than the second convergence angle θ2.

[0088] It should be noted that the first convergence angle θ1 is located at the gas inlet. Setting the first convergence angle θ1 at a larger angle is beneficial to improving the dynamic pressure effect and quickly forming an air film. Setting the second convergence angle θ2 to be smaller than the first convergence angle θ1 is beneficial to reducing airflow turbulence.

[0089] Specifically, in one embodiment, the value range of the first convergence angle θ1 is 1° to 4°.

[0090] Specifically, Fig. 9As shown, in one embodiment, the bump foil 22 includes a bump foil body 221 and two bump foil connecting parts 222. The bump foil body 221 is in contact with the top foil body 211 and is used to support the top foil body 211; the two bump foil connecting parts 222 are respectively arranged at the two ends of the bump foil body 221, and the two bump foil connecting parts 222 are respectively arranged in the two second mounting grooves 122; when the rotor 100 rotates in the counterclockwise direction, one of the bump foil connecting parts 222 is in a tensile state due to the rotor tangential force and the air film tangential force, and the other bump foil connecting part 222 is in a compressed state due to the rotor tangential force and the air film tangential force; when the rotor 100 rotates in the clockwise direction, one of the bump foil connecting parts 222 is in a compressed state due to the rotor tangential force and the air film tangential force, and the other bump foil connecting part 222 is in a tensile state due to the rotor tangential force and the air film tangential force.

[0091] In the above arrangement, the two bump foil connecting parts 222 are deformed by force to make the bump foil 22 in a taut state, thereby enhancing the elastic support strength of the bump foil 22 itself, thereby achieving stable elastic support for the top foil 21. This ensures that the bidirectional suspension function of the dynamic pressure gas radial bearing can be realized later.

[0092] Specifically, Figures 3 to 7 as well as Fig. 9 As shown, in one embodiment, the corrugated foil body 221 includes a first corrugated support section 2211, a second corrugated support section 2212 and a third corrugated support section 2213. The first corrugated support section 2211 is in contact with the arc section 2111 and is used to support the arc section 2111; the second corrugated support section 2212 is respectively arranged at both ends of the first corrugated support section 2211, and the second corrugated support section 2212 is used to support the second top foil folding edge 2114; the third corrugated support section 2213 is arranged on one end of the second corrugated support section 2212 away from the first corrugated support section 2211, and the third corrugated support section 2213 is in contact with the first top foil folding edge 2113 and is used to support the first top foil folding edge 2113. In this way, the three corrugated support sections are arranged to support the first and second top foil folding edges and the arc section 2111 one by one. Thereby, stable elastic support for the top foil 21 is achieved.

[0093] Specifically, Fig. 9 As shown, in one embodiment, the first wave-shaped support segment 2211 includes a plurality of first semi-arc arches connected in sequence, the second wave-shaped support segment 2212 is a single second semi-arc arch, and the third wave-shaped support segment 2213 is a single third semi-arc arch. Among the three semi-arc arches, the first semi-arc arch has the highest height, the third semi-arc arch has the lowest height, and the second semi-arc arch has a middle height.

[0094] Specifically, Figure 6As shown, in one embodiment, the corrugated foil connection part 222 includes a single first corrugated foil stress beam 2221, a single second corrugated foil stress beam 2223, and a single corrugated foil elastic beam 2222. Among them, the single second corrugated foil stress beam 2223 is arranged at intervals from the single first corrugated foil stress beam 2221; the corrugated foil elastic beam 2222 is arranged between the single first corrugated foil stress beam 2221 and the single second corrugated foil stress beam 2223; the single first corrugated foil stress beam 2221 and the single second corrugated foil stress beam 2223 can be subjected to the rotor tangential force and the air film tangential force and undergo elastic deformation to enhance the elastic support strength of the inner wall surface of the corrugated foil 22.

[0095] Of course, according to actual conditions, the corrugated foil connection part 222 can be configured to include multiple first corrugated foil stress beams 2221, multiple second corrugated foil stress beams 2223, and multiple corrugated foil elastic beams 2222. Among them, multiple first corrugated foil stress beams 2221 and multiple second corrugated foil stress beams 2223 are sequentially arranged at intervals, and a single corrugated foil elastic beam 2222 is arranged between two adjacent first corrugated foil stress beams 2221, two adjacent second corrugated foil stress beams 2223, and adjacent first corrugated foil stress beams 2221 and second corrugated foil stress beams 2223 for connection.

