Gas bearing, compressor and air conditioning system

Abstract

This application relates to the field of air conditioning technology and discloses a gas bearing, comprising: a bearing base having a plurality of annular throttling orifice groups thereon, wherein the throttling orifices in adjacent annular throttling orifice groups are staggered; the annular throttling orifice groups include a plurality of throttling orifices, and the plurality of throttling orifices are arranged in annularity. The gas bearing of this disclosure optimizes the gas supply method by staggering the throttling orifices in adjacent annular throttling orifice groups. Compared with the traditional flush arrangement, the gas bearing using the staggered throttling orifice arrangement of this disclosure doubles the number of gas supply positions in the circumferential direction, resulting in a more uniform distribution of lubricating gas within the bearing clearance. This application also discloses a compressor and an air conditioning system.

Description

Technical Field

[0001] This application relates to the field of air conditioning technology, such as a gas bearing, compressor, and air conditioning system. Background Technology

[0002] Currently, air-suspended hydrostatic bearings (hereinafter referred to as gas bearings) are widely used in aerospace, high-speed, and high-precision industries due to their advantages such as low power consumption, long life, and high precision. Among them, orifice throttling hydrostatic bearings supply high-pressure gas or refrigerant to the bearing clearance through a throttling orifice, replacing traditional lubricating oil to support rotor rotation. However, under high-speed operating conditions, gas bearings are prone to whirl instability, which can lead to bearing malfunction, severe damage, or even bearing seizure in severe cases.

[0003] In the process of implementing the embodiments of this disclosure, it was found that at least the following problems exist in the related technology: the setting method of the throttling orifice on the existing gas bearing makes the performance of the gas bearing poor. Summary of the Invention

[0004] To provide a basic understanding of some aspects of the disclosed embodiments, a brief summary is given below. This summary is not intended as a general commentary, nor is it intended to identify key / important components or describe the scope of protection of these embodiments, but rather as a prelude to the detailed description that follows.

[0005] This disclosure provides a gas bearing, a compressor, and an air conditioning system to address the problem that the performance of gas bearings is poor due to the existing method of setting throttle orifices on gas bearings.

[0006] In some embodiments, the gas bearing includes:

[0007] The bearing base has multiple annular throttling orifice groups, with the throttling orifices in adjacent annular throttling orifice groups being staggered; the annular throttling orifice group includes multiple throttling orifices, and the multiple throttling orifices are arranged in annular order.

[0008] In some embodiments, the compressor includes the aforementioned gas bearing.

[0009] In some embodiments, the air conditioning system includes the aforementioned compressor.

[0010] The gas bearing, compressor, and air conditioning system provided in this disclosure can achieve the following technical effects:

[0011] The gas bearing of this disclosure optimizes the gas supply method by staggering the throttling orifices in adjacent annular throttling orifice groups. Compared with the traditional flush arrangement, the gas bearing with staggered throttling orifices of this disclosure doubles the number of gas supply positions in the circumferential direction, resulting in a more uniform distribution of lubricating gas within the bearing clearance. Increasing the contact angle between the lubricating gas (e.g., compressed gas) and the rotor helps improve the stability of the orifice throttling gas bearing. It also increases the uniformity of the gas receiving angle in the bearing clearance, enhancing the bearing's dynamic performance and contributing to improved stability during high-speed operation.

[0012] The above general description and the description below are exemplary and illustrative only and are not intended to limit this application. Attached Figure Description

[0013] One or more embodiments are illustrated by way of example with reference to the accompanying drawings. These illustrations and drawings do not constitute a limitation on the embodiments. Elements having the same reference numerals in the drawings are shown as similar elements. The drawings are not to be scaled. And wherein:

[0014] Figure 1 This is a schematic diagram of an existing radial gas bearing.

[0015] Figure 2 This is a schematic diagram of an existing axial thrust gas bearing.

[0016] Figure 3 This is a schematic diagram of the structure of a gas bearing provided in an embodiment of this disclosure;

[0017] Figure 4 This is a schematic diagram of the structure of a gas bearing provided in an embodiment of this disclosure;

[0018] Figure 5 yes Figure 4 Schematic diagram of the cross-sectional structure along the middle AA direction;

[0019] Figure 6 yes Figure 5 A partially enlarged schematic diagram of the cross-sectional structure shown;

[0020] Figure 7 This is a schematic diagram of the airflow direction structure of a gas bearing provided in an embodiment of this disclosure;

[0021] Figure 8 yes Figure 4 Schematic diagram of the cross-sectional structure in the middle BB direction;

[0022] Figure 9 This is another gas bearing provided in the embodiments of this disclosure. Figure 4 Schematic diagram of the BB-direction cross-section structure in the middle;

[0023] Figure 10 This is another gas bearing provided in the embodiments of this disclosure. Figure 4 A schematic diagram of the CC-direction cross-section of the rotor; where the cross-sectional plane passes through the rotor's axis.

