Air suspension compressors and refrigeration equipment

Abstract

The present invention relates to an air suspension compressor and a refrigeration device. The air suspension compressor includes: a housing; a rotor rotatably disposed in the housing; a first impeller disposed at a first axial end of the rotor; a second impeller disposed at a second axial end of the rotor; a first adjustment ring disposed at the first axial end of the rotor and forming a first gap with the first impeller, the first gap being located in a first gas post-compression region, and the first adjustment ring being configured to offset part of the axial force generated by the pressure difference between the first gas pre-compression region and the first gap; and a second adjustment ring disposed at the second axial end of the rotor and forming a second gap with the second impeller, the second gap being located in a second gas post-compression region, and the second adjustment ring being configured to offset part of the axial force generated by the pressure difference between the second gas pre-compression region and the second gap. The present invention can greatly reduce the axial force and improve the reliability of the operation of the air suspension compressor through back-to-back impellers + double adjustment rings.

Description

Technical Field

[0001] The present invention relates to the field of electrical equipment, and in particular to an air suspension compressor and refrigeration equipment. Background Art

[0002] An air-suspension compressor utilizes gas bearings to support its rotor, boasting high maximum speeds and strong adaptive stability. However, as the impeller compresses gas, the motor's rotor can move, impacting the compressor's performance. Axial gas bearings are commonly used to prevent rotor movement. However, the greater the rotor's movement, the greater the likelihood of axial gas bearing failure, leading to reduced reliability in the air-suspension compressor. Summary of the Invention

[0003] Some embodiments of the present invention provide an air-suspended compressor and a refrigeration device for alleviating the problem of large rotor movement.

[0004] Some embodiments of the present invention provide an air suspension compressor comprising:

[0005] case;

[0006] a rotor rotatably disposed in the housing;

[0007] a first impeller disposed at a first axial end of the rotor, the first impeller being configured to rotate to form a first gas pre-compression region in front of the first impeller and a first gas post-compression region behind the first impeller;

[0008] a second impeller disposed at a second axial end of the rotor, the second impeller being configured to rotate to form a second gas front compression region in front of the second impeller and a second gas rear compression region behind the second impeller;

[0009] a first adjustment ring disposed at a first axial end of the rotor, wherein a first gap is formed between the first adjustment ring and the first impeller, the first gap being located in a region after compression of the first gas, and the first adjustment ring being configured to offset a portion of an axial force generated by a gas pressure difference between the region before compression of the first gas and the first gap; and

[0010] A second adjustment ring is provided at the second axial end of the rotor, and a second gap is formed between the second adjustment ring and the second impeller. The second gap is located in the area after compression of the second gas. The second adjustment ring is configured to offset part of the axial force generated by the gas pressure difference between the area before compression of the second gas and the second gap.

[0011] In some embodiments, a motor cavity is formed in the housing;

[0012] The gas pressure in the motor cavity acts on the first adjustment ring, and the first adjustment ring is configured to offset part of the axial force generated by the pressure difference between the first gas pre-compression area, the first gap, and the gas in the motor cavity, and / or,

[0013] The gas pressure in the motor cavity acts on the second adjustment ring, and the second adjustment ring is configured to offset a portion of the axial force generated by the second gas pre-compression area, the second gap, and the gas pressure difference in the motor cavity.

[0014] In some embodiments, the outer diameter of the first adjustment ring is smaller than or equal to the outer diameter of the first impeller, and / or the outer diameter of the second adjustment ring is smaller than or equal to the outer diameter of the second impeller.

[0015] In some embodiments, the air suspension compressor further comprises:

[0016] an annular first diffuser and a first comb-teeth sealing structure, wherein the outer periphery of the first diffuser is connected to the inner wall of the housing, and the first comb-teeth sealing structure is provided between the inner periphery of the first diffuser and the first adjustment ring, and / or,

[0017] An annular second diffuser and a second comb-teeth sealing structure, wherein the outer periphery of the second diffuser is connected to the inner wall of the housing, and the second comb-teeth sealing structure is provided between the inner periphery of the second diffuser and the second adjustment ring.

[0018] In some embodiments, the air suspension compressor further includes an axial bearing assembly, wherein the axial bearing assembly is located at a first axial end of the rotor and close to an axial middle portion of the housing relative to the first adjustment ring.

[0019] In some embodiments, the inner diameter of the axial bearing assembly is the same as the inner diameter of the first adjustment ring, and the outer diameter of the axial bearing assembly is larger than the outer diameter of the first adjustment ring.

[0020] In some embodiments, the axial bearing assembly comprises:

[0021] a thrust plate, provided on the rotor;

[0022] a first axial bearing located between the thrust plate and the first adjustment ring; and

[0023] The second axial bearing is located on a side of the thrust plate away from the first axial bearing.

[0024] In some embodiments, the air suspension compressor further includes a first radial bearing, wherein the first radial bearing is located at a first axial end of the rotor and close to an axial middle portion of the housing relative to the axial bearing assembly.