[0096] Specifically, Figures 3 to 7 as well as Fig. 9 As shown, in one embodiment, the profile of the bump foil connecting portion 222 is in an “N” shape.

[0097] Specifically, Figure 1 As shown, in one embodiment, the hydrodynamic gas radial bearing also includes an elastic adjustment member 40, which is disposed in the bearing shell 10 and is used to radially compress the arc segment 2111 toward the central axis of the shaft hole to increase the wedge-shaped convergence section 31 and adjust the length of the gas flow channel in the air film bearing area 32.

[0098] Specifically, Figures 3 to 5 , Figure 7 , Fig.11 and Fig.12 As shown, in one embodiment, the bearing housing 10 is provided with a second axial groove 13 extending along its axial direction, and the elastic adjustment member 40 is arranged in the second axial groove 13 along the axial direction of the bearing housing 10. This improves the efficiency of disassembly and assembly of the elastic adjustment member 40.

[0099] Specifically, Figures 3 to 5 , Figure 7 , Fig.11 and Fig.12 As shown, Figure 1 As shown, in one embodiment, the profile of the elastic adjusting member 40 is in a “Z” shape, and the second axial groove 13 is a “Z”-shaped groove matched with the elastic adjusting member 40 .

[0100] Of course, the profile of the elastic adjusting member 40 can be set according to actual conditions and is not limited to the “Z” shape.

[0101] like Figures 3 to 12 As shown, based on the first embodiment, a more specific embodiment is described below:

[0102] This embodiment provides a dynamic pressure gas radial bearing with a rotor capable of bidirectional operation, such as Figure 3 As shown, it includes a bearing shell 10 and an elastic support assembly 20. Among them, the rotor 100 is a shaft-type part, and the outer diameter surface (outer wall surface) of the rotor 100 and the inner wall surface of the elastic support assembly 20 are clearance-matched, and a first wedge-shaped convergence area 311 (distributed in the counterclockwise direction), a second wedge-shaped convergence area 312 (distributed in the clockwise direction), and an adjustment air film bearing area 32 with different clearances are formed in different matching areas. When working, the rotor 100 rotates at a high speed under the action of the electromagnetic field of the motor. When the speed reaches the design value, the dynamic pressure gas radial bearing forms an air film through the dynamic pressure effect to suspend the rotor 100.

[0103] It should be noted that the aforementioned wedge-shaped convergent section 31 includes a first wedge-shaped convergent area 311 and a second wedge-shaped convergent area 312. The rotor 100 rotates clockwise to form the second wedge-shaped convergent area 312, and the rotor 100 rotates counterclockwise to form the first wedge-shaped convergent area 311.

[0104] The dynamic pressure gas radial bearing is composed of a shell (bearing shell 10), a "Z"-shaped adjustment part (elastic adjustment part 40), a bump foil 22, a top foil 21, etc. In terms of positioning, the shell has three axially-through "N"-shaped axial grooves (second mounting grooves 122) evenly distributed along the circumference, which are used to assemble the bump foil 22 and limit the freedom of the bump foil 22 in the circumferential direction. Similarly, the shell has three axially-through "N"-shaped axial grooves (first mounting grooves 121) evenly distributed along the circumference, which are used to assemble the top foil 21 and limit the freedom of the top foil 21 in the circumferential direction. Similarly, the shell has three "Z"-shaped axial grooves (second axial grooves 13) evenly distributed in the radial direction, which are used to assemble the "Z"-shaped adjustment part (elastic adjustment part 40) and limit the radial freedom of the "Z"-shaped adjustment part.

[0105] Specifically, the bump foil 22 is an elastic support structure (bump foil body 221) with multiple wave features. The bump foil 22 is assembled between the housing and the top foil 21 in a curved shape, and provides partial rigidity and damping for the rotor through the elastic support structure.

[0106] It should be noted that the material of the corrugated foil 22 itself and the elastic support structure form a comprehensive elastic modulus to provide support stiffness. The dynamic pressure gas radial bearing is a flexible bearing. The foil will deform and displace during operation, absorbing vibration through frictional heat, thereby playing a damping role.

[0107] It should be noted that Figure 1 The bearings of the traditional structure have waveforms of equal height, and the wave foil 22 in this embodiment has waveforms of various heights, that is, the heights of the first to third semi-arc arches are different, the purpose of which is to enable the dynamic pressure gas radial bearing in this embodiment to adapt to the bidirectional operation of the rotor 100.