[0024] Figure 11 This is another gas bearing provided in the embodiments of this disclosure. Figure 4 Schematic diagram of the BB-direction cross-section structure in the middle;

[0025] Figure 12 yes Figure 11 A partially enlarged schematic diagram of the cross-sectional structure shown;

[0026] Figure 13 This is another gas bearing provided in the embodiments of this disclosure. Figure 4 Schematic diagram of the BB-direction cross-section structure in the middle;

[0027] Figure 14 yes Figure 13 A partially enlarged schematic diagram of the cross-sectional structure shown;

[0028] Figure 15 This is a schematic diagram of another gas bearing structure provided in an embodiment of this disclosure;

[0029] Figure 16 This is a schematic diagram of another gas bearing provided in an embodiment of this disclosure.

[0030] Figure label:

[0031] 010. Existing radial gas bearing; 011. Throttling orifices in each row; 020. Existing axial thrust gas bearing; 021. Throttling orifices in each ring;

[0032] 10: Throttling orifice; 101: Inlet section; 102: Buffer section; 103: Outlet section; 104: Curved protrusion; 11: First throttling orifice; 12: Second throttling orifice; 13: Third throttling orifice; 14: Fourth throttling orifice; 15: Fifth throttling orifice; 16: Sixth throttling orifice; 17: Seventh throttling orifice; 18: Eighth throttling orifice; 19: Ninth throttling orifice; 21: Hollow cylindrical bearing base; 22: Disc-shaped bearing base; 30: Rotor. Detailed Implementation

[0033] To provide a more detailed understanding of the features and technical content of the embodiments of this disclosure, the implementation of the embodiments of this disclosure will be described in detail below with reference to the accompanying drawings. The accompanying drawings are for illustrative purposes only and are not intended to limit the embodiments of this disclosure. In the following technical description, for ease of explanation, several details are used to provide a full understanding of the disclosed embodiments. However, one or more embodiments may still be implemented without these details. In other cases, well-known structures and devices may be simplified in their depiction to simplify the drawings.

[0034] The terms "first," "second," etc., used in the specification, claims, and accompanying drawings of this disclosure are used to distinguish similar objects and are not necessarily used to describe a specific order or sequence. It should be understood that such data can be interchanged where appropriate for the embodiments of this disclosure described herein. Furthermore, the terms "comprising" and "having," and any variations thereof, are intended to cover non-exclusive inclusion.

[0035] In this disclosure, the terms "upper," "lower," "inner," "middle," "outer," "front," and "rear," etc., indicate the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings. These terms are primarily for better description of the embodiments of this disclosure and their implementations, and are not intended to limit the indicated devices, elements, or components to having a specific orientation, or to require them to be constructed and operated in a specific orientation. Furthermore, some of the aforementioned terms may be used to indicate other meanings besides orientation or positional relationship; for example, the term "upper" may in some cases indicate a dependency or connection relationship. Those skilled in the art can understand the specific meaning of these terms in the embodiments of this disclosure according to the specific circumstances.

[0036] Furthermore, the terms "set up," "connect," and "fix" should be interpreted broadly. For example, "connection" can be a fixed connection, a detachable connection, or an integral structure; it can be a mechanical connection or an electrical connection; it can be a direct connection or an indirect connection through an intermediate medium, or it can be an internal connection between two devices, components, or parts. Those skilled in the art can understand the specific meaning of the above terms in the embodiments of this disclosure according to the specific circumstances.

[0037] Unless otherwise stated, the term "multiple" means two or more.

[0038] It should be noted that, unless otherwise specified, the embodiments and features described in the present disclosure can be combined with each other.

[0039] Combination Figures 1-16As shown, this embodiment of the present disclosure provides a gas bearing, including a bearing base, on which a plurality of annular throttling orifice groups are provided, and the throttling orifices 10 in two adjacent annular throttling orifice groups are staggered; the annular throttling orifice group includes a plurality of throttling orifices 10, and the plurality of throttling orifices 10 are arranged in annularity.