[0025] In some embodiments, the air suspension compressor further comprises:

[0026] a first diffuser, an outer periphery of which is connected to the inner wall of the housing, and the first adjustment ring is located between the inner periphery of the first diffuser and the rotor; and

[0027] a first bearing seat connected to the inner wall of the housing, wherein the first radial bearing is provided on the first bearing seat;

[0028] Wherein, the axial bearing assembly is located between the first diffuser and the first bearing seat.

[0029] In some embodiments, the axial bearing assembly includes a thrust plate, a first axial bearing, and a second axial bearing; the thrust plate is provided on the rotor; the first axial bearing is located between the thrust plate and the first adjustment ring, and is connected to the first diffuser; the second axial bearing is located between the thrust plate and the first bearing seat, and is connected to the first bearing seat.

[0030] In some embodiments, a third gap is formed between the first diffuser and the first bearing seat at a portion close to the rotor, the axial bearing assembly is located in the third gap, and the first diffuser and the first bearing seat are in contact with each other at a portion away from the rotor.

[0031] In some embodiments, the rotor includes a first shaft segment and a second shaft segment, the diameter of the first shaft segment is smaller than the diameter of the second shaft segment, the first adjustment ring and the axial bearing assembly are located in the first shaft segment, and the first radial bearing is located in the second shaft segment.

[0032] In some embodiments, the air suspension compressor further includes a second radial bearing, wherein the second radial bearing is located at the second axial end of the rotor and close to the axial middle of the housing relative to the second adjustment ring.

[0033] In some embodiments, the air suspension compressor further comprises:

[0034] a second diffuser, an outer periphery of which is connected to the inner wall of the housing, and the second adjustment ring is located between the inner periphery of the second diffuser and the rotor; and

[0035] The second bearing seat is connected to the inner wall of the housing, and the second radial bearing is provided on the second bearing seat; the second bearing seat is in contact with the second diffuser.

[0036] In some embodiments, the rotor has shaft sections with different diameters, and the diameter of the shaft section of the rotor where the second adjustment ring is located is smaller than the diameter of the shaft section of the rotor where the second radial bearing is located.

[0037] In some embodiments, the air suspension compressor further comprises:

[0038] a first volute, provided at a first axial end of the housing and surrounding the first impeller, wherein the first gas pre-compression region and the first gas post-compression region are located within the first volute and are in communication with each other; and / or

[0039] The second volute is provided at the second axial end of the casing and surrounds the second impeller. The second gas pre-compression area and the second gas post-compression area are located in the second volute and are connected to each other.

[0040] In some embodiments,

[0041] The material hardness of the first adjustment ring is greater than the material hardness of the first diffuser; and / or,

[0042] The material hardness of the second adjustment ring is greater than the material hardness of the second diffuser.

[0043] In some embodiments,

[0044] The difference between the hardness of the material of the first adjustment ring and the hardness of the material of the first diffuser is ≥15HRC; and / or,

[0045] A difference in hardness between the material of the second adjustment ring and the material of the second diffuser is ≥15 HRC.

[0046] In some embodiments, the axial dimension of the first gap is ≥0.6 mm, and / or the axial dimension of the second gap is ≥0.6 mm.

[0047] Some embodiments provide an air suspension compressor comprising:

[0048] a compressor body, wherein the compressor body has a gas pre-compression region and a gas post-compression region connected thereto, and the compressor body includes a rotor and an impeller; and

[0049] an adjusting ring, mounted on the rotor, the adjusting ring being located in the gas post-compression region and having an adjustable gap between the adjusting ring and the impeller to offset a portion of the axial force generated by the gas pressure difference between the gas post-compression region and the gas pre-compression region;

[0050] Wherein, the axial dimension of the adjustment gap is ≥0.6 mm.

[0051] Some embodiments provide an air suspension compressor comprising:

[0052] A compressor body having a gas pre-compression region and a gas post-compression region connected thereto, the compressor body including a rotor, an impeller, and a diffuser; and

[0053] an adjusting ring, mounted on the rotor, the adjusting ring being located in the gas post-compression region and having an adjustable gap between the adjusting ring and the impeller to offset a portion of the axial force generated by the gas pressure difference between the gas post-compression region and the gas pre-compression region;

[0054] A comb-teeth sealing structure is provided between the adjustment ring and the diffuser, and the material hardness of the adjustment ring is greater than the material hardness of the diffuser.

[0055] In some embodiments, a difference in hardness between the material of the adjustment ring and the material of the diffuser is ≥15 HRC.

[0056] Some embodiments provide an air suspension compressor comprising:

[0057] A compressor body having a gas pre-compression region and a gas post-compression region connected thereto, the compressor body including a rotor, an impeller, and a diffuser; and

[0058] an adjusting ring, mounted on the rotor, the adjusting ring being located in the gas post-compression region and having an adjustable gap between the adjusting ring and the impeller to offset a portion of the axial force generated by the gas pressure difference between the gas post-compression region and the gas pre-compression region;

[0059] Wherein, the axial dimension of the adjustment gap is ≥0.6mm;

[0060] A comb-teeth sealing structure is provided between the adjustment ring and the diffuser, and the material hardness of the adjustment ring is greater than that of the diffuser.

[0061] In some embodiments, a difference in hardness between the material of the adjustment ring and the material of the diffuser is ≥15 HRC.