[0108] Specifically, Figure 4 As shown, when the rotor 100 rotates counterclockwise, in order to form a dynamic pressure effect, the wave height of the corrugated foil body 221 in the first wedge-shaped convergence area 311 gradually increases in the counterclockwise direction, and the top foil 21 matched therewith is also designed with the first and second top foil folding edges and arc segments 2111. Among them, the "N"-shaped force-bearing elastic surface (the upper surface of the first and second corrugated foil force-bearing beams) at one end of the corrugated foil 22 is in a stretched state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and uses its own deformation to provide support for the corrugated foil 22, and the "N"-shaped force-bearing elastic beam (corrugated foil elastic beam 2222) plays the role of connecting the two "N"-shaped force-bearing elastic surfaces.

[0109] Similarly, at this time, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second corrugated foil stress-bearing beams) at the other end of the corrugated foil 22 is in a compressed state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and also provides support for the corrugated foil 22 by its own deformation, while the "N"-shaped stress-bearing elastic beam (corrugated foil elastic beam 2222) serves to connect the two "N"-shaped stress-bearing elastic surfaces at the other end of the corrugated foil.

[0110] and Figure 1 Compared with the bearing of the traditional structure, each corrugated foil has only one elastic surface for bearing force, while each corrugated foil 22 in this embodiment has four elastic surfaces for bearing force, and the theoretical strength is four times that of the traditional structure.

[0111] Similarly, in this process, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second top foil stress-bearing beams) at one end of the top foil 21 located in the first wedge-shaped convergence zone 311 is in a stretched state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and uses its own deformation to provide support for the top foil 21, while the "N"-shaped stress-bearing elastic beam (top foil elastic beam 2122) plays the role of connecting the two "N"-shaped stress-bearing elastic surfaces;

[0112] Similarly, at this time, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second top foil stress-bearing beams) at the other end of the top foil 21 is in a compressed state in the counterclockwise direction due to the tangential force of the rotor and the air film in the circumferential direction, and uses its own deformation to provide support for the top foil 21, while the "N"-shaped stress-bearing elastic beam (top foil elastic beam 2122) plays the role of connecting the two "N"-shaped stress-bearing elastic surfaces; so Figure 1 Compared with the bearing of the traditional structure, each top foil of the traditional structure has only one stress-bearing elastic surface, while each top foil of the present embodiment has four stress-bearing elastic surfaces, and the theoretical strength is four times that of the traditional structure.

[0113] Specifically, Figure 5 As shown, when the rotor 100 rotates counterclockwise, in order to form a dynamic pressure effect, the wave height of the corrugated foil body 221 of the second wedge-shaped convergence area 312 gradually increases in the counterclockwise direction, and the top foil 21 matched therewith is also designed with the first and second top foil folding edges and arc segments 2111. Among them, the "N"-shaped force-bearing elastic surface (the upper surface of the first and second corrugated foil force-bearing beams) at one end of the corrugated foil 22 is in a stretched state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and uses its own deformation to provide support for the corrugated foil 22, and the "N"-shaped force-bearing elastic beam (corrugated foil elastic beam 2222) plays the role of connecting the two "N"-shaped force-bearing elastic surfaces.

[0114] Similarly, at this time, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second corrugated foil stress-bearing beams) at the other end of the corrugated foil 22 is in a compressed state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and also provides support for the corrugated foil 22 by its own deformation, while the "N"-shaped stress-bearing elastic beam (corrugated foil elastic beam 2222) serves to connect the two "N"-shaped stress-bearing elastic surfaces at the other end of the corrugated foil.

[0115] and Figure 1 Compared with the bearing of the traditional structure, each corrugated foil has only one elastic surface for bearing force, while each corrugated foil 22 in this embodiment has four elastic surfaces for bearing force, and the theoretical strength is four times that of the traditional structure.

[0116] Similarly, in this process, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second top foil stress-bearing beams) at one end of the top foil 21 located in the second wedge-shaped convergence area 312 is in a stretched state in the counterclockwise direction due to the tangential force of the rotor 100 and the air film in the circumferential direction, and uses its own deformation to provide support for the top foil 21, while the "N"-shaped stress-bearing elastic beam (top foil elastic beam 2122) plays the role of connecting the two "N"-shaped stress-bearing elastic surfaces;

[0117] Similarly, at this time, the "N"-shaped stress-bearing elastic surface (the upper surface of the first and second top foil stress-bearing beams) at the other end of the top foil 21 is in a compressed state in the counterclockwise direction due to the tangential force of the rotor and the air film in the circumferential direction, and uses its own deformation to provide support for the top foil 21, while the "N"-shaped stress-bearing elastic beam (top foil elastic beam 2122) plays the role of connecting the two "N"-shaped stress-bearing elastic surfaces; so Figure 1 Compared with the bearing of the traditional structure, each top foil of the traditional structure has only one stress-bearing elastic surface, while each top foil of the present embodiment has four stress-bearing elastic surfaces, and the theoretical strength is four times that of the traditional structure.