[0040] The gas bearing of this embodiment optimizes the gas supply method by staggering the throttling orifices 10 in adjacent annular throttling orifice groups. Compared with the conventional flush arrangement, increasing the contact angle between the lubricating gas (e.g., compressed gas) and the rotor helps improve the stability of the orifice throttling gas bearing. It also increases the uniformity of the gas receiving angle in the bearing clearance, improving the dynamic performance of the bearing and contributing to improved stability during high-speed operation.

[0041] In this embodiment of the disclosure, the conventional flush arrangement refers to the arrangement in the existing radial gas bearing 010 where the rows of throttling orifices 011 are parallel and axially collinear (e.g., ...). Figure 1 (as shown); or, in the existing axial thrust gas bearing 020, the throttling orifice 021 of each ring is located on the common radial line of the bearing disc (as shown). Figure 2 (As shown).

[0042] The lubrication process of a gas bearing with throttling orifices (denoted as a small-orifice throttling hydrostatic gas bearing) is as follows: compressed gas is drawn from an external gas supply device, flows through a gas supply pipe, passes through a throttling device (throttling structure), and finally enters the bearing clearance through the throttling orifice, thereby bearing the rotation of the rotor. Analysis shows that when using a traditional flush arrangement, the lubrication angle of the compressed gas entering the bearing clearance is uneven, which is detrimental to the stability of the bearing. However, the gas bearing with staggered throttling orifices according to the embodiments of this disclosure doubles the number of gas supply positions in the circumferential direction, making the distribution of lubricating gas within the bearing clearance more uniform (e.g., ...). Figure 7 As shown), and reduces the circumferential flow of lubricating gas caused by rotor motion (e.g. Figure 7 The circumferential airflow direction (indicated by the dashed arrow) reduces the possibility of eddy current instability, making the bearing more stable. This effect is more pronounced under high-speed operating conditions. Simultaneously, the more uniform gas distribution within the bearing clearance also helps to raise the threshold for air hammer, meaning that air hammer oscillation is less likely to occur, significantly improving the bearing's dynamic performance.

[0043] In addition, compared with conventional gas bearings with flush orifices, the gas bearing with staggered orifices according to the present invention has increased stiffness (up to 1.5 to 1.8 times that of conventional gas bearings) and increased damping (up to 1.3 to 1.5 times that of conventional gas bearings), which can effectively improve the dynamic stability of the bearing and thus increase the compressor operating speed when it is applied to a compressor.

[0044] In this embodiment of the disclosure, the gas bearing further includes a rotor 30 disposed on the outlet side of the throttling orifice 10 on the bearing base. For example... Figure 3 The radial gas bearing shown has a rotor 30 located in the hollow part of a hollow cylindrical bearing base 21, forming a bearing gap between the rotor 30 and the inner wall of the bearing base.

[0045] The specific arrangement of the multiple annular throttling orifice groups on the gas bearing in this embodiment can be determined according to the specific structural form of the gas bearing.

[0046] In some embodiments, the gas bearing is a radial gas bearing, an axial thrust gas bearing, a gas bearing with a local porous throttling device, or a split bearing structure including a bearing body and a bearing sleeve, etc. The structural form of the bearing base is determined according to the type of gas bearing, ensuring that the throttling holes in adjacent annular throttling hole groups are staggered.

[0047] In some embodiments, such as Figure 3 As shown, the bearing base is a hollow cylindrical bearing base 21, for example, the bearing base of a radial gas bearing. Multiple annular throttling orifice groups are arranged parallel to each other along the circumference of the hollow cylindrical bearing base 21, and the throttling orifices 10 in adjacent annular throttling orifice groups are staggered. In this embodiment, two or more rows of parallel annular throttling orifice groups are provided on the hollow cylindrical bearing base 21, and the plane of each row of annular throttling orifice groups is perpendicular to the axial direction of the hollow cylindrical bearing base 21.

[0048] In this embodiment, each annular orifice group may include 4 to 8 orifices 10. Optionally, each annular orifice group may include 5 to 7 orifices 10. Optionally, each annular orifice group may include 6 orifices 10. Of course, the number of orifices 10 can be any integer within the range of 4 to 8.

[0049] Optionally, the multiple throttling orifices 10 in the annular throttling orifice group are evenly distributed circumferentially on the hollow cylindrical bearing base 21. This uniform distribution ensures the rigidity of the bearing base.

