Gas bearing and compressor

Abstract

The utility model provides a gas bearing and a compressor. The gas bearing comprises a bearing support; the first bearing shell is arranged in the bearing support, and a first-stage damping structure is arranged between the outer wall of the first bearing shell and the inner wall of the bearing support; and the second bearing shell is arranged in the first bearing sleeve shell, and a secondary damping structure is arranged between the outer wall of the second bearing shell and the inner wall of the first bearing shell. According to the gas bearing and the compressor provided by the utility model, the first-stage damping structure and the second-stage damping structure are arranged, so that impact, load and the like suffered by the rotor can be buffered, and the influence of the impact and the load on the bearing and the compressor is reduced; in addition, the problem of local abrasion caused by uneven stress at the two ends of the bearing due to inclination of the rotor can be further reduced, and the reliability and stability of the gas bearing and the compressor are further improved.

Description

Technical Field

[0001] The utility model relates to the technical field of compression equipment, in particular to a gas bearing and a compressor. Background Art

[0002] Centrifugal chillers are widely used in large public buildings, comfort air conditioning, data centers, district energy, and heat pumps. Their energy efficiency has a significant impact on public building energy consumption. Compressors, as a general power source, are widely used in centrifugal chillers.

[0003] For air-suspended centrifugal compressors, the air bearing is a core component that determines its safe and stable operation. The stability and reliability of the air bearing directly affect the performance of the centrifugal compressor. Compared with dynamic air bearings, static air bearings have attracted widespread attention for their stronger load-bearing capacity. The reliability and stability of static air suspension are affected by many factors, such as support method, rotational speed, and air flow rate. The structure of the bearing has a significant impact on its performance. During operation, the rotor assembly is subject to certain loads and radial impacts. Large impact loads can affect the operating performance and reliability of the bearings. In severe cases, the shaft can become stuck and the motor can burn out, which in turn affects the operating performance and life of the compressor. Utility Model Content

[0004] In order to solve the technical problem in the prior art that static pressure air suspension bearings may get stuck when subjected to impact or load, thereby affecting the reliability of the compressor, a gas bearing and compressor are provided with a secondary damping structure for buffering to improve the impact resistance and thus improve the reliability.

[0005] A gas bearing comprising:

[0006] Bearing support;

[0007] a first bearing housing, wherein the first bearing housing is disposed in the bearing support, and a primary damping structure is disposed between an outer wall of the first bearing housing and an inner wall of the bearing support;

[0008] The second bearing housing is arranged in the first bearing sleeve housing, and a secondary damping structure is provided between the outer wall of the second bearing housing and the inner wall of the first bearing housing.

[0009] The primary damping structure includes a wave foil structure, which is annularly surrounded on the first bearing shell, and the wave crests of the wave foil structure abut against the bearing support, and the wave troughs of the wave foil structure abut against the first bearing shell.

[0010] The corrugated foil structure has a first end and a second end in a length direction, the first end is arranged on the bearing support, and the second end is movably located between the bearing support and the first bearing housing.

[0011] The thickness L3 of the corrugated foil structure has a numerical range of 0.1 mm to 0.5 mm; and / or the pitch L4 between two adjacent wave crests of the corrugated foil structure has a numerical range of 2 mm to 8 mm; and / or the height L5 of a single wave between a wave crest and a wave trough of the corrugated foil structure has a numerical range of 1.5 mm to 3 mm.

[0012] The number of the corrugated foil structures is at least two, and all the corrugated foil structures are arranged in parallel along the axis direction of the gas bearing.

[0013] There is a seam distance between two adjacent corrugated foil structures. The relationship among the seam distance L6, the number n of the corrugated foil structures and the axial length L2 of the gas bearing is: L2=L6*n*(20-50).

[0014] The secondary damping structure includes a damping ring, which surrounds the outer wall of the second bearing shell, and the outer wall of the damping ring is in abutment with the first bearing shell.

[0015] The number of the damping rings is at least two, and all the damping rings are arranged in parallel along the axis direction of the gas bearing.

[0016] The gas bearing has a first portion, a middle portion, and a second portion distributed in an axial direction. At least one damping ring is located at the first portion, and at least one damping ring is located at the second portion.

[0017] The thickness L1 of the damping ring ranges from 2.6 mm to 5.3 mm.

[0018] The gas bearing further includes a porous structure disposed within the second bearing housing.