[0062] Some embodiments provide an air-suspended compressor, the air-suspended compressor comprising: a compressor body and an adjustment ring;

[0063] The compressor body has a gas pre-compression area and a gas post-compression area that are connected to each other;

[0064] The adjusting ring is mounted on the rotor of the motor of the compressor body. The adjusting ring is located in the gas post-compression area and has an adjustment gap with the impeller of the compressor body to offset part of the axial force generated by the gas pressure difference between the gas post-compression area and the gas pre-compression area.

[0065] In some embodiments, the adjustment ring is fixed to the rotor of the motor by means of interference fit.

[0066] In some embodiments, the compressor body includes: a casing, a first diffuser disposed at a first opening of the casing, a first volute covered on the casing, a first impeller located in the first volute, and the motor, a first radial bearing, and an axial bearing assembly disposed in the casing;

[0067] The first axial end of the rotor of the motor passes through the first radial bearing, the axial bearing assembly, the first diffuser and is connected to the first impeller in sequence;

[0068] The adjustment ring includes a first adjustment ring, which is located in the first diffuser and forms the adjustment gap with the first impeller. The adjustment gap here is a first gap.

[0069] In some embodiments, the first radial bearing is fixed in the housing via a first bearing seat.

[0070] In some embodiments, a first step surface is provided in the housing;

[0071] The first bearing seat abuts between the first diffuser and the first step surface.

[0072] In some embodiments, a second step surface is provided on the outer wall of the rotor;

[0073] The inner ring portion of the axial bearing assembly is confined in the accommodating cavity formed between the first adjustment ring and the second step surface, and the outer ring portion of the axial bearing assembly is connected between the first diffuser and the first bearing seat.

[0074] In some embodiments, a third step surface is provided at the first opening of the housing, and a fourth step surface is provided on the outer wall of the first diffuser;

[0075] The fourth step surface is overlapped on the third step surface by a fastener.

[0076] In some embodiments, the compressor body further comprises: a second diffuser disposed at the second opening of the housing, a second volute covered on the housing, a second impeller located in the second volute, and a second radial bearing disposed in the housing;

[0077] The second axial end of the rotor passes through the second radial bearing and the second diffuser in sequence and is connected to the second impeller.

[0078] In some embodiments, the adjustment ring further includes a second adjustment ring, which is located in the second diffuser and forms the adjustment gap with the second impeller. Here, the adjustment gap is a second gap.

[0079] In some embodiments, the second radial bearing is fixed in the housing via a second bearing seat.

[0080] In some embodiments, a fifth step surface is provided in the housing;

[0081] The second bearing seat abuts between the second diffuser and the fifth step surface.

[0082] In some embodiments, a sixth step surface is provided at the second opening of the housing, and a seventh step surface is provided on the outer wall of the second diffuser;

[0083] The seventh step surface is overlapped on the sixth step surface by a fastener.

[0084] In some embodiments, an eighth step surface is provided on the outer wall of the rotor;

[0085] The second adjustment ring abuts against the eighth step surface.

[0086] Some embodiments further provide a refrigeration device, which includes the above-mentioned air suspension compressor.

[0087] Based on the above technical solution, the present invention has at least the following beneficial effects:

[0088] In some embodiments, the first impeller and the second impeller are arranged back to back and are respectively arranged at the two axial ends of the rotor. The axial forces are offset by each other by the opposite gas pressures applied to the first impeller and the second impeller, and the axial force is finally weakened to avoid the accumulation of axial forces of the air suspension compressor; since the back of the impeller will be subjected to the pressure brought by the air pressure, the adjustment ring is fixed on the rotor, and the force area of ​​the back of the impeller can be adjusted by the adjustment ring to reduce the force area of ​​the impeller and further reduce the axial force; through the back-to-back impeller structure + double adjustment ring structure, the axial force can be greatly reduced, and the bearing air film thickness and the bearing safety factor can be improved.

[0089] In some embodiments, in the above-mentioned air-suspended compressor and refrigeration equipment, an adjustment ring is mounted on the rotor of the motor. The adjustment ring is located in the gas post-compression region and has an adjustment gap with the impeller. When the rotor of the motor drives the adjustment ring and the impeller to rotate, the gas in the adjustment gap will generate pressure on the adjustment ring. The pressure is opposite in direction and has the same magnitude as the axial force borne by the part of the back side of the impeller opposite to the adjustment ring. This can offset part of the axial force generated by the gas pressure difference between the gas post-compression region and the gas pre-compression region, ensuring that the gas film formed in the axial bearing assembly has a certain thickness, thereby reducing the probability of failure of the axial bearing assembly, and improving the reliability of the operation of the air-suspended compressor. BRIEF DESCRIPTION OF THE DRAWINGS

[0090] The drawings described herein are used to provide a further understanding of the present invention and constitute a part of this application. The exemplary embodiments of the present invention and their descriptions are used to explain the present invention and do not constitute an improper limitation of the present invention. In the drawings:

[0091] Figure 1 A schematic structural diagram of an air suspension compressor according to some embodiments of the present invention;

[0092] Figure 2 for Figure 1 A local enlarged schematic diagram at position I;

[0093] Figure 3 for Figure 2 A local enlarged schematic diagram at III;

[0094] Figure 4 for Figure 1 A local enlarged schematic diagram at point II.