[0050] Optionally, in each pair of adjacent annular throttling orifice groups, the two adjacent throttling orifices (first throttling orifice 11, second throttling orifice 12) in the first annular throttling orifice group and one throttling orifice (third throttling orifice 13) in the second annular throttling orifice group located between the two adjacent throttling orifices (11, 12) form an isosceles triangle, with the throttling orifice 13 in the second annular throttling orifice group serving as the vertex. This makes the distribution of lubricating gas within the bearing clearance more uniform. In this embodiment, the height of the isosceles triangle is the axial distance h between the two adjacent annular throttling orifice groups. The specific value of the axial distance h can be determined based on the performance requirements of the bearing base required in actual applications. Here, "first" and "second" are used to distinguish between two adjacent annular throttling orifice groups; therefore, the same annular throttling orifice group may be either the "first annular throttling orifice group" or the "second annular throttling orifice group."

[0051] Optionally, the axial spacing h between any two adjacent annular throttling orifice groups is equal.

[0052] Optionally, the number of annular throttling orifice groups is three or more; in the three adjacent annular throttling orifice groups, the throttling orifices in the two outer annular throttling orifice groups are collinear in the axial direction, and the line connecting the four throttling orifices (first throttling orifice 11, second throttling orifice 12, fourth throttling orifice 14 and fifth throttling orifice 15) on the two adjacent collinear groups forms a square; one throttling orifice (third throttling orifice 13) in the middle annular throttling orifice group is located at the center of the square. In this embodiment, in the axial direction of the hollow cylindrical bearing base 21, the axial length H of the square is the sum of the axial distances between the two adjacent annular throttling orifice groups.

[0053] Optionally, the square can be a rectangle or a square. When the direction is rectangular, the axial side can be either the longer side or the shorter side, without limitation. That is, the length of the side of the square can be determined according to the actual application.

[0054] In some embodiments, each throttling orifice has one or more outlet directions, which may intersect the axis of the bearing base; and the outlet directions of multiple throttling orifices in an annular throttling orifice group are consistent. This creates more axial air inlet angles and air supply positions, resulting in a more uniform distribution of lubricating gas within the bearing clearance, further reducing the circumferential flow of lubricating gas caused by rotor motion, reducing the possibility of eddy instability, and making the bearing operation more stable. In this embodiment, the outlet direction of the throttling orifice 10 may intersect the axis of the bearing base, and the included angle α formed by the intersection is not limited.

[0055] Optionally, such as Figure 8As shown, the included angle α can be 90°, so the outlet direction of the throttling orifice 10 can be orthogonal to the axis l of the bearing base. This case, where the included angle α between the outlet direction of the throttling orifice 10 and the axis l of the bearing base is 90°, is defined as the outlet direction of the throttling orifice 10 being perpendicular to the outlet direction.

[0056] Optionally, the included angle α is not 90°. That is, the included angle α belongs to any angle within the interval (0°, 90°) or (90°, 180°). Optionally, the included angle α belongs to any angle within the interval (45°, 90°) or (90°, 135°). Optionally, the included angle α belongs to any angle within the interval (60°, 85°) or (95°, 120°). In this embodiment, when the included angle α between the outlet direction of the throttling orifice 10 and the axis l of the bearing base is not 90°, the outlet direction of the throttling orifice 10 is defined as an inclined outlet direction; and based on the range to which the included angle α belongs, it is defined as a first inclined outlet direction (for example, the included angle α1 belongs to the interval (0°, 90°)) and a second inclined outlet direction (for example, the included angle α2 belongs to the interval (90°, 180°)). The included angle α can be regarded as the inclination angle of the outlet direction.

[0057] That is, based on the angle formed by the intersection of the outlet direction of the throttle orifice and the axis l of the bearing base, the outlet direction is divided into a vertical outlet direction (orthogonal) and an inclined outlet direction (non-orthogonal). The inclined outlet direction is further divided into a first inclined outlet direction and a second inclined outlet direction.

[0058] In this embodiment, the consistent air outlet direction of multiple throttling orifices in each annular throttling orifice group means that the air outlet directions of multiple throttling orifices in one annular throttling orifice group may intersect at one point (when there is only one air outlet direction of the throttling orifice) or multiple points (when there are multiple air outlet directions of the throttling orifice) on the axis of the bearing base.

[0059] Optionally, in multiple annular throttling orifice groups, the tilt angles of the tilted outlet directions of the throttling orifices 10 in different annular throttling orifice groups may be the same or different. This can be set according to the actual situation.