[0118] Through the structural design of the corrugated foil 22 and the top foil 21 , no matter whether the rotor 100 rotates counterclockwise or clockwise, the dynamic pressure gas radial bearing can form an air film through the dynamic pressure effect to support the rotor 100 .

[0119] In this embodiment, in addition to setting θ1 and θ2 to adjust the dynamic pressure effect of the bearing (short for dynamic pressure radial bearing), it is also to shorten the time of the bearing in the take-off stage (take-off is a process starting from zero rotor speed, gradually increasing the speed, and forming a sufficient pressure air film to support the rotor to float completely).

[0120] like Figure 7 and Fig.12 As shown, the present embodiment further designs a "Z"-shaped adjusting member (elastic adjusting member 40), and the height of the "Z"-shaped adjusting member is H2. By designing the value of H2, when the bearing is in the stopped state, the "Z"-shaped adjusting member forces the wave foil 22 and the top foil 21 to move radially toward the center of the circle within the range of θ (the central angle of the circle corresponding to the arc length of the contact between the "Z"-shaped adjusting member and the wave foil 22), so that the gap H1 (the regional gap value corresponding to the first wave-shaped support segment 2211 in the working state) becomes smaller, and the wedge angle θ3 of the air film bearing area 32 (the angle formed by the arc segment 2111 and the outer circle of the rotor 100) becomes larger, and cooperates with the first wedge-shaped convergence area 311 or the second wedge-shaped convergence area 312 to form a wedge-shaped convergence area with a longer flow channel, thereby accelerating the formation of the air film. When the running speed of the rotor 100 is very high, the air film pressure in the regulating air film bearing area 32 is very large, and the air film is pressed within the range of θ. The corrugated foil 22 and the top foil 21 move radially away from the center of the circle. Since the "Z"-shaped adjusting part is elastic (the working principle of this structure is similar to that of a spring), the height H2 of the "Z"-shaped adjusting part is also compressed and becomes smaller. The convergence length of the regulating air film bearing area 32 is restored, and the H1 gap area is all high-pressure air film, which is beneficial to maintaining the stability of the rotor 100 in the high-speed area.

[0121] like Fig.12As shown, the height of the "Z"-shaped adjustment member in the shutdown state is H4, and the regional gap value corresponding to the first wave-shaped support section 2211 is H3. Among them, H4 is greater than H2, and H3 is less than H1.

[0122] Embodiment 2

[0123] refer to Figures 1 to 12 As shown, this embodiment provides a bearing shell 10 and an elastic support assembly 20. The bearing shell 10 is provided with an axial hole therein; the elastic support assembly 20 is provided on the inner hole wall of the axial hole along the circumferential direction of the axial hole, and the two ends of the elastic support assembly 20 are circumferentially limited in the bearing shell 10; the rotor 100 is rotatably provided in the elastic support assembly 20, and a wedge-shaped gap is formed between the inner wall surface of the elastic support assembly 20 and the outer wall surface of the rotor 100. When the rotor 100 rotates in a clockwise or counterclockwise direction, the two ends of the elastic support assembly 20 are subjected to the tangential force of the rotor and the tangential force of the air film and elastically deform, so that the elastic support assembly 20 is in a taut state. When the elastic support assembly 20 is in a taut state, the elastic deformation amount of the inner wall surface after being subjected to pressure can be controlled within a preset deformation amount, so that an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap.

[0124] Specifically, in one embodiment, when the rotor 100 rotates in the counterclockwise direction, one end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a stretched state, and the other end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a compressed state, so that the elastic support component 20 is in a taut state. In this way, when the rotor 100 rotates in the counterclockwise direction, the elastic support component 20 is in a taut state, and its inner wall surface has sufficient anti-deformation ability. When the rotor 100 rotates in the clockwise direction, one end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a compressed state, and the other end of the elastic support component 20 is subjected to the rotor tangential force and the air film tangential force and is in a stretched state, so that the elastic support component 20 is in a taut state. In this way, when the rotor 100 rotates in the clockwise direction, the elastic support component 20 is in a taut state.