[0095] The reference numerals in the accompanying drawings are described as follows:

[0096] A1-area before first gas compression; B1-area after first gas compression;

[0097] A2-area before the second gas compression; B2-area after the second gas compression;

[0098] 110-motor; 111-rotor; 112-stator;

[0099] 120a-first impeller; 120b-second impeller;

[0100] 130-housing; 131-motor cavity;

[0101] 140a-first diffuser; 140b-second diffuser;

[0102] 150a-first volute; 151a-first air inlet; 152a-first air outlet;

[0103] 150b-second volute; 151b-second air inlet; 152b-second air outlet;

[0104] 160a-first radial bearing; 160b-second radial bearing;

[0105] 170- axial bearing assembly; 171- first axial bearing; 172- thrust plate; 173- second axial bearing;

[0106] 180a-first bearing seat; 180b-second bearing seat;

[0107] 190a-first gap; 190b-second gap;

[0108] 200a-first adjustment ring; 200b-second adjustment ring;

[0109] 210a-first comb tooth structure; 210b-second comb tooth structure. DETAILED DESCRIPTION

[0110] The following will be combined with the accompanying drawings in the embodiments of the present invention to clearly and completely describe the technical solutions in the embodiments. 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 any creative efforts are within the scope of protection of the present invention.

[0111] In the description of the present invention, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "up", "down", "front", "back", "left", "right", "vertical", "horizontal", "top", "bottom", "inside", "outside", "clockwise", "counterclockwise", "axial", "radial", "circumferential" and the like to indicate orientations or positional relationships based on the orientations or positional relationships shown in the accompanying drawings, and are only for the convenience of describing the present invention and simplifying the description, rather than indicating or implying that the device or element referred to must have a specific orientation, be constructed and operated in a specific orientation, and therefore should not be understood as limiting the present invention.

[0112] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of the technical features being referred to. Thus, a feature defined as "first" or "second" may explicitly or implicitly include at least one such feature. In the description of the present invention, "plurality" means at least two, such as two, three, etc., unless otherwise specifically defined.

[0113] In the present invention, unless otherwise specified or limited, the terms "installed," "connected," "connect," "fixed," etc. should be understood in a broad sense. For example, they can refer to fixed connection, detachable connection, or integration; mechanical connection, electrical connection; direct connection, or indirect connection through an intermediate medium; internal communication between two components, or interaction between two components, unless otherwise specified. Those skilled in the art will understand the specific meanings of the above terms in the present invention based on specific circumstances.

[0114] In the present invention, unless otherwise expressly specified or limited, when a first feature is "above" or "below" a second feature, it may mean that the first and second features are in direct contact, or that the first and second features are in indirect contact through an intermediary. Furthermore, when a first feature is "above," "above," or "above" a second feature, it may mean that the first feature is directly above or diagonally above the second feature, or simply means that the first feature is at a higher level than the second feature. When a first feature is "below," "below," or "below" a second feature, it may mean that the first feature is directly below or diagonally below the second feature, or simply means that the first feature is at a lower level than the second feature.

[0115] It should be noted that when an element is referred to as being "fixed to" or "disposed on" another element, it may be directly on the other element or there may be an intermediate element. When an element is considered to be "connected to" another element, it may be directly connected to the other element or there may be an intermediate element. The terms "vertical," "horizontal," "upper," "lower," "left," "right," and similar expressions used herein are for illustrative purposes only and do not represent the only implementation methods.

[0116] See Figure 1 , Figure 1 A schematic structural diagram of an air suspension compressor in some embodiments of the present invention is shown. Some embodiments of the present invention provide an air suspension compressor, which includes: a compressor body and an adjustment ring; the compressor body has connected gas pre-compression areas A1, A2 and gas post-compression areas B1, B2; the adjustment ring is mounted on the rotor 111 of the motor 110 of the compressor body, and the adjustment ring is located in the gas post-compression areas B1, B2 and has an adjustment gap with the impeller of the compressor body to offset part of the axial force generated by the gas pressure difference between the gas post-compression areas B1, B2 and the gas pre-compression areas A1, A2.

[0117] It should be noted that during the process of gas compression by the impeller of the air-suspended compressor, a pressure difference exists before and after the refrigerant gas is compressed. The rotor 111 of the motor 110 is subjected to an axial force directed from the compressed gas toward the compressed gas, causing it to move axially. In the related art, an axial gas bearing is typically used to offset this axial force. The axial gas bearing includes a thrust bearing and a thrust plate spaced along the axial direction of the rotor 111 of the motor 110. The principle of offsetting the axial force is as follows: the rotor 111 of the motor 110 rotates at high speed, driving the thrust plate to rotate. After the thrust plate reaches a certain speed, an air film is formed between the thrust plate and the surface of the thrust bearing. This air film has a certain load-bearing capacity and can support the axial force. However, the thickness of the air film is inversely proportional to the magnitude of the axial force borne by the rotor 111 of the motor 110. In other words, the greater the axial force borne by the rotor 111 of the motor 110, the smaller the thickness of the air film, and the greater the possibility of failure of the axial gas bearing.