[0060] In some embodiments, in an annular throttling orifice group, each throttling orifice 10 has a single outlet direction, and the outlet directions of multiple throttling orifices 10 in the annular throttling orifice group are consistent and can be perpendicular to the axis l of the hollow cylindrical bearing base 21. That is, the outlet directions of multiple throttling orifices are all directed toward the center of the circumference of the annular throttling orifice group, and are all perpendicular to the outlet direction.

[0061] like Figure 5 and Figure 8The gas bearing shown has multiple annular throttling orifice groups, each of which has a single outlet direction, all of which are perpendicular to the outlet direction.

[0062] In some embodiments, when the outlet direction of the throttling orifice 10 of the plurality of annular throttling orifice groups includes an inclined outlet direction, the inclined outlet directions of the axially collinear throttling orifices are in the same direction, and the inclined outlet directions of the throttling orifices 10 of two adjacent annular throttling orifice groups are in opposite directions.

[0063] In this embodiment, "consistent tilt direction" means that the tilted air outlet direction of the axially collinear throttling orifices 10 is either the first tilted air outlet direction or the second tilted air outlet direction. "Opposite tilt direction" means that in two adjacent annular throttling orifice groups, the tilted air outlet direction of the throttling orifice 10 in one annular throttling orifice group is the first tilted air outlet direction, while the tilted air outlet direction of the throttling orifice 10 in the other annular throttling orifice group is the second tilted air outlet direction. That is, when the air outlet direction of the throttling orifice 10 includes a tilted air outlet direction, all throttling orifices 10 in the multiple annular throttling orifice groups include a tilted air outlet direction, and the tilted direction of the throttling orifice in each annular throttling orifice group is set according to the configuration of this embodiment.

[0064] Optionally, the outlet direction of the throttling orifices 10 in the multiple annular throttling orifice groups is the same, and it is an inclined outlet direction; the throttling orifices are collinear in the axial direction (e.g. Figure 9 The inclined directions of the second throttling orifice 12 and the fifth throttling orifice 15 in the annular throttling orifice group are the same, and the inclined directions of the throttling orifice 10 in two adjacent annular throttling orifice groups are opposite. Figure 9 and Figure 10 As shown, the inclined air outlet directions of the second throttling orifice 12 and the fifth throttling orifice 15, which are collinear in the axial direction, are the first inclined air outlet directions, and the inclined air outlet directions of the third throttling orifice 13 and the sixth throttling orifice 16, which are collinear in the axial direction, are the second inclined air outlet directions; and the inclined air outlet directions of the second throttling orifice 12 and the third throttling orifice 13 of two adjacent annular throttling orifice groups are opposite.

[0065] Optionally, combined Figures 11 to 14 As shown, the outlet directions of the throttling orifices 10 in the multiple annular throttling orifice groups are multiple, and one or more outlet directions are inclined outlet directions; then, the inclined outlet directions of the axially collinear throttling orifices are consistent, and the inclined outlet directions of the throttling orifices 10 in two adjacent annular throttling orifice groups are opposite.

[0066] In this embodiment, optionally, when there is one or more (i.e., two or more) air outlet directions that are inclined air outlet directions, all of the one or more air outlet directions are either the first inclined air outlet direction or the second inclined air outlet direction, or, some of the one or more air outlet directions are the first inclined air outlet direction and the rest are the second inclined air outlet direction.

[0067] like Figure 11 and Figure 12 As shown, the throttling orifices 10 of the multiple annular throttling orifice groups have two outlet directions: one vertical and one inclined. Therefore, the inclined outlet directions of the axially collinear throttling orifices are aligned, and the inclined outlet directions of adjacent annular throttling orifice groups are opposite. The arrangement of the inclined outlet directions of the throttling orifices 10 of the multiple annular throttling orifice groups is the same as... Figure 9 and Figure 10 As shown, it will not be elaborated further here.

[0068] like Figure 13 and Figure 14 As shown, the throttling orifice 10 of the multiple annular throttling orifice groups has two outlet directions, both of which are inclined outlet directions, one being a first inclined outlet direction and the other a second inclined outlet direction. The arrangement of these two inclined outlet directions also satisfies the same... Figure 9 and Figure 10 The setup method described above will not be repeated here.