[0125] Specifically, in one embodiment, the dynamic pressure gas radial bearing includes four elastic support components 20, and the four elastic support components 20 are arranged in the shaft hole at intervals along the circumferential direction of the shaft hole.

[0126] Specifically, in one embodiment, the bearing shell 10 is provided with two first axial grooves 12 extending along its axial direction, and the two ends of the elastic support assembly 20 are respectively provided in the two first axial grooves 12 along the axial direction of the bearing shell 10, and the two first axial grooves 12 are respectively adapted to the two ends of the elastic support assembly 20, and are used to limit the circumferential movement of the elastic support assembly 20. In this way, the elastic support assembly 20 can be inserted into the first axial groove 12 along the axial direction of the bearing shell 10, and the elastic support assembly 20 installed in the first axial groove 12 can also be taken out along the axial direction of the bearing shell 10. Thereby, the disassembly and assembly efficiency of the elastic support assembly 20 is improved.

[0127] Specifically, in one embodiment, the first axial groove 12 includes a first mounting groove 121 and a second mounting groove 122. The elastic support assembly 20 includes a top foil 21 and a wave foil 22. The top foil 21 has two ends respectively arranged in the two first mounting grooves 121, and a wedge-shaped gap is formed between the inner wall surface of the top foil 21 and the outer wall surface of the rotor 100; the wave foil 22 has two ends respectively arranged in the two second mounting grooves 122, and the wave foil 22 is arranged in the top foil 21 to support the top foil 21; when the rotor 100 rotates in the counterclockwise direction, one end of the top foil 21 and the wave foil 22 in the same direction is subjected to the rotor tangential force and the air film tangential force and is in a tensile state, and the other end of the elastic support assembly 20 and the wave foil 22 in the same direction is subjected to the rotor tangential force and the air film tangential force and is in a compressed state. When the rotor 100 rotates in the counterclockwise direction, one end of the top foil 21 and the bump foil 22 in the same direction is in a stretched state due to the rotor tangential force and the air film tangential force, and the other end of the elastic support assembly 20 and the bump foil 22 in the same direction is in a compressed state due to the rotor tangential force and the air film tangential force. In this way, the elastic support assembly 20 is tightened by the receptor deformation at both ends of the top foil 21 and the bump foil 22. This ensures that no matter whether the rotor 100 rotates in the clockwise or counterclockwise direction, an air film for suspending the rotor 100 can be continuously formed in the wedge-shaped gap, thereby realizing the bidirectional suspension function of the dynamic pressure gas radial bearing for the rotor 100.

[0128] Specifically, Figure 1As shown, in one embodiment, the top foil 21 includes a top foil body 211 and two top foil connecting parts 212. The top foil body 211 forms a wedge-shaped gap with the outer wall of the rotor 100; the two top foil connecting parts 212 are respectively arranged at the two ends of the top foil body 211, and the two top foil connecting parts 212 are respectively arranged in the two first mounting grooves 121; when the rotor 100 rotates in the counterclockwise direction, one of the top foil connecting parts 212 is in a tensile state due to the rotor tangential force and the air film tangential force, and the other top foil connecting part 212 is in a compressed state due to the rotor tangential force and the air film tangential force; when the rotor 100 rotates in the clockwise direction, one of the top foil connecting parts 212 is in a compressed state due to the rotor tangential force and the air film tangential force, and the other top foil connecting part 212 is in a tensile state due to the rotor tangential force and the air film tangential force.

[0129] Specifically, in one embodiment, the top foil connection part 212 includes a first top foil stress beam 2121, a second top foil stress beam 2123, and a top foil elastic beam 2122. The second top foil stress beam 2123 is spaced apart from the first top foil stress beam 2121; the top foil elastic beam 2122 is disposed between the first top foil stress beam 2121 and the second top foil stress beam 2123; the first top foil stress beam 2121 and the second top foil stress beam 2123 can be elastically deformed by the rotor tangential force and the air film tangential force, so as to enhance the elastic support strength of the top foil 21.