[0019] The gas bearing further comprises a retaining ring, which is arranged at the end of the first bearing housing and abuts against the second bearing housing; or, the retaining ring is arranged at the end of the second bearing housing and abuts against the first bearing housing.

[0020] A compressor comprises the above-mentioned gas bearing.

[0021] The gas bearing and compressor provided by the present invention can buffer the impact and load on the rotor by providing a primary damping structure and a secondary damping structure, thereby reducing the impact and load on the bearing and the compressor. It can also further reduce the problem of local wear caused by uneven force at both ends of the bearing due to rotor tilt, and further improve the reliability and stability of the gas bearing and the compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0022] Figure 1 A cross-sectional view of a gas bearing provided in an embodiment of the present utility model;

[0023] Figure 2 A side view of a gas bearing provided by an embodiment of the present utility model;

[0024] Figure 3 A schematic structural diagram of a corrugated foil structure provided in an embodiment of the present utility model;

[0025] Figure 4 Another structural schematic diagram of the corrugated foil structure provided by an embodiment of the present utility model;

[0026] In the picture:

[0027] 1. Bearing support; 2. First bearing housing; 3. Second bearing housing; 4. Corrugated foil structure; 5. Damping ring; 6. Porous structure; 7. Retaining ring. DETAILED DESCRIPTION

[0028] In order to make the purpose, technical solutions and advantages of the present invention more clearly understood, the present invention is further described in detail below with reference to the accompanying drawings and embodiments. It should be understood that the specific embodiments described herein are only used to explain the present invention and are not intended to limit the present invention.

[0029] In order to help those skilled in the art better understand the present invention, the following will be combined with the drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments of the present invention. Obviously, the embodiments described are only part of the embodiments of the present invention, not all of the embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts should fall within the scope of protection of the present invention.

[0030] It should be noted that the terms "first," "second," and the like in the specification and claims of the present invention and the accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate for the embodiments of the present invention described herein. In addition, the terms "including" and "having," as well as any variations thereof, are intended to cover non-exclusive inclusions. For example, a process, method, system, product, or apparatus comprising a series of steps or units is not necessarily limited to those steps or units explicitly listed, but may include other steps or units that are not explicitly listed or that are inherent to these processes, methods, products, or apparatuses.

[0031] It should be noted that in the description of this utility model, terms such as "upper," "lower," "left," "right," "inner," and "outer" indicating directions or positional relationships are based on the directions or positional relationships shown in the accompanying drawings. These terms are used solely for ease of description and are not intended to indicate or imply that the device or component described must have a specific orientation, be constructed, or operate in a specific position. Therefore, they should not be construed as limitations on this utility model. Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance.

[0032] Furthermore, it should be noted that, in the description of this utility model, unless otherwise expressly specified or limited, the terms "installed," "set," and "connected" should be understood in a broad sense. For example, they may refer to fixed connections, detachable connections, or integral connections; they may refer to direct connections, indirect connections through an intermediate medium, or internal communication between two components. Those skilled in the art will understand the specific meanings of the above terms in this utility model based on the specific circumstances.

[0033] For air-suspended centrifugal compressors, the air bearing is a core component that determines its safe and stable operation. The stability and reliability of the air bearing directly affect the performance of the centrifugal compressor. Compared with dynamic air bearings, static air bearings have attracted widespread attention for their stronger load-bearing capacity. The reliability and stability of static air suspension are affected by many factors, such as support method, rotational speed, and air flow rate. The structure of the bearing has a significant impact on its performance. During operation, the rotor assembly is subject to certain loads and radial impacts. Large impact loads can affect the operating performance and reliability of the bearings. In severe cases, the shaft can become stuck and the motor can burn out, which in turn affects the operating performance and life of the compressor.

[0034] To this end, this application provides a Figures 1 to 4The gas bearing shown includes: a bearing support 1; a first bearing housing 2, which is disposed within the bearing support 1 and has a primary damping structure disposed between the outer wall of the first bearing housing 2 and the inner wall of the bearing support 1; and a second bearing housing 3, which is disposed within the first bearing sleeve housing and has a secondary damping structure disposed between the outer wall of the second bearing housing 3 and the inner wall of the first bearing housing 2. By providing the primary and secondary damping structures, impacts and loads on the rotor can be cushioned, reducing the impact of impacts and loads on the bearing and compressor. Furthermore, the problem of localized wear caused by uneven force on both ends of the bearing due to rotor tilt can be further reduced, further improving the reliability and stability of the gas bearing and compressor.