[0069] In some embodiments, along the intake direction, the throttle orifice 10 includes an intake section 101, a buffer section 102, and an outlet section 103, wherein the diameter of the intake section 101 is larger than the diameter of the outlet section 103; one end of the buffer section 102 communicates with the intake section 101, and the other end communicates with the outlet section 103. The outlet section 103 includes one or more independent outlet segments. The outlet direction of the throttle orifice 10 refers to the direction parallel to the axial direction of the outlet section 103.

[0070] Combination Figure 6 As shown, there is one air outlet section 103, whose axial direction is perpendicular to the axis l of the hollow cylindrical bearing base 21.

[0071] Combination Figure 9 As shown, there is one air outlet section 103, whose axial direction intersects the axis l of the hollow cylindrical bearing base 21, and the included angle α1 is in the range of (0°, 90°). For example, the included angle α1 is 60°.

[0072] Combination Figure 10 As shown, there is one air outlet section 103, whose axial direction intersects the axis l of the hollow cylindrical bearing base 21, and the included angle α2 is in the range of (90°, 180°). For example, the included angle α2 is 120°.

[0073] Combination Figure 12As shown, there are two air outlet sections 103. The axial direction of one air outlet section is perpendicular to the axis l of the hollow cylindrical bearing base 21, and the axial direction of the other air outlet section is perpendicular to the axis l of the hollow cylindrical bearing base 21. The included angle α1 belongs to the range of (0°, 90°) or (90°, 180°).

[0074] Combination Figure 14 As shown, there are two air outlet sections 103. The axial direction of one air outlet section intersects the axis l of the hollow cylindrical bearing base 21, and the included angle α1 is in the range of (0°, 90°), which is the first inclined air outlet section. The axial direction of the other air outlet section intersects the axis l of the hollow cylindrical bearing base 21, and the included angle α2 is in the range of (90°, 180°), which is the second inclined air outlet section.

[0075] Optionally, a curved protrusion 104 facing the buffer section 102 is provided between the first inclined air outlet section and the second inclined air outlet section. This reduces the resistance during air intake diversion and allows for smooth air intake diversion.

[0076] Optionally, the diameter of the outlet section 103 of the throttling orifice 10 is 0.06–0.6 mm. Optionally, the diameter of the outlet section 103 of the throttling orifice 10 is 0.1–0.5 mm. Optionally, the diameter of the outlet section 103 of the throttling orifice 10 is 0.3–0.4 mm.

[0077] In other embodiments, combined with Figure 15 and Figure 16 As shown, the bearing base is a disc-shaped bearing base 22, for example, the bearing base of an axial thrust gas bearing. Multiple annular throttling orifice groups are coaxially arranged on the disc-shaped bearing base 22, and the throttling orifices 10 in adjacent annular throttling orifice groups are staggered. That is, two or more coaxial annular throttling orifice groups are provided on the disc-shaped bearing base 22.

[0078] Optionally, the center of the disc-shaped bearing base 22 is hollowed out to form an annular bearing base.

[0079] Optionally, such as Figure 15 and Figure 16 As shown, a bearing base for an axial thrust gas bearing has two coaxial annular throttling orifice groups on it; the throttling orifices 10 in the two annular throttling orifice groups are staggered.

[0080] In this embodiment, each annular orifice group may include 4 to 8 orifices 10. Optionally, each annular orifice group may include 5 to 7 orifices 10. Optionally, each annular orifice group may include 6 orifices 10.

[0081] Optionally, the multiple throttling orifices 10 in the annular throttling orifice group are evenly distributed on the disk surface of the disc-shaped bearing base 22. This uniform arrangement ensures the rigidity of the bearing base.

[0082] In this embodiment, the spacing between adjacent annular throttling orifice groups and the spacing between each throttling orifice in the same annular throttling orifice group are not limited, and can be determined according to the performance requirements of the bearing base required in actual application.

[0083] Optionally, such as Figure 15 As shown, in every two adjacent annular throttling orifice groups, the line connecting two adjacent throttling orifices (seventh throttling orifice 17, eighth throttling orifice 18) in one annular throttling orifice group with the center O of the annular bearing base forms a fan-shaped region, and one throttling orifice (ninth throttling orifice 19) in the other annular throttling orifice group is located on the center line of the fan-shaped region. This makes the distribution of lubricating gas in the bearing clearance more uniform.

[0084] In some embodiments, each throttling orifice has one or more outlet directions, which may be parallel to the axis of the disc-shaped bearing base 22, or parallel to the outlet side of the disc-shaped bearing base 22 (e.g., the outlet direction is parallel to the axis of the disc-shaped bearing base 22). Figure 16 The axes of the two orifices (pointed in the middle arrow are on the air outlet side) intersect; and the air outlet directions of multiple orifices in an annular orifice group are consistent.