[0130] Specifically, in one embodiment, the wedge-shaped gap includes a wedge-shaped convergent section 31 and a regulating air film bearing area 32 connected to the wedge-shaped convergent section 31, and the top foil body 211 includes an arc segment 2111 and two fold line segments 2112. Among them, the arc segment 2111 forms the regulating air film bearing area 32 with the outer wall surface of the rotor 100; the two fold line segments 2112 are respectively arranged at the two ends of the arc segment 2111, and the wedge-shaped convergent section 31 is formed between the fold line segment 2112 and the outer wall surface of the rotor 100; the wedge-shaped convergent section 31 is used for air intake, and the regulating air film bearing area 32 is used to form an air film for suspending the rotor 100.

[0131] Specifically, in one embodiment, the fold line segment 2112 includes a first top foil fold 2113 and a second top foil fold 2114. The first top foil fold 2113 is close to the air inlet of the bearing housing 10; one end of the second top foil fold 2114 is connected to the first top foil fold 2113, and the other end of the second top foil fold 2114 is connected to one end of the arc segment 2111; there is a first convergence angle θ1 between the first top foil fold 2113 and the outer wall surface of the rotor 100, and there is a second convergence angle θ2 between the second top foil fold 2114 and the outer wall surface of the rotor 100, and the first convergence angle θ1 is greater than the second convergence angle θ2.

[0132] It should be noted that the first convergence angle θ1 is located at the gas inlet. Setting the first convergence angle θ1 at a larger angle is beneficial to improving the dynamic pressure effect and quickly forming an air film. Setting the second convergence angle θ2 to be smaller than the first convergence angle θ1 is beneficial to reducing airflow turbulence.

[0133] Specifically, in one embodiment, the value range of the first convergence angle θ1 is 1° to 4°.

[0134] Specifically, in one embodiment, the bump foil 22 includes a bump foil body 221 and two bump foil connecting parts 222. The bump foil body 221 is in contact with the top foil body 211 and is used to support the top foil body 211; the two bump foil connecting parts 222 are respectively arranged at the two ends of the bump foil body 221, and the two bump foil connecting parts 222 are respectively arranged in the two second mounting grooves 122; when the rotor 100 rotates in the counterclockwise direction, one of the bump foil connecting parts 222 is in a tensile state due to the rotor tangential force and the air film tangential force, and the other bump foil connecting part 222 is in a compressed state due to the rotor tangential force and the air film tangential force; when the rotor 100 rotates in the clockwise direction, one of the bump foil connecting parts 222 is in a compressed state due to the rotor tangential force and the air film tangential force, and the other bump foil connecting part 222 is in a tensile state due to the rotor tangential force and the air film tangential force.

[0135] In the above arrangement, the two bump foil connecting parts 222 are deformed by force to make the bump foil 22 in a taut state, thereby enhancing the elastic support strength of the bump foil 22 itself, thereby achieving stable elastic support for the top foil 21. This ensures that the bidirectional suspension function of the dynamic pressure gas radial bearing can be realized later.

[0136] Specifically, in one embodiment, the corrugated foil body 221 includes a first corrugated support section 2211, a second corrugated support section 2212 and a third corrugated support section 2213. The first corrugated support section 2211 is in contact with the arc section 2111 and is used to support the arc section 2111; the second corrugated support section 2212 is respectively arranged at both ends of the first corrugated support section 2211, and the second corrugated support section 2212 is used to support the second top foil folding edge 2114; the third corrugated support section 2213 is arranged on one end of the second corrugated support section 2212 away from the first corrugated support section 2211, and the third corrugated support section 2213 is in contact with the first top foil folding edge 2113 and is used to support the first top foil folding edge 2113. In this way, the three corrugated support sections are arranged to support the first and second top foil folding edges and the arc section 2111 one by one. Thereby, stable elastic support for the top foil 21 is achieved.

[0137] Specifically, in one embodiment, the first corrugated support section 2211 includes a plurality of first semi-arc arches connected in sequence, the second corrugated support section 2212 is a single second semi-arc arch, and the third corrugated support section 2213 is a single third semi-arc arch. Among the three semi-arc arches, the first semi-arc arch has the highest height, the third semi-arc arch has the lowest height, and the second semi-arc arch has a middle height.

[0138] Specifically, in one embodiment, the corrugated foil connection part 222 includes a first corrugated foil stress beam 2221, a second corrugated foil stress beam 2223 and a corrugated foil elastic beam 2222. The second corrugated foil stress beam 2223 is spaced apart from the first corrugated foil stress beam 2221; the corrugated foil elastic beam 2222 is disposed between the first corrugated foil stress beam 2221 and the second corrugated foil stress beam 2223; the first corrugated foil stress beam 2221 and the second corrugated foil stress beam 2223 can be elastically deformed by the rotor tangential force and the air film tangential force, so as to enhance the elastic support strength of the inner wall surface of the corrugated foil 22.