[0118] Among them, the gas pressure in the areas B1 and B2 after gas compression is greater than the gas pressure in the areas A1 and A2 before gas compression. Then the direction of the axial force generated by the gas pressure difference between the areas B1 and B2 after gas compression and the areas A1 and A2 before gas compression is from the areas B1 and B2 after gas compression to the areas A1 and A2 before gas compression.

[0119] For example: the back of the impeller is subjected to an axial force F1 (see Figure 2 ). Furthermore, the adjustment gap between the adjustment ring and the impeller is part of the gas compression area B1. When the rotor 111 of the motor 110 drives the adjustment ring and the impeller to rotate, the gas in the adjustment gap will generate a pressure Fx1 on the adjustment ring (see Figure 2 ), the direction of Fx1 is opposite to the axial force F1 borne by the part of the back of the impeller opposite to the adjustment ring, and the magnitude is the same, so the force Fx1 will offset part of the axial force borne by the back of the impeller, which can reduce the force area of ​​the back of the impeller, that is, the pressure area of ​​the impeller borne by the axial force F1 is equal to Among them, R 叶轮 is the outer radius of the impeller, R 调节环 To adjust the outer radius of the ring, it can offset part of the axial force generated by the gas pressure difference between the gas compression area B1 and the gas compression area A1. Figure 1 The arrows in the figure represent the direction of gas flow.

[0120] As shown in the air suspension compressor above, the rotor 111 of the motor 110 is provided with an adjustment ring, which is located in the gas compression area B1, B2 and has an adjustment gap with the impeller. When the rotor 111 of the motor 110 drives the adjustment ring and the impeller to rotate, the gas in the adjustment gap will generate pressure on the adjustment ring. The pressure is opposite in direction and has the same magnitude as the axial force borne by the part of the back side of the impeller opposite to the adjustment ring. This can offset part of the axial force generated by the gas pressure difference between the gas compression area B1, B2 and the gas compression area A1, A2, thereby ensuring that the gas film formed by the axial bearing assembly 170 has a certain thickness, thereby reducing the probability of failure of the axial bearing assembly 170, thereby improving the reliability of the operation of the air suspension compressor.

[0121] Regarding the setting of the adjustment ring size, it can be seen from the above description that the axial force F1 on the impeller is equal to Then the larger the outer diameter of the adjusting ring is, the smaller the force area of ​​the impeller exerted by the axial force F1 is, and the smaller the axial force F1 is.

[0122] Since the pressure in the cavity of the motor 110 is relatively low, the compressed gas will generate a pressure difference with the gas in the cavity of the motor 110, which will then generate a pressure Fx3 on the adjustment ring (see Figure 3 ), the force direction is toward the motor cavity, and the force area of ​​the adjustment ring under the pressure Fx3 is the entire ring area of ​​the adjustment ring, that is, Among them, r 调节环 The inner radius of the adjusting ring is the smaller the outer diameter of the adjusting ring, the smaller the force-bearing area, and the smaller Fx3. As can be seen from the above, the size of the adjusting ring will affect the size of F1 and Fx3. The selection of the size of the adjusting ring requires a comprehensive evaluation based on the compressor power of different sizes and different operating conditions.

[0123] In some embodiments of the present invention, the adjustment ring is fixed to the rotor 111 of the motor 110 by an interference fit. In this way, the adjustment ring can be firmly mounted on the rotor 111 of the motor 110 to effectively rotate with the rotor 111 of the motor 110.

[0124] It should be noted that the inner diameter of the adjustment ring is smaller than the outer diameter of the rotor 111 , so that the adjustment ring and the rotor 111 are tightly connected by interference fit.

[0125] In some embodiments of the present invention, the outer diameter of the adjustment ring is smaller than or equal to the outer diameter of the impeller.

[0126] In some embodiments of the present invention, the axial dimension of the adjustment gap is ≥0.6 mm.

[0127] In some embodiments of the present invention, an air suspension compressor includes a compressor body and an adjustment ring.

[0128] The compressor body has a gas pre-compression region and a gas post-compression region that are connected to each other. The compressor body includes a rotor 111, an impeller and a diffuser.

[0129] The adjusting ring is mounted on the rotor 111 and is located in the gas post-compression region with an adjusting gap between the adjusting ring and the impeller to offset part of the axial force generated by the gas pressure difference between the gas post-compression region and the gas pre-compression region.

[0130] In some embodiments of the present invention, a comb-teeth sealing structure is provided between the adjustment ring and the diffuser, and the material hardness of the adjustment ring is greater than the material hardness of the diffuser.

[0131] Optionally, a difference between the material hardness of the adjustment ring and the material hardness of the diffuser is ≥15 HRC.

[0132] In some embodiments of the present invention, the axial dimension of the adjustment gap is ≥0.6 mm.