[0085] In this embodiment, the outlet direction of the throttling orifice 10 can be parallel to the axis l′ of the disc-shaped bearing base 22, that is, the outlet direction of the throttling orifice 10 is perpendicular to the disc surface of the disc-shaped bearing base 22. This type of outlet direction of the throttling orifice 10 is defined as a parallel outlet direction.

[0086] In this embodiment, the outlet direction of the throttling orifice 10 can intersect with the axis l′ of the outlet side of the disc-shaped bearing base 22, and the angle formed by the intersection is not limited. Optionally, the angle (i.e., the tilt angle) can be any angle within the range of (0°, 90°). Optionally, the angle can be any angle within the range of (30°, 60°). Optionally, the angle can be 45°. This type of outlet direction of the throttling orifice 10 is defined as an inclined outlet direction.

[0087] In this embodiment, the consistent air outlet direction of multiple throttling orifices in each annular throttling orifice group means that the air outlet direction of multiple throttling orifices in one annular throttling orifice group is parallel to the axis l′ of the disc-shaped bearing base 22, or they may intersect at one point (when there is one air outlet direction of the throttling orifice) or multiple points (when there are multiple air outlet directions of the throttling orifice) on the axis l′ of the disc-shaped bearing base 22.

[0088] Optionally, when the outlet direction of the throttling orifices 10 of the multiple annular throttling orifice groups includes an inclined outlet direction, the inclination angle of the throttling orifices 10 of each annular throttling orifice group decreases from the inside to the outside along the radial direction of the disc-shaped bearing base 22. That is, the intersection point of the inclined outlet direction of the throttling orifices of the outer ring annular throttling orifice group with the axis l′ of the disc-shaped bearing base 22 is further away from the disc surface of the disc-shaped bearing base 22.

[0089] Optionally, in an annular throttling orifice group, each throttling orifice 10 has a single outlet direction, and the outlet directions of multiple throttling orifices 10 are consistent, all parallel to the axis of the disc-shaped bearing base 22.

[0090] Optionally, in an annular throttling orifice group, each throttling orifice 10 has multiple outlet directions, and one or more outlet directions are inclined outlet directions. In this embodiment, when the multiple outlet directions of the throttling orifice have one or more (i.e., two or more) inclined outlet directions, the inclination angles are different.

[0091] Optionally, in an annular throttling orifice group, the throttling orifice 10 has two outlet directions: one is a parallel outlet direction and the other is an inclined outlet direction.

[0092] The structure of the throttling orifice 10 on the bearing base of the axial thrust gas bearing in this embodiment can adopt the structure of the throttling orifice in the hollow cylindrical bearing base 21, which will not be described in detail here.

[0093] This disclosure provides a compressor that includes the aforementioned gas bearing.

[0094] The compressor using embodiments of this disclosure may include multiple gas bearings, which may include one, two, or three of the following: radial gas bearings, axial thrust gas bearings, and gas bearings with local porous throttling devices. When the gas bearings provided in this embodiment are used to support the compressor shaft, stable static and dynamic performance can be maintained even under high-speed operating conditions.

[0095] Optionally, the compressor is a centrifugal compressor.

[0096] Meanwhile, the refrigerant gas flows better within the gas bearing, further removing the frictional heat generated by the shaft rotation and further improving the high-speed operation performance of the centrifugal compressor.

[0097] This disclosure provides an air conditioning system including the aforementioned compressor.

[0098] Applying a compressor that includes the aforementioned gas bearing to an air conditioning system allows the refrigerant gas to be used as a lubricant for the gas bearing. It also removes the frictional heat generated by the refrigerant gas due to shaft rotation, further improving the high-speed operation performance of the centrifugal compressor and ensuring the stability of the air conditioning system.

[0099] The foregoing description and accompanying drawings fully illustrate embodiments of the present disclosure to enable those skilled in the art to practice them. Other embodiments may include structural and other changes. The embodiments represent only possible variations. Individual components and functions are optional unless explicitly required, and the order of operation may vary. Parts and features of some embodiments may be included or substituted for parts and features of other embodiments. Embodiments of the present disclosure are not limited to the structures described above and shown in the accompanying drawings, and various modifications and changes may be made without departing from its scope. The scope of the present disclosure is limited only by the appended claims.

