CN211398265U - Radial gas bearing, compressor and air conditioning unit - Google Patents
Radial gas bearing, compressor and air conditioning unit Download PDFInfo
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- CN211398265U CN211398265U CN202020041899.2U CN202020041899U CN211398265U CN 211398265 U CN211398265 U CN 211398265U CN 202020041899 U CN202020041899 U CN 202020041899U CN 211398265 U CN211398265 U CN 211398265U
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Abstract
The utility model relates to a radial gas bearing, compressor and air conditioning unit, wherein radial gas bearing includes bearing housing (20), top foil (40) and ripples foil (50), ripples foil (50) set up between bearing housing (20) and top foil (40), ripples foil (50) are including first bearing segment (51) and second bearing segment (52) of arranging along the circumference of bearing housing (20), first bearing segment (51) and second bearing segment (52) are constructed and are absorbed the effort that comes from top foil (40) transmission at least partially, the compressive capacity of first bearing segment (51) is different with the compressive capacity of second bearing segment (52). The utility model discloses the ripples paper tinsel includes first pressure-bearing section and the second pressure-bearing section that compressive capacity is different, through the mode that sets up different pressure-bearing sections in week for the bearing has different bearing rigidity, improves the adaptability of bearing to different radial load, makes the bearing adapt to the different operating condition of compressor better.
Description
Technical Field
The utility model relates to a bearing technical field especially relates to a radial gas bearing, compressor and air conditioning unit.
Background
The bearing is a basic part for supporting the rotor to do mechanical rotation, and the current commonly used bearings comprise a rolling bearing, a sliding bearing, a magnetic suspension bearing and the like. Since the 60 s of the 20 th century, the gas suspension bearing is gradually developed and applied along with the development of the transmission machinery industry towards high rotating speed, high precision and the like.
The air suspension bearing is divided into a static pressure air bearing and a dynamic pressure air bearing. The static pressure gas bearing uses gas as a lubricating medium for the movement of the static pressure gas bearing, the gas is supplied by an external gas supply source and enters a lubricating gap on the surface of the bearing through a throttling layer to form a gas film, so that the gas film pressure is generated between the bearing and the surface of a shaft for supporting.
The dynamic pressure gas bearing is a self-acting pressure type flexible bearing, runs by depending on a layer of lubricating gas film formed by the dynamic pressure gas bearing, the principle is a dynamic pressure principle, and the necessary conditions for forming the lubricating gas film are three: the wedge-shaped gap between the two working surfaces must be formed, the gas with certain viscosity must be filled between the two working surfaces, the relative sliding speed must be formed between the two working surfaces, and the moving direction must ensure that the gas flows in from the large section of the wedge shape and flows out from the small section. The working surface is the inner surface of the bearing and the outer surface of the rotor which forms clearance fit with the inner surface of the bearing. When the dynamic pressure gas bearing works, the rotating shaft is eccentric relative to the bearing under the action of gravity, and a wedge-shaped gap is formed between the rotating shaft and the inner surface of the bearing. When the rotating shaft rotates at a high speed, gas with certain viscosity is continuously brought into the wedge-shaped gap, the gas continuously enters the wedge-shaped gap to enable the gas film to generate certain pressure, and when the gas film force is enough to balance the load of the rotating shaft, the shaft is completely separated from the bearing.
The foil dynamical pressure gas bearing is a common form of the dynamical pressure gas bearing, and the common foil dynamical pressure gas bearing consists of a bearing shell, a top foil and a wave foil, wherein the bearing shell plays a supporting role, the top foil is matched with a rotor to form a gap and a working surface with a relative movement speed, and the wave foil is an elastic foil with a corrugated shape and provides partial rigidity and damping for the bearing.
The existing foil dynamical pressure gas bearing has the following two problems:
1. the top foil is in clearance fit with the surface of the corresponding rotor, the clearance is a forming space of the dynamic pressure gas film, in order to ensure the fit clearance, the top foil is generally formed by a curled foil, the section of the top foil is circular, the rigidity of the top foil is very limited, and extra rigidity can not be provided for the bearing;
2. the bump foil plays a crucial role in the stability of the rotor, and most of the stiffness and damping of the bearing comes from the bump foil. With the progress of science and technology, most motors adopt variable frequency motors, the rotating speed of a rotor can be subjected to stepless speed regulation during working, and the bearing rigidity and the damping required by a rotor system are also changed along with the change of the rotating speed, so that higher requirements are provided for a bearing, and the bearing is required to be capable of adapting to the change. In the prior art, the wave foil generally adopts double-layer or multi-layer elastic foils with corrugated shapes to realize double-rigidity or multi-rigidity support, but the double-layer or multi-layer foils limit the realization of the miniaturization of the bearing structure, and meanwhile, the multi-layer foils relate to the coupling effect among the foils of each layer, so that the design difficulty, the processing difficulty and the assembly difficulty are greatly improved.