[0139] Specifically, in one embodiment, the profiles of the bump foil connecting portion 222 and the top foil connecting portion 212 are in an “M” shape.

[0140] Of course, the contours of the bump foil connection portion 222 and the top foil connection portion 212 may be set to other shapes, such as a “U” shape, according to actual conditions.

[0141] Although the present invention has been described with reference to preferred embodiments, various modifications may be made thereto and parts thereof may be replaced with equivalents without departing from the scope of the present invention. In particular, the various technical features mentioned in the various embodiments may be combined in any manner as long as there is no structural conflict. The present invention is not limited to the specific embodiments disclosed herein, but includes all technical solutions falling within the scope of the claims.

Claims

1. A dynamic pressure gas radial bearing, characterized in that: include: a bearing shell having a shaft hole disposed therein; and An elastic support component is arranged on the inner hole wall of the shaft hole along the circumference of the shaft hole, and two ends of the elastic support component are confined in the bearing shell along the circumference; In which, a rotor is arranged in the elastic support component, and a wedge-shaped gap is formed between the inner wall surface of the elastic support component and the outer wall surface of the rotor. When the rotor rotates in a clockwise or counterclockwise direction, the two ends of the elastic support component are subjected to the action of force and elastically deform, so that the elastic support component is in a taut state. When the elastic support component is in a taut state, the elastic deformation amount of the inner wall surface is within a preset deformation amount, and the wedge-shaped gap is within a preset gap range.

2. The dynamic pressure gas radial bearing according to claim 1, characterized in that: When the rotor rotates in the counterclockwise direction, one end of the elastic support component is in a stretched state due to the rotor tangential force and the air film tangential force, and the other end of the elastic support component is in a compressed state due to the rotor tangential force and the air film tangential force, so that the elastic support component is in the taut state; When the rotor rotates in the clockwise direction, one end of the elastic support component is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support component is in a stretched state due to the tangential force of the rotor and the tangential force of the air film, so that the elastic support component is in the taut state.

3. The dynamic pressure gas radial bearing according to claim 1 or 2, characterized in that: The dynamic pressure gas radial bearing includes a plurality of elastic support components, and the plurality of elastic support components are arranged in the shaft hole at intervals along the circumferential direction of the shaft hole.

4. The dynamic pressure gas radial bearing according to claim 3, characterized in that: The bearing shell is provided with two first axial grooves along its axial extension, and the two ends of the elastic support component are respectively arranged in the two first axial grooves along the axial direction of the bearing shell, and the two first axial grooves are respectively adapted to the two ends of the elastic support component to limit the circumferential movement of the elastic support component.

5. The dynamic pressure gas radial bearing according to claim 4, characterized in that: The first axial groove includes a first mounting groove and a second mounting groove, and the elastic support assembly includes: A top foil, two ends of which are respectively arranged in the two first installation grooves, and a wedge-shaped gap is formed between the inner wall surface of the top foil and the outer wall surface of the rotor; and A corrugated foil, two ends of which are respectively arranged in the two second mounting grooves, and the corrugated foil is arranged in the top foil to support the top foil; Among them, when the rotor rotates in the counterclockwise direction, one end of the top foil and the corrugated foil in the same direction is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support component and the corrugated foil in the same direction is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates in the clockwise direction, one end of the top foil and the corrugated foil in the same direction is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other end of the elastic support component and the corrugated foil in the same direction is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

6. The dynamic pressure gas radial bearing according to claim 5, characterized in that: The top foil comprises: a top foil body, wherein the wedge-shaped gap is formed between the top foil body and the outer wall surface of the rotor; and Two top foil connection parts, which are respectively arranged at two ends of the top foil body, and the two top foil connection parts are respectively arranged in the two first installation grooves; Among them, when the rotor rotates in the counterclockwise direction, one of the top foil connecting parts is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other top foil connecting part is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates in the clockwise direction, one of the top foil connecting parts is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other top foil connecting part is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

7. The dynamic pressure gas radial bearing according to claim 6, characterized in that: The wedge-shaped gap includes a wedge-shaped convergent section and a regulating air film bearing area connected to the wedge-shaped convergent section, and the top foil body includes: an arc segment, which forms the regulating air film bearing area with the outer wall surface of the rotor; and Two broken line segments, which are respectively arranged at two ends of the arc segment, and the wedge-shaped convergent section is formed between the broken line segment and the outer wall surface of the rotor; The wedge-shaped convergent section is used for air intake, and the regulating air film bearing area is used for forming an air film for suspending the rotor.