Claims

1. A gas bearing, characterized in that, include: A bearing base having multiple annular throttling orifice groups thereon, wherein the throttling orifices in two adjacent annular throttling orifice groups are staggered; the annular throttling orifice group includes multiple throttling orifices, and the multiple throttling orifices are arranged in annular order; The bearing base is a hollow cylindrical bearing base; multiple annular throttling orifice groups are arranged parallel to each other along the circumference of the hollow cylindrical bearing base, and the throttling orifices in adjacent annular throttling orifice groups are staggered; wherein, each throttling orifice has one or more outlet directions, and the outlet direction of the throttling orifice intersects the axis of the bearing base, forming an angle α; the angle α is not 90°, and the outlet direction of the throttling orifice is an inclined outlet direction; in the multiple annular throttling orifice groups, the inclination angle of the inclined outlet direction of the throttling orifices in different annular throttling orifice groups is different; the inclination direction of the inclined outlet direction of the throttling orifices that are collinear in the axial direction is consistent, and the inclination direction of the inclined outlet direction of the throttling orifices in adjacent annular throttling orifice groups is opposite; Alternatively, the bearing base is a disc-shaped bearing base; multiple annular throttling orifice groups are coaxially arranged on the disc-shaped bearing base, and the throttling orifices in adjacent annular throttling orifice groups are staggered; wherein, each throttling orifice has one or more outlet directions, and the outlet direction of the throttling orifice intersects the axis of the air outlet side of the disc-shaped bearing base, and this outlet direction is defined as an inclined outlet direction; when the outlet direction of the throttling orifices of multiple annular throttling orifice groups includes an inclined outlet direction, the inclination angle of the throttling orifices of each annular throttling orifice group decreases from the inside to the outside along the radial direction of the disc-shaped bearing base.

2. The gas bearing according to claim 1, characterized in that, In the case where the bearing base is a hollow cylindrical bearing base, in every two adjacent annular throttling orifice groups, the two adjacent throttling orifices in the first annular throttling orifice group and one throttling orifice in the second annular throttling orifice group located between the two adjacent throttling orifices form an isosceles triangle, wherein one throttling orifice in the second annular throttling orifice group serves as the vertex; or... The number of annular throttling orifice groups is three or more; among the three adjacent annular throttling orifice groups, the throttling orifices in the two outer annular throttling orifice groups are collinear in the axial direction, and the line connecting the four throttling orifices in the two adjacent collinear groups forms a square; one of the throttling orifice groups in the middle annular throttling orifice group is located at the center of the square.

3. The gas bearing according to claim 1, characterized in that, In the case where the bearing base is a hollow cylindrical bearing base, the outlet direction of multiple throttling orifices in an annular throttling orifice group is consistent.

4. The gas bearing according to claim 1, characterized in that, In the case where the bearing base is a disc-shaped bearing base, in every two adjacent annular throttling orifice groups, the line connecting the two adjacent throttling orifices in one annular throttling orifice group with the center of the disc-shaped bearing base forms a fan-shaped region, and one throttling orifice in the other annular throttling orifice group is located on the center line of the fan-shaped region.

5. The gas bearing according to claim 1, characterized in that, In the case where the bearing base is a disc-shaped bearing base, the outlet directions of multiple throttling orifices in an annular throttling orifice group are consistent.

6. The gas bearing according to any one of claims 1 to 5, characterized in that, Along the intake direction, the throttle orifice includes an intake section, a buffer section, and an exhaust section. The diameter of the intake section is larger than the diameter of the exhaust section. One end of the buffer section is connected to the intake section, and the other end is connected to the exhaust section. The exhaust section includes one or more independent exhaust sections. The exhaust direction of the throttle orifice refers to the direction parallel to the axial direction of the exhaust section.

7. The gas bearing according to claim 6, characterized in that, The air outlet section includes a first inclined air outlet section and a second inclined air outlet section, and a curved protrusion facing the buffer section is provided between the first inclined air outlet section and the second inclined air outlet section.

8. The gas bearing according to claim 6, characterized in that, The diameter of the outlet section of the throttling orifice is 0.06–0.6 mm; or The diameter of the outlet section of the throttling orifice is 0.1–0.5 mm; or The diameter of the outlet section of the throttling orifice is 0.3–0.4 mm.

9. A compressor, characterized in that, Including the gas bearing as described in any one of claims 1 to 8.

10. An air conditioning system, characterized in that, Includes the compressor as described in claim 9.

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