[0035] When using a gas bearing, the gas bearing can generate an air film between its second bearing shell 3 and the rotor, thereby supporting the rotor. When the rotor is subjected to an impact load, the impact load on the rotor can act on the second bearing shell 3 through the air film, and the primary damping structure and the secondary damping structure can correspondingly deform, thereby buffering and offsetting the impact load. In particular, when the rotor is subjected to an overturning load, it will produce axial tilt. The axial tilt will cause local contact between the rotor and the gas bearing at the end of the gas bearing and cause severe wear. At this time, the primary damping structure and the secondary damping structure can correspondingly deform, so that the gas bearing can adapt to the tilt of the rotor, avoiding further rigid contact between the rotor and the gas bearing and increasing the degree of wear, thereby achieving the purpose of ensuring the reliability and stability of the gas bearing and the compressor.

[0036] As an embodiment, the primary damping structure includes a corrugated foil structure 4, which is annularly wrapped around the first bearing housing 2, with the crests of the corrugated foil structure 4 abutting against the bearing support 1, and the troughs of the corrugated foil structure 4 abutting against the first bearing housing 2. The shape of the corrugated foil structure 4 enables it to deform as the crests and troughs change when subjected to an applied force, thereby producing a damping and buffering effect, achieving the effect of buffering and offsetting the impact and load applied to the rotor. The corrugated foil structure 4 is annularly wrapped around the first bearing housing 2, so that when the corrugated foil structure 4 is subjected to an impact or load transmitted from the rotor, the corrugated foil structure 4 can extend along the annular shape, thereby ensuring that the corrugated foil structure 4 reliably deforms and reliably buffers the impact and load.

[0037] The bump foil structure 4 has a first end and a second end in its longitudinal direction. The first end is mounted on the bearing support 1, and the second end is movably positioned between the bearing support 1 and the first bearing housing 2. The free movement of the second end enables the bump foil structure 4 to reliably deform, ensuring its damping effect. When the bump foil structure 4 deforms, the second end approaches the first end. When the force acting on the bump foil structure 4 disappears, the second end moves away from the first end.

[0038] The thickness L3 of the bump foil structure 4 has a numerical range of 0.1 mm to 0.5 mm. When the thickness L3 of the bump foil structure 4 is too large, the force required to deform the bump foil structure 4 is large, and the reaction rate to the rotor being subjected to impact loads is low. When the thickness L3 of the bump foil structure 4 is too small, the structural strength of the bump foil structure 4 is poor. At the same time, the structural strength between the bearing support 1 and the first bearing housing 2 cannot reliably support the rotor, which will affect the operating reliability of the gas bearing and the compressor. Only when the thickness L3 of the bump foil structure 4 is between 0.1 mm and 0.5 mm can the reliable deformation and structural strength of the bump foil structure 4 be guaranteed, thereby ensuring the mechanical reliability of the gas bearing and the compressor.

[0039] The pitch L4 between two adjacent wave crests of the corrugated foil structure 4 ranges from 2 mm to 8 mm. When the pitch L4 of the corrugated foil structure 4 is too large, the bearing capacity of the corrugated foil structure 4 is reduced. When the pitch L4 of the corrugated foil structure 4 is too small, the force required to deform the corrugated foil structure 4 is large, and the reaction rate to the rotor impact load is slow. Only when the pitch L4 of the corrugated foil structure 4 is between 2 mm and 8 mm can the corrugated foil structure 4 be reliably deformed and its structural strength be guaranteed, thereby ensuring the mechanical reliability of the gas bearing and compressor.

[0040] The height L5 of a single wave between the peak and trough of the bump foil structure 4 ranges from 1.5 mm to 3 mm. When the height L5 of a single wave of the bump foil structure 4 is too large, the deformation of the bump foil structure 4 is large, but the thickness of the bump foil structure 4 is too large, affecting the overall volume of the gas bearing. When the height L5 of a single wave of the bump foil structure 4 is too small, the deformation of the bump foil structure 4 is small, reducing the bearing capacity of the bump foil structure 4. Only when the height L5 of a single wave of the bump foil structure 4 is between 1.5 mm and 3 mm can the reliable deformation and structural strength of the bump foil structure 4 be guaranteed, thereby ensuring the mechanical reliability of the gas bearing and compressor.

[0041] There are at least two bump foil structures 4, all of which are arranged in parallel along the axis of the gas bearing. Providing multiple bump foil structures 4 not only ensures mutual backup between the multiple bump foil structures 4, improving the reliability of the gas bearing, but also increases the contact area by utilizing multiple bump foil structures 4, thereby absorbing more impact and load.