For this reason, there is a need for an improved hydrodynamic gas bearing to improve the reliability of the hydrodynamic gas bearing.
It is noted that the information disclosed in this background section of the invention is only for enhancement of understanding of the general background of the invention, and should not be taken as an acknowledgement or any form of suggestion that this information constitutes prior art already known to a person skilled in the art.
SUMMERY OF THE UTILITY MODEL
The utility model aims at providing a radial gas bearing, compressor and air conditioning unit improve radial gas bearing's adaptability.
In order to achieve the above object, the present invention provides a radial gas bearing, including:
a bearing housing;
a top foil; and
and a wave foil disposed between the bearing housing and the top foil, the wave foil including first and second bearing segments arranged along a circumference of the bearing housing, the first and second bearing segments being configured to at least partially absorb a force transmitted from the top foil, a pressure-resistant capacity of the first bearing segment being different from a pressure-resistant capacity of the second bearing segment.
In some embodiments, the first and second bearing segments are convex with respect to the bearing housing in a direction away from the bearing housing, and a radial distance between the first bearing segment and the bearing housing is different from a radial distance between the second bearing segment and the bearing housing.
In some embodiments, the first and second bearing segments are convex with respect to the bearing housing in a direction away from the bearing housing, and a projected length of the first bearing segment on a circumferential side of the bearing housing is different from a projected length of the second bearing segment on the circumferential side of the bearing housing.
In some embodiments, a side of the first bearing segment remote from the bearing housing and a side of the second bearing segment remote from the bearing housing are both in contact with the top foil.
In some embodiments, the top foil comprises a first support section in contact with a side of the first bearing section remote from the bearing housing, a second support section in contact with a side of the second bearing section remote from the bearing housing, and a first connection section connected between the first support section and the second support section.
In some embodiments, the first connection section is inclined relative to both the first support section and the second support section.
In some embodiments, two first connection sections respectively connected to both ends of the first support section are symmetrically arranged with respect to the first support section.
In some embodiments, the radial distance between the first bearing section and the bearing housing is smaller than the radial distance between the second bearing section and the bearing housing, and the side of the second support section away from the bearing housing is provided with a solid lubricant.
In some embodiments, the number of the first pressure-bearing section and the second pressure-bearing section is multiple, and the first pressure-bearing section and the second pressure-bearing section are arranged at intervals.
In some embodiments, the wave foil further comprises a second connecting section connecting the first bearing section and the second bearing section, the second connecting section being in contact with the inner wall of the bearing housing.
In order to achieve the above object, the present invention further provides a compressor, including the above radial gas bearing.
In order to achieve the above object, the present invention further provides an air conditioning unit, including the above compressor.
Based on the technical scheme, the embodiment of the utility model provides an in ripples paper tinsel include the first pressure-bearing section and the second pressure-bearing section that compressive capacity is different, through the mode that sets up different pressure-bearing sections in week for the bearing has different bearing rigidity, improves the adaptability of bearing to different radial load, makes the bearing adapt to the different operating condition of compressor better.
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 undue limitation to the invention. In the drawings:
fig. 1 is a schematic diagram of an embodiment of the radial gas bearing of the present invention.
Fig. 2 is a schematic structural diagram of an embodiment of the radial gas bearing of the present invention.
Fig. 3 is an axial side view of an embodiment of the radial gas bearing of the present invention.
Fig. 4 is an enlarged view of the reference portion P in fig. 3.
Fig. 5 is a schematic structural diagram of a bump foil in an embodiment of the radial gas bearing of the present invention.
Fig. 6 is a schematic structural diagram of a top foil in an embodiment of the radial gas bearing of the present invention.