[0133] In some embodiments of the present invention, Figure 1 As shown, the compressor body includes: a casing 130, a first diffuser 140a arranged at a first opening of the casing 130, a first volute 150a covering the first opening of the casing 130, a first impeller 120a located in the first volute 150a, and a motor 110, a first radial bearing 160a and an axial bearing assembly 170 arranged in the casing 130; a first axial end of the rotor 111 of the motor 110 passes through the first radial bearing 160a, the axial bearing assembly 170 and the first diffuser 140a in sequence, and is connected to the first impeller 120a; the adjustment ring includes a first adjustment ring 200a, which is located between the inner periphery of the first diffuser 140a and the rotor 111, and forms a first gap 190a between the first adjustment ring 200a and the first impeller 120a. It can be understood that there is a slight gap between the first adjustment ring 200a and the first diffuser 140a, and between the first adjustment ring 200a and the axial bearing assembly 170. The width of the gap is mainly determined by the type of the compressor.

[0134] Optionally, the axial dimension of the first gap 190a is ≥0.6 mm.

[0135] It should be noted that if Figure 1 As shown, the first volute 150a has a first air inlet 151a and a first air outlet 152a. When the first impeller 120a rotates at high speed, gas enters the first volute 150a through the first air inlet 151a. The first impeller 120a, in cooperation with the first diffuser 140a, compresses the gas and discharges it through the first air outlet 152a.

[0136] Alternatively, as Figure 1As shown, the shell 130 is an irregular cylindrical structure, which can be formed by casting and mainly plays the role of supporting, protecting and shock absorbing.

[0137] Alternatively, as Figure 1 As shown, motor 110 includes a rotor 111 and a stator 112. Stator 112 is composed of windings to provide a magnetic field for rotor 111. Rotor 111 can rotate at high speed within the magnetic field. Stator 112 can be fixed to housing 130 using screws or an interference fit.

[0138] In some embodiments of the present invention, a first comb-teeth sealing structure 210a is installed between the first diffuser 140a and the first adjustment ring 200a, wherein the first comb-teeth sealing structure 210a is installed on the first diffuser 140a.

[0139] In some embodiments of the present invention, the material hardness of the first adjustment ring 200 a is greater than the material hardness of the first diffuser 140 a .

[0140] Optionally, a difference between the material hardness of the first adjustment ring 200 a and the material hardness of the first diffuser 140 a is ≥15 HRC.

[0141] Optionally, the first radial bearing 160a is a gas bearing. This type of bearing refers to a sliding bearing that uses gas as a lubricant. The most commonly used gas lubricant is air, and gases such as nitrogen, argon, hydrogen, helium, or carbon dioxide can also be used as needed. It should be noted that the first radial bearing 160a limits the rotor 111 in the radial direction of the rotor 111, while the axial bearing assembly 170 limits the rotor 111 in the axial direction (i.e., Figure 1 The rotor 111 is limited in the left and right directions (as shown).

[0142] Furthermore, in some embodiments of the present invention, Figure 1 As shown, the first radial bearing 160a is fixed in the housing 130 via a first bearing seat 180a.

[0143] Specifically in some embodiments of the present invention, such as Figure 1 As shown, a first step surface is provided on the inner wall of the housing 130, and the first bearing seat 180a is in contact between the first diffuser 140a and the first step surface, so as to facilitate the disassembly and assembly of the first bearing seat 180a.

[0144] Alternatively, as Figure 1 As shown, a ninth step is provided on the outer wall of the first bearing seat 180a, and a limiting protrusion is provided on the first diffuser 140a; the limiting protrusion abuts against the ninth step. This increases the secure installation of the first bearing seat 180a within the housing 130 and prevents shaking of the first bearing seat 180a.

[0145] Specifically in some embodiments of the present invention, such as Figure 1 As shown, a second step surface is provided on the outer wall of the rotor 111; the inner ring portion of the axial bearing assembly 170 is confined in the accommodation cavity formed between the first adjustment ring 200a and the second step surface, and the outer ring portion of the axial bearing assembly 170 is connected between the first diffuser 140a and the first bearing seat 180a. It should be noted that, as Figure 2 As shown, the axial bearing assembly 170 includes a first axial bearing 171 secured to the first diffuser 140a, a thrust plate 172 mounted on the rotor 111 of the motor 110, and a second axial bearing 173 secured to the first bearing seat 180a. As such, when the rotor 111 of the motor 110 is subjected to axial forces, a stable dynamic air film is formed between the thrust plate 172 of the axial bearing assembly 170 and the first axial bearing 171, effectively supporting the axial forces acting on the rotor 111 of the motor 110.

[0146] Specifically in some embodiments of the present invention, such as Figure 1 As shown, a third stepped surface is provided at the first opening of the housing 130, and a fourth stepped surface is provided on the outer wall of the first diffuser 140a. The fourth stepped surface is overlapped with the third stepped surface via fasteners. This securing method of the first diffuser 140a allows the first diffuser 140a to remain flush with the first opening of the housing 130, preventing excessive components of the first diffuser 140a from protruding into the first volute 150a, ensuring that compressed gas flows smoothly out of the first outlet 152a of the first volute 150a.