[0042] There is a seam spacing between two adjacent bump foil structures 4. By setting the seam spacing, structural interference between the two adjacent bump foil structures 4 is avoided, the relative independence of the bump foil structures 4 is ensured, and the reliability of the gas bearing is improved.

[0043] The relationship between the joint spacing L6, the number n of the bump foil structures 4, and the axial length L2 of the gas bearing is: L2 = L6*n*(20-50); when the joint spacing L6 is too large, the number of bump foil structures 4 and the size of a single bump foil structure 4 will be reduced, thereby reducing the bearing capacity of the bump foil structure 4; and when the joint spacing L6 is too small, structural interference is easily generated between two adjacent bump foil structures 4, thereby reducing the reliability of the gas bearing; and when the number n of the bump foil structures 4 is too large, the support capacity of the bump foil structure 4 will be reduced. The number and size of a single bump foil structure 4 are set to reduce the load-bearing capacity of the bump foil structure 4. When the number n of the bump foil structures 4 is too small, the width of a single bump foil structure 4 is too large, which makes the reaction rate of the bump foil structure 4 to impact and load lower. Only when the relationship between the seam spacing L6, the number n of the bump foil structures 4 and the axial length L2 of the gas bearing meets the condition L2=L6*n*(20~50), that is, even if the seam spacing L6 and the number n of the bump foil structures 4 are inversely proportional, can the reliability and load-bearing capacity of the gas bearing be guaranteed.

[0044] The secondary damping structure includes a damping ring 5, which surrounds the outer wall of the second bearing housing 3 and abuts against the first bearing housing 2. The damping ring 5 enables a certain degree of relative movement between the first bearing housing 2 and the second bearing housing 3, further improving the gas bearing's adaptability to impacts and loads on the rotor and enhancing its support effectiveness.

[0045] There are at least two damping rings 5, all of which are arranged in parallel along the axis of the gas bearing. Providing multiple damping rings 5 ​​further enhances the damping effect of the secondary damping structure. Furthermore, the differential deformation of the damping rings 5 ​​at different positions improves the relative movement accuracy between the first bearing housing 2 and the second bearing housing 3, thereby ensuring the reliability and load-bearing capacity of the gas bearing.

[0046] Preferably, the gas bearing has a first portion, a middle portion, and a second portion distributed along the axial direction, with at least one damping ring 5 located at the first portion and at least one damping ring 5 located at the second portion. When the rotor is subjected to impact, load, or other conditions causing tilt, the rotor will inevitably tilt relative to the axial direction. For example, when the left end of the rotor tilts downward, the lower portion of the damping ring 5 in the first portion on the left side is squeezed and deformed, while the upper portion of the damping ring 5 in the second portion is also squeezed and deformed. However, the damping ring 5 in the first portion and the damping ring 5 in the second portion are located at both ends of the gas bearing, further preventing the rotor from directly and rigidly contacting the gas bearing, thereby improving the support reliability of the gas bearing.

[0047] The thickness L1 of the damping ring 5 ranges from 2.6 mm to 5.3 mm. If the thickness L1 of the damping ring 5 is too small, the damping effect of the damping ring 5 is poor. If the thickness L1 of the damping ring 5 is too large, the gas bearing is too large, exceeding the allowable deformation of the gas bearing. Only when the thickness L1 of the damping ring 5 is between 2.6 mm and 5.3 mm can the reliability and load-bearing capacity of the gas bearing be guaranteed.

[0048] like Figure 2 As shown, a receiving groove is provided on the inner wall of the first bearing housing 2, and the damping ring 5 is provided in the receiving groove, and part of the damping ring 5 protrudes from the receiving groove. The receiving groove is used to fix the setting position of the damping ring 5, thereby ensuring that the damping ring 5 is reliably fixed, thereby ensuring the structural reliability of the gas bearing.

[0049] The gas bearing also includes a porous structure 6, which is disposed within the second bearing housing 3. External pressurized gas is supplied to the porous structure 6 through gas passages provided in the bearing support 1, the first bearing housing 2, and the second bearing housing 3, thereby forming an air film between the porous structure 6 and the rotor, thereby supporting the rotor with the air film. Furthermore, the porous structure 6 enables a reliable air film to be formed on the rotor surface, thereby improving the reliability of the rotor support. Preferably, the porous structure 6 can be made of graphite, ceramic, sintered material, or the like.