In the figure:
10. a rotating shaft; 20. a bearing housing; 21. positioning a groove; 30. a gas film gap; 40. a top foil; 50. a bump foil; 60. positioning pins;
41. a first support section; 42. a second support section; 43. a first connection section;
51. a first pressure-bearing section; 52. a second pressure-bearing section; 53. a second connection section.
Detailed Description
The technical solutions in the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings in the embodiments of the present invention. It is obvious that the described embodiments are only some of the embodiments of the present invention, and not all of them. Based on the embodiments of the present invention, all other embodiments obtained by a person of ordinary skill in the art without creative efforts belong to the protection scope of the present invention.
In the description of the present invention, it is to be understood that the terms "center", "lateral", "longitudinal", "front", "rear", "left", "right", "up", "down", "vertical", "horizontal", "top", "bottom", "inner", "outer", and the like indicate orientations or positional relationships based on those shown in the drawings, and are used only for convenience of description and simplicity of description, and do not indicate or imply that the device or element being referred to must have a particular orientation, be constructed and operated in a particular orientation, and therefore, should not be construed as limiting the scope of the invention.
As shown in fig. 1, the radial gas bearing includes a bearing housing 20, the bearing housing 20 is disposed at a radial outer periphery of a rotating shaft 10 supported by the bearing, and a gas film gap 30 is provided between an inner wall of the bearing housing 20 and an outer wall of the rotating shaft 10. When the compressor is operated, the gas enters the gas film gap 30 to form a dynamic pressure gas film, thereby suspending the rotating shaft 10.
As shown in fig. 2 and 3, in one embodiment of the radial gas bearing provided by the present invention, the radial gas bearing includes a bearing housing 20, a top foil 40, and a wave foil 50, the wave foil 50 being disposed between the bearing housing 20 and the top foil 40. The top foil 40 and the bump foil 50 may be fixed to the bearing housing 20, respectively. The bearing housing 20 has a through hole at the center, the bump foil 50 and the top foil 40 are both disposed on the wall of the through hole, and the rotating shaft 10 is located at the radial inner side of the top foil 40 to form a radial support for the rotating shaft 10.
As shown in fig. 4, the wave foil 50 includes a first bearing segment 51 and a second bearing segment 52 arranged along the circumferential direction of the bearing housing 20, the first bearing segment 51 and the second bearing segment 52 are respectively located at different circumferential positions of the bearing housing 20, the first bearing segment 51 and the second bearing segment 52 are configured to at least partially absorb the force transmitted from the top foil 40, and the pressure resistance of the first bearing segment 51 is different from that of the second bearing segment 52.
In the above embodiment, the wave foil 50 includes the first pressure-bearing section 51 and the second pressure-bearing section 52 with different pressure-bearing capacities, and the bearing has different bearing stiffnesses by arranging different pressure-bearing sections in the circumferential direction, so that the adaptability of the bearing to different radial loads is improved, and the bearing can better adapt to different operation conditions of the compressor.
In other embodiments, the bump foil 50 may also include three or more pressure-bearing segments having different pressure-bearing capacities.
In order to realize that the pressure resistance of the first pressure-bearing section 51 is different from that of the second pressure-bearing section 52, the first pressure-bearing section 51 and the second pressure-bearing section 52 may be protruded in a direction away from the bearing housing 20 with respect to the bearing housing 20, and a radial distance between the first pressure-bearing section 51 and the bearing housing 20 is different from a radial distance between the second pressure-bearing section 52 and the bearing housing 20. The smaller the radial distance between the bearing segment and the bearing housing 20, the stronger the pressure resistance of the bearing segment.
Referring to fig. 5, the first pressure-containing section 51 and the second pressure-containing section 52 are both arch-shaped, the radial distance between the first pressure-containing section 51 and the bearing housing 20 is L3, and the radial distance between the second pressure-containing section 52 and the bearing housing 20 is L1, wherein L3< L1, and the pressure-resistant capacity of the first pressure-containing section 51 is greater than that of the second pressure-containing section 52.
In order to realize that the pressure resistance of the first pressure-bearing section 51 is different from that of the second pressure-bearing section 52, the first pressure-bearing section 51 and the second pressure-bearing section 52 may be protruded in a direction away from the bearing housing 20 relative to the bearing housing 20, and a projection length of the first pressure-bearing section 51 on the circumferential side surface of the bearing housing 20 is different from a projection length of the second pressure-bearing section 52 on the circumferential side surface of the bearing housing 20. The smaller the projected length of the bearing segment on the circumferential side of the bearing housing 20, the stronger the pressure resistance of the bearing segment.