[0147] like Figure 1 As shown, in some embodiments of the present invention, the compressor body further includes: a second diffuser 140b arranged at the second opening of the casing 130, a second volute 150b covering the second opening of the casing 130, a second impeller 120b located in the second volute 150b, and a second radial bearing 160b arranged in the casing 130; the second axial end of the rotor 111 of the motor 110 passes through the second radial bearing 160b and the second diffuser 140b in sequence and is connected to the second impeller 120b. When the rotor 111 of the motor 110 drives the impeller to rotate, the impeller will generate axial force due to its own structure. In view of this, the present application arranges the first impeller 120a and the second impeller 120b on both sides of the rotor 111. The principle that the gas pressures acting on the first impeller 120a and the second impeller 120b are opposite can be utilized to make some of the axial forces cancel each other out, and finally weaken the axial force. This solves the problem of axial force accumulation caused by arranging the first impeller 120a and the second impeller 120b on the same side of the rotor 111 in conventional air suspension compressors.

[0148] In some embodiments of the present invention, a second comb-teeth sealing structure 210b is installed between the second diffuser 140b and the second adjustment ring 200b, wherein the second comb-teeth sealing structure 210b is installed on the second diffuser 140b.

[0149] In some embodiments of the present invention, the material hardness of the second adjustment ring 200 b is greater than the material hardness of the second diffuser 140 b .

[0150] Optionally, a difference between the material hardness of the second adjustment ring 200 b and the material hardness of the second diffuser 140 b is ≥15 HRC.

[0151] Furthermore, if Figure 1 As shown, in some embodiments of the present invention, the adjustment ring further includes a second adjustment ring 200b, and the second adjustment ring 200b is located between the inner periphery of the second diffuser 140b and the rotor 111, and a second gap 190b is formed between the second adjustment ring 200b and the second impeller 120b. The rotor 111 of the motor 110 drives the second impeller 120b to rotate at high speed, and the second diffuser 140b cooperates with the second impeller 120b to perform secondary compression on the gas sucked into the second volute 150b. Similar to the first impeller 120a, the back pressure of the second impeller 120b is greater than the pressure of the second air inlet 151b, generating an axial force F2 (such as Figure 4 (as shown), pushing the second impeller 120b toward the second air inlet 151b. The gas within the second gap 190b between the second adjustment ring 200b and the second impeller 120b generates a pressure Fx2 on the second adjustment ring 200b. This pressure Fx2 is in the opposite direction and has the same magnitude as the axial force F2 exerted on the portion of the back of the second impeller 120b opposite the second adjustment ring 200b. Therefore, this force Fx2 offsets part of the axial force F2 exerted on the back of the second impeller 120b, thereby reducing the force-bearing area of ​​the second impeller 120b and achieving the effect of reducing the axial force.

[0152] Optionally, the axial dimension of the second gap 190b is ≥0.6 mm.

[0153] Furthermore, in some embodiments of the present invention, Figure 1 As shown, the second radial bearing 160b is fixed in the housing 130 via a second bearing seat 180b.

[0154] Specifically in some embodiments of the present invention, such as Figure 1 As shown, a fifth step surface is provided on the inner wall of the housing 130, and the second bearing seat 180b is in contact between the second diffuser 140b and the fifth step surface, so as to facilitate the disassembly and assembly of the second bearing seat 180b.

[0155] Specifically in some embodiments of the present invention, such as Figure 1As shown, a sixth stepped surface is provided at the second opening of the housing 130, and a seventh stepped surface is provided on the outer wall of the second diffuser 140b. The seventh stepped surface is overlapped with the sixth stepped surface via fasteners. This securing method of the second diffuser 140b allows the second diffuser 140b to remain flush with the second opening of the housing 130, preventing excessive components of the second diffuser 140b from protruding into the second volute 150b, thereby ensuring smooth flow of compressed gas through the second outlet 152b of the second volute 150b.

[0156] Specifically in some embodiments of the present invention, such as Figure 1 As shown, an eighth step surface is provided on the outer wall of the rotor 111 of the motor 110; the second adjustment ring 200b abuts against the eighth step surface. In this way, the connection firmness of the second adjustment ring 200b to the rotor 111 of the motor 110 can be improved.

[0157] As can be seen from the above, in the process of the rotor 111 of the motor 110 driving the first impeller 120a and the second impeller 120b to rotate, the backs of the first impeller 120a and the second impeller 120b are both subjected to the axial force generated between their respective gas compression areas B1, B2 and gas pre-compression areas A1, A2, and the first impeller 120a and the second impeller 120b will also generate axial force due to their own structural reasons, as well as the axial force generated by the pressure difference between the compressed gas and the inner cavity of the motor 110, making the axial force of the compressor body complex and changeable. The direction of the final total axial force is uncertain, and may be from the primary axis to the secondary axis (i.e., from the first impeller 120a to the second impeller 120b), or from the secondary axis to the primary axis (i.e., from the second impeller 120b to the first impeller 120a). When the axial force is directed to the first impeller 120a, the small gap between the thrust plate 172 and the first axial bearing 171 will form a dynamic pressure air film to support the axial force. Similarly, when the axial force is directed toward the second impeller 120 b , a dynamic pressure air film will also be formed on the surface of the second axial bearing 173 .