[0050] The porous structure 6 and the second bearing housing 3 are fixedly connected by glue.

[0051] The gas bearing further includes a retaining ring 7, which is disposed at the end of the first bearing housing 2 and abuts against the second bearing housing 3. The retaining ring 7 restrains the second bearing housing 3, preventing axial relative movement between the first and second bearing housings 2 and 3, thereby ensuring the structural reliability of the gas bearing.

[0052] The retaining ring 7 is provided at the end of the second bearing housing 3 and abuts against the first bearing housing 2. The retaining ring 7 is used to restrict the first bearing housing 2, preventing axial relative movement between the first bearing housing 2 and the second bearing housing 3, thereby ensuring the structural reliability of the gas bearing.

[0053] A compressor comprises the above-mentioned gas bearing.

[0054] The above-described embodiments merely represent several implementation methods of the present invention. While the descriptions are relatively specific and detailed, they should not be construed as limiting the scope of the present invention. It should be noted that a person skilled in the art would be able to make various modifications and improvements without departing from the concept of the present invention, and these modifications and improvements fall within the scope of protection of the present invention. Therefore, the scope of protection of the present invention shall be determined by the appended claims.

Claims

1. A gas bearing, characterized in that: include: Bearing support (1); A first bearing shell (2), the first bearing shell (2) being arranged in the bearing support (1), and a primary damping structure being arranged between an outer wall of the first bearing shell (2) and an inner wall of the bearing support (1); A second bearing housing (3) is provided in the first bearing housing, and a secondary damping structure is provided between the outer wall of the second bearing housing (3) and the inner wall of the first bearing housing (2).

2. The gas bearing according to claim 1, wherein: The primary damping structure comprises a wave foil structure (4), which is annularly arranged around the first bearing housing (2), and the wave crests of the wave foil structure (4) are in abutment with the bearing support (1), and the wave troughs of the wave foil structure (4) are in abutment with the first bearing housing (2).

3. The gas bearing according to claim 2, wherein: The corrugated foil structure (4) has a first end and a second end in a length direction, the first end is arranged on the bearing support (1), and the second end is movably located between the bearing support (1) and the first bearing housing (2).

4. The gas bearing according to claim 2, wherein: The thickness L3 of the corrugated foil structure (4) has a numerical range of 0.1 mm to 0.5 mm; and / or the pitch L4 between two adjacent wave crests of the corrugated foil structure (4) has a numerical range of 2 mm to 8 mm; and / or the height L5 of a single wave between a wave crest and a wave trough of the corrugated foil structure (4) has a numerical range of 1.5 mm to 3 mm.

5. The gas bearing according to claim 2, wherein: The number of the corrugated foil structures (4) is at least two, and all the corrugated foil structures (4) are arranged in parallel along the axial direction of the gas bearing.

6. The gas bearing according to claim 5, characterized in that: There is a seam spacing between two adjacent wave foil structures (4), and the relationship between the seam spacing L6, the number n of the wave foil structures (4) and the axial length L2 of the gas bearing is: L2 = L6*n*(20-50).

7. The gas bearing according to claim 1, wherein: The secondary damping structure comprises a damping ring (5), the damping ring (5) surrounds the outer wall of the second bearing shell (3), and the outer wall of the damping ring (5) abuts against the first bearing shell (2).

8. The gas bearing according to claim 7, characterized in that: The number of the damping rings (5) is at least two, and all the damping rings (5) are arranged in parallel along the axial direction of the gas bearing.

9. The gas bearing according to claim 8, characterized in that: The gas bearing has a first portion, a middle portion and a second portion distributed in the axial direction, at least one damping ring (5) is located at the first portion, and at least one damping ring (5) is located at the second portion.

10. The gas bearing according to claim 7, wherein: The thickness L1 of the damping ring (5) has a numerical range of 2.6 mm to 5.3 mm.

11. The gas bearing according to claim 1, wherein: The gas bearing further comprises a porous structure (6), and the porous structure (6) is arranged in the second bearing housing (3).

12. The gas bearing according to claim 1, wherein: The gas bearing further comprises a retaining ring (7), wherein the retaining ring (7) is arranged at the end of the first bearing housing (2), and the retaining ring (7) is in abutment with the second bearing housing (3); or, the retaining ring (7) is arranged at the end of the second bearing housing (3), and the retaining ring (7) is in abutment with the first bearing housing (2).

13. A compressor, characterized in that: A gas bearing comprising the gas bearing according to any one of claims 1 to 12.

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