Referring to fig. 5, the first bearing segment 51 and the second bearing segment 52 are both arch-shaped, the span of the first bearing segment 51 is L4, the span of the second bearing segment 52 is L2, wherein L4< L2, and the pressure resistance of the first bearing segment 51 is greater than that of the second bearing segment 52.
In fact, in the embodiment shown in fig. 5, the first pressure-containing section 51 and the second pressure-containing section 52 are both arch-shaped, the radial distance between the first pressure-containing section 51 and the bearing housing 20 is smaller than the radial distance between the second pressure-containing section 52 and the bearing housing 20, and the span of the first pressure-containing section 51 is smaller than the span of the second pressure-containing section 52, so that the pressure-resisting capacity of the first pressure-containing section 51 is greater than that of the second pressure-containing section 52.
When the radial distance between the first bearing segment 51 and the bearing housing 20 is different from the radial distance between the second bearing segment 52 and the bearing housing 20, it is still necessary to make both the side of the first bearing segment 51 away from the bearing housing 20 and the side of the second bearing segment 52 away from the bearing housing 20 contact with the top foil 40, so as to ensure the contact between the top foil 40 and each bearing segment, ensure the smooth transmission of pressure, and avoid instability caused by the non-contact between the top foil 40 and the bearing segment.
As shown in fig. 4 and 6, the top foil 40 includes a first support section 41, a second support section 42, and a first connection section 43, the first support section 41 being in contact with a side of the first bearing section 51 away from the bearing housing 20, the second support section 42 being in contact with a side of the second bearing section 52 away from the bearing housing 20, the first connection section 43 being connected between the first support section 41 and the second support section 42.
Since the radial distance between the first bearing section 51 and the bearing housing 20 is different from the radial distance between the second bearing section 52 and the bearing housing 20, a certain height difference exists between the first support section 41 and the second support section 42, the transition between the first support section 41 and the second support section 42 can be realized by arranging the first connecting section 43, and the plurality of first connecting sections 43 connect the plurality of first support sections 41 and the plurality of second support sections 42 in series to form the circumferentially continuous top foil 40.
The first connecting section 43 is inclined with respect to both the first support section 41 and the second support section 42. This has the advantage that the air flow can be made to pass between the side of the first support section 41 close to the rotating shaft 10 and the side of the second support section 42 close to the rotating shaft 10 in order, and the air flow is prevented from forming turbulence in the transition region and affecting the smooth operation of the rotating shaft. Meanwhile, the first connecting section 43 is obliquely arranged to form an air film converging section, so that air flow flows from a large section to a small section when moving from the side surface of the first supporting section 41 to the side surface of the second supporting section 42, a dynamic pressure air film is formed in the full circumferential range of the top foil 40, the structural rigidity of the top foil 40 is effectively combined with the rigidity of the air film, and the bearing capacity of the bearing is improved.
A first connecting section 43 is connected to each end of the first supporting section 41, the first connecting section 43 connected to the upstream of the first supporting section 41 is used to connect the first supporting section 41 and the second supporting section 42 located at the upstream of the first supporting section 41, and the first connecting section 43 connected to the downstream of the first supporting section 41 is used to connect the first supporting section 41 and the second supporting section 42 located at the downstream of the first supporting section 41. The two first connection sections 43 respectively connected to both ends of the first support section 41 are symmetrically arranged, that is, the two first connection sections 43 are symmetrically arranged at both ends of the first support section 41.
For the second supporting section 42, a first connecting section 43 is connected to each end of the second supporting section 42, the first connecting section 43 connected to the upstream of the second supporting section 42 is used for connecting the second supporting section 42 and the first supporting section 41 located at the upstream of the second supporting section 42, and the first connecting section 43 connected to the downstream of the second supporting section 42 is used for connecting the second supporting section 42 and the first supporting section 41 located at the downstream of the second supporting section 42. The two first connection sections 43 respectively connected to both ends of the second support section 42 are symmetrically arranged, that is, the two first connection sections 43 are symmetrically arranged at both ends of the second support section 42.