8. The dynamic pressure gas radial bearing according to claim 7, characterized in that: The broken line segment comprises: a first top foil fold adjacent to the air inlet of the bearing shell; and A second top foil folded edge, one end of which is connected to the first top foil folded edge, and the other end of the second top foil folded edge is connected to one end of the arc segment; There is a first convergence angle θ1 between the first top foil folded edge and the outer wall surface of the rotor, there is a second convergence angle θ2 between the second top foil folded edge and the outer wall surface of the rotor, and the first convergence angle θ1 is greater than the second convergence angle θ2.

9. The dynamic pressure gas radial bearing according to claim 8, characterized in that: The bump foil comprises: a corrugated foil body, which contacts the top foil body and is used to support the top foil body; and Two corrugated foil connecting parts are respectively arranged at two ends of the corrugated foil body, and the two corrugated foil connecting parts are respectively arranged in the two second mounting grooves; Among them, when the rotor rotates in the counterclockwise direction, one of the corrugated foil connecting parts is in a tensile state due to the tangential force of the rotor and the tangential force of the air film, and the other corrugated foil connecting part is in a compressed state due to the tangential force of the rotor and the tangential force of the air film; when the rotor rotates in the clockwise direction, one of the corrugated foil connecting parts is in a compressed state due to the tangential force of the rotor and the tangential force of the air film, and the other corrugated foil connecting part is in a tensile state due to the tangential force of the rotor and the tangential force of the air film.

10. The dynamic pressure gas radial bearing according to claim 9, characterized in that: The wave foil body comprises: a first corrugated support segment, which contacts the arc segment and is used to support the arc segment; and A second corrugated support segment, which is respectively arranged at both ends of the first corrugated support segment, and the second corrugated support segment is used to support the second top foil folded edge; and A third corrugated support segment is arranged on one end of the second corrugated support segment away from the first corrugated support segment, and the third corrugated support segment is in contact with the first top foil folded edge to support the first top foil folded edge.

11. The dynamic pressure gas radial bearing according to claim 9, characterized in that: The corrugated foil connecting portion comprises: one or more first foil load bearing beams; and one or more second corrugated foil stress beams, which are spaced apart from the first corrugated foil stress beams; and One or more corrugated foil elastic beams, which are arranged between the first corrugated foil stress beam and the second corrugated foil stress beam; The first corrugated foil stress beam and the second corrugated foil stress beam can be elastically deformed by the rotor tangential force and the air film tangential force, so as to enhance the elastic support strength of the inner wall surface of the corrugated foil.

12. The dynamic pressure gas radial bearing according to claim 11, characterized in that: The profile of the corrugated foil connecting portion is in an "N" shape, an "M" shape, or a "U" shape.

13. The dynamic pressure gas radial bearing according to claim 7, characterized in that: The dynamic pressure gas radial bearing also includes an elastic adjustment member, which is arranged in the bearing shell and is used to radially compress the arc segment toward the central axis of the axial hole to increase the length of the wedge-shaped convergent section and the gas flow channel in the regulating air film bearing area.

14. The dynamic pressure gas radial bearing according to claim 13, characterized in that: The bearing shell is provided with a second axial groove extending along the axial direction thereof, and the elastic adjustment member is arranged in the second axial groove along the axial direction of the bearing shell.

15. The dynamic pressure gas radial bearing according to claim 14, characterized in that: The contour of the elastic adjusting member is in a "Z" shape, and the second axial groove is a "Z" shaped groove matched with the elastic adjusting member.

16. The dynamic pressure gas radial bearing according to claim 6, characterized in that: The top foil connecting portion comprises: a first top foil load bearing beam; and a second top foil stress beam, which is spaced apart from the first top foil stress beam; and A top foil elastic beam, which is arranged between the first top foil stress beam and the second top foil stress beam; The first top foil stress beam and the second top foil stress beam can be elastically deformed by the rotor tangential force and the air film tangential force, so as to enhance the elastic support strength of the top foil.

17. The dynamic pressure gas radial bearing according to claim 16, characterized in that: The top foil connecting portion has an "N"-shaped configuration, an "M"-shaped configuration, or a "U"-shaped configuration.

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