As shown in fig. 4, the included angle θ 1 between the first connecting section 43 and the second supporting section 42 located upstream of the first supporting section 41 is equal to the included angle θ 2 between the first connecting section 43 and the second supporting section 42 located downstream of the first supporting section 41.
The radial distance between the first bearing section 51 and the bearing housing 20 is smaller than the radial distance between the second bearing section 52 and the bearing housing 20, and the side of the second support section 42 away from the bearing housing 20 is provided with a solid lubricant. At the start and stop stages of the rotating shaft 10, due to reasons such as insufficient rotating speed, the air film is difficult to form, dry friction is formed by contact between the top foil 40 and the rotating shaft 10, at the moment, the second supporting section 42 mainly plays a supporting role, and the solid lubricant is arranged on one side, far away from the bearing shell 20, of the second supporting section 42, so that abrasion between the rotating shaft 10 and the bearing shell 20 can be reduced, and the service life of the rotating shaft 10 and the bearing shell 20 is prolonged.
In the above embodiments, the number of the first bearing segments 51 and the second bearing segments 52 is plural, and the first bearing segments 51 and the second bearing segments 52 are arranged at intervals. This arrangement ensures that the pressure-bearing capacity of the bump foil 50 in the circumferential direction is relatively uniform.
A plurality of first and second bearing segments 51 and 52 are connected to form a single layer of corrugated foil 50.
The bump foil 50 further includes a second connection section 53 connecting the first bearing section 51 and the second bearing section 52, the second connection section 53 being in contact with the inner wall of the bearing housing 20.
The radial gas bearing comprises at least two sections of corrugated foils 50 arranged along the circumference of the bearing housing 20 with a gap between adjacent sections of corrugated foils 50.
The bearing housing 20 is provided at an inner side thereof with a positioning groove 21, and the bearing further includes a positioning pin 60, and one ends of the top foil 40 and the bump foil 50 are inserted into the positioning groove 21 and fixed by the positioning pin 60. By providing the positioning groove 21 and the positioning pin 60, the fixing of the top foil 40 and the bump foil 50 is achieved.
Further, the downstream end of the top foil 40 and the downstream end of the wave foil 50 are inserted into the positioning groove 21, and the upstream end of the top foil 40 and the upstream end of the wave foil 50 are both free ends, so that the top foil 40 and the wave foil 50 can have a certain degree of freedom of deformation, and the reduction of the pressure resistance of the top foil 40 and the wave foil 50 when the rotating shaft 10 rotates can be avoided.
The inner side of the bearing housing 20 is further provided with a mounting hole for mounting the positioning pin 60, and the mounting hole is disposed at the side of the positioning groove 21 and communicated with the positioning groove 21. Thus, after the positioning pin 60 is inserted into the mounting hole, the part of the positioning pin 60 exposed out of the mounting hole just enters the positioning groove 21 to press the top foil 40 and the bump foil 50, so that the top foil 40 and the bump foil 50 are fixed.
The structure and operation of an embodiment of the radial gas bearing of the present invention will be described below with reference to fig. 1 to 6:
as shown in fig. 1, the radial gas bearing includes a bearing housing 20, the bearing housing 20 is disposed at the outer circumference of the rotating shaft 10, and a gas film gap 30 is provided between the inner wall of the bearing housing 20 and the outer wall of the rotating shaft 10. The bearing housing 20 and the rotating shaft 10 are circular in cross section.
As shown in fig. 2 and 3, the top foil 40 and the bump foil 50 are each disposed between the inner wall of the bearing housing 20 and the outer wall of the rotating shaft 10, and the bump foil 50 is located between the bearing housing 20 and the top foil 40.
The bump foil 50 and the top foil 40 are both single-layer foils. The number of the wave foils 50 is 3, and the 3 wave foils 50 are arranged along the circumferential direction of the bearing shell 20, and a gap is formed between two adjacent wave foils 50. The top foil 40 is circumferentially continuous with a gap between the ends.
The downstream ends of the top foil 40 and the bump foil 50 are inserted into the positioning groove 21 and fixed by the positioning pin 60. The positioning groove 21 is provided in the inner wall of the bearing housing 20 and extends radially outward from the inner wall surface. The inner wall of the bearing housing 20 is further provided with a mounting hole extending in the axial direction of the bearing housing 20, the mounting hole communicating with the positioning groove 21, and the positioning pin 60 inserted into the mounting hole and press-fixing the top foil 40 and the bump foil 50 through a portion exposed out of the mounting hole.
As shown in fig. 4, 5 and 6, the wave foil 50 includes a first bearing segment 51, a second bearing segment 52 and a second connecting segment 53 connected between the first bearing segment 51 and the second bearing segment 52, and the first bearing segment 51 and the second bearing segment 52 are both in an arch shape, and the arch shape is opened toward the bearing housing 20. The height L3 of the first pressure section 51 is less than the height L1 of the second pressure section 52, and the span L4 of the first pressure section 51 is less than the span L2 of the second pressure section 52. The second connecting section 53 is in tangential contact with the inner wall of the bearing housing 20.
The first pressure-bearing section 51 and the second pressure-bearing section 52 in each section of the wave foil 50 are arranged at intervals.
The top foil 40 comprises a first support section 41 in contact and tangent with a first bearing section 51 and a second support section 42 in contact and tangent with a second bearing section 52 and a first connecting section 43 connecting the first support section 41 and the second support section 42. Two first connection sections 43 connected at both ends of the first support section 41 are symmetrically arranged about the center of the first support section 41.
The first supporting section 41 and the second supporting section 42 are both arc-shaped with a smaller radian, the first connecting section 43 is obliquely arranged, and an included angle theta 1 between the upstream first connecting section 43 and the second supporting section 42 is equal to an included angle theta 2 between the downstream first connecting section 43 and the second supporting section 42.
During operation, when the rotating speed of the rotating shaft 10 is low, the second pressure-bearing section 52 is easier to deform than the first pressure-bearing section 51 due to low pressure-bearing capacity, and the support required by the rotating shaft 10 is mainly provided by the second pressure-bearing section 52; when the rotating speed of the rotating shaft 10 increases, the deformation of the second pressure-bearing section 52 is increased, and at this time, the first pressure-bearing section 51 starts to participate in providing support, so that a single-layer foil dual-rigidity coupling support shaft system is realized, and the load-changing adaptability of the radial gas bearing is improved.
As shown in fig. 4, when a dynamic pressure gas film with a certain viscosity flows from the side of the first support section 41 to the side of the second support section 42, under the action of the convergence angle θ 1, the gas flows from the large section to the small section to form a dynamic pressure gas film, and finally flows to the side of the next first support section 41, so that the dynamic pressure gas film is formed in the full circumference range of the top foil 40, and the structural rigidity and the gas film rigidity of the top foil 40 are effectively combined to provide additional rigidity and damping for the bearing.
When the rotation shaft 10 rotates reversely, the flow of the gas from the large cross section to the small cross section is realized by the convergent angle θ 2, and a dynamic pressure film is formed.
Based on foretell radial gas bearing, the utility model discloses still provide a compressor, this compressor includes foretell radial gas bearing. The compressor further includes a rotating shaft 10, a radial gas bearing is disposed at a radial outer periphery of the rotating shaft 10, the radial gas bearing is used for supporting the rotating shaft 10, a gas film gap 30 is formed between a top foil 40 of the radial gas bearing and the rotating shaft 10, and when the compressor is in operation, gas enters the gas film gap 30 to form a dynamic pressure gas film, so that the rotating shaft 10 is suspended.
Based on foretell compressor, the utility model discloses still provide an air conditioning unit, this air conditioning unit includes foretell compressor.
The positive technical effects of the radial gas bearing in the above embodiments are also applicable to the compressor and the air conditioning unit, and are not described herein again.
Finally, it should be noted that: the above embodiments are only used to illustrate the technical solution of the present invention and not to limit it; although the present invention has been described in detail with reference to preferred embodiments, it should be understood by those skilled in the art that: the utility model discloses a do not deviate from under the prerequisite of the principle, still can be right the utility model discloses a specific embodiment modifies or carries out the equivalent replacement to some technical features, and these are modified and should be covered with the equivalent replacement in the middle of the technical scheme scope of the utility model.
Claims (12)
1. A radial gas bearing, comprising:
a bearing housing (20);
a top foil (40); and
a wave foil (50) disposed between the bearing housing (20) and the top foil (40), the wave foil (50) comprising a first bearing section (51) and a second bearing section (52) arranged along a circumference of the bearing housing (20), the first bearing section (51) and the second bearing section (52) being configured to at least partially absorb a force transmitted from the top foil (40), a pressure resistance of the first bearing section (51) being different from a pressure resistance of the second bearing section (52).
2. Radial gas bearing according to claim 1, wherein the first bearing segment (51) and the second bearing segment (52) are convex with respect to the bearing housing (20) in a direction away from the bearing housing (20), the radial distance between the first bearing segment (51) and the bearing housing (20) being different from the radial distance between the second bearing segment (52) and the bearing housing (20).
3. Radial gas bearing according to claim 1 or 2, wherein the first bearing segment (51) and the second bearing segment (52) are convex with respect to the bearing housing (20) in a direction away from the bearing housing (20), the projected length of the first bearing segment (51) on the circumferential side of the bearing housing (20) and the projected length of the second bearing segment (52) on the circumferential side of the bearing housing (20) being different.
4. Radial gas bearing according to claim 2, wherein both a side of the first bearing segment (51) facing away from the bearing housing (20) and a side of the second bearing segment (52) facing away from the bearing housing (20) are in contact with the top foil (40).
5. Radial gas bearing according to claim 2, wherein the top foil (40) comprises a first support section (41), a second support section (42) and a first connection section (43), the first support section (41) being in contact with a side of the first bearing section (51) remote from the bearing housing (20), the second support section (42) being in contact with a side of the second bearing section (52) remote from the bearing housing (20), the first connection section (43) being connected between the first support section (41) and the second support section (42).
6. Radial gas bearing according to claim 5, wherein the first connection section (43) is inclined with respect to both the first support section (41) and the second support section (42).
7. Radial gas bearing according to claim 6, wherein two first connection segments (43) connected at both ends of the first support segment (41), respectively, are arranged symmetrically.
8. The radial gas bearing according to claim 5, characterized in that the radial distance between the first bearing segment (51) and the bearing housing (20) is smaller than the radial distance between the second bearing segment (52) and the bearing housing (20), and that the side of the second support segment (42) facing away from the bearing housing (20) is provided with a solid lubricant.
9. Radial gas bearing according to claim 1, wherein the number of said first bearing segments (51) and said second bearing segments (52) is plural, said first bearing segments (51) and said second bearing segments (52) being arranged at intervals.
10. Radial gas bearing according to claim 1, wherein the wave foil (50) further comprises a second connection section (53) connecting the first bearing section (51) and the second bearing section (52), the second connection section (53) being in contact with an inner wall of the bearing housing (20).
11. A compressor comprising a radial gas bearing according to any one of claims 1 to 10.
12. An air conditioning assembly, characterized in that it comprises a compressor according to claim 11.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020041899.2U CN211398265U (en) | 2020-01-09 | 2020-01-09 | Radial gas bearing, compressor and air conditioning unit |
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| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| CN202020041899.2U CN211398265U (en) | 2020-01-09 | 2020-01-09 | Radial gas bearing, compressor and air conditioning unit |
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| CN211398265U true CN211398265U (en) | 2020-09-01 |
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| CN202020041899.2U Active CN211398265U (en) | 2020-01-09 | 2020-01-09 | Radial gas bearing, compressor and air conditioning unit |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| CN115076220A (en) * | 2022-07-30 | 2022-09-20 | 广东美的暖通设备有限公司 | Air bearing, rotor assembly, compressor and heating and ventilation equipment |
| CN116733837A (en) * | 2023-08-15 | 2023-09-12 | 江苏海拓宾未来工业科技集团有限公司 | Air dynamic pressure foil bearing, suspension centrifugal blower comprising same and processing technology |
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2020
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN115076220A (en) * | 2022-07-30 | 2022-09-20 | 广东美的暖通设备有限公司 | Air bearing, rotor assembly, compressor and heating and ventilation equipment |
| CN115076220B (en) * | 2022-07-30 | 2024-04-26 | 广东美的暖通设备有限公司 | Air bearing, rotor assembly, compressor and heating and ventilation equipment |
| CN116733837A (en) * | 2023-08-15 | 2023-09-12 | 江苏海拓宾未来工业科技集团有限公司 | Air dynamic pressure foil bearing, suspension centrifugal blower comprising same and processing technology |
| CN116733837B (en) * | 2023-08-15 | 2023-11-21 | 江苏海拓宾未来工业科技集团有限公司 | Air dynamic pressure foil bearing, suspension centrifugal blower comprising same and processing technology |
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