[0158] The present invention effectively reduces the total axial force through the coordinated use of back-to-back impellers and dual adjustment rings, thereby keeping the bearing within a safety factor range and significantly reducing the risk of bearing failure. The outer diameter of the adjustment ring must be designed based on different operating conditions. The pressure differentials under different operating conditions generate different axial forces, and therefore the outer diameter of the adjustment ring varies.

[0159] Because an air-suspension compressor uses an impeller, diffuser, and volute to compress gas, the impeller experiences a horizontal axial force due to the pressure differential before and after refrigerant compression and the impeller's gas compression structure. This axial force is directed from the compressed refrigerant back to the compressed refrigerant, causing the rotor to move horizontally. The greater the rotor movement, the less reliable the air-suspension compressor.

[0160] In the related art, an axial bearing with a large load-bearing capacity is used to offset and adjust the axial force. This method has high requirements for the selection of bearings and is very likely to cause bearing failure.

[0161] Gas bearings utilize the high-speed rotation of the rotor, driving the thrust plate. Once the speed reaches a certain level, an air film forms on the bearing surface. This air film supports axial forces. The higher the speed, the greater the air film's bearing capacity. However, the greater the axial load, the smaller the air film thickness, and the greater the likelihood of bearing failure. Consequently, if the axial force exceeds the air film's bearing capacity, bearing failure is highly likely. Therefore, axial loads must be controlled within the gas bearing's safety factor to ensure proper operation.

[0162] Based on this, some embodiments of the present disclosure provide an air-suspended compressor, which can further balance the axial force of the compressor and alleviate the problem of large axial movement of the rotor.

[0163] like Figure 1 As shown, in some embodiments, the air suspension compressor includes a housing 130 , a rotor 111 , a first impeller 120 a and a second impeller 120 b .

[0164] The rotor 111 is rotatably disposed in the housing 130 .

[0165] The first impeller 120a is disposed at a first axial end of the rotor 111. The first impeller 120a is configured to rotate with the rotor 111 to form a first gas pre-compression region A1 in front of the first impeller 120a and a first gas post-compression region B1 behind the first impeller 120a. The front of the first impeller 120a is farther from the axial center of the housing 130 than the rear of the first impeller 120a.

[0166] The second impeller 120b is disposed at a second axial end of the rotor 111. The second impeller 120b is configured to rotate with the rotor 111 to form a second gas pre-compression region A2 in front of the second impeller 120b and a second gas post-compression region B2 behind the second impeller 120b. The front of the second impeller 120b is farther from the axial center of the housing 130 than the rear of the second impeller 120b.

[0167] The first axial end and the second axial end are two opposite ends of the rotor 111 in the axial direction.

[0168] The first adjustment ring 200a is arranged at the first axial end of the rotor 111 and is close to the axial middle part of the housing 130 relative to the first impeller 120a. The first adjustment ring 200a is configured to rotate with the rotor 111. A first gap 190a is formed between the first adjustment ring 200a and the first impeller 120a. The first gap 190a is located in the first gas post-compression area B1. The first adjustment ring 200a is configured to offset part of the axial force generated by the gas pressure difference between the first gas pre-compression area A1 and the first gap 190a.

[0169] The second adjustment ring 200b is arranged at the second axial end of the rotor 111 and is close to the axial middle part of the housing 130 relative to the second impeller 120b. The second adjustment ring 200b is configured to rotate with the rotor 111. A second gap 190b is formed between the second adjustment ring 200b and the second impeller 120b. The second gap 190b is located in the second gas post-compression area B2. The second adjustment ring 200b is configured to offset part of the axial force generated by the gas pressure difference between the second gas pre-compression area A2 and the second gap 190b.

[0170] In the above embodiment, the first impeller 120a and the second impeller 120b are arranged back to back and are respectively arranged at the two axial ends of the rotor 111. By utilizing the method of the opposite gas pressures on the first impeller 120a and the second impeller 120b, the axial forces are offset against each other, and finally the axial forces are weakened, thereby avoiding the accumulation of axial forces in the air suspension compressor.

[0171] After the impeller rotates and compresses the refrigerant gas, two regions exist: the area before and after the gas is compressed. The pressure difference between the areas before and after the refrigerant gas is compressed creates a pressure force, with the direction of the force being from the area after compression toward the area before compression.

[0172] according to Figure 1 As shown, the gas pre-compression regions A1 and A2 are located farther from the axial center of the housing 130 than the gas post-compression regions B1 and B2. Therefore, it can be seen that the back surfaces of the first impeller 120a and the second impeller 120b are both subject to pressure from the gas pressure. By providing a first adjustment ring 200a at the first axial end of the rotor 111 and a second adjustment ring 200b at the second axial end of the rotor 111, the force-bearing areas of the back surfaces of the first and second impellers 120a, 120b can be adjusted via the adjustment rings to reduce the force-bearing areas of the impellers and further reduce the axial force. By using a back-to-back impeller structure + a dual adjustment ring structure, the axial force can be greatly reduced, increasing the bearing air film thickness and the bearing safety factor. Furthermore, because the axial forces acting on the rotor 111 are complex and variable, the direction of the final total axial force is uncertain. The use of dual adjustment rings improves the axial force offsetting effect by more than two times compared to a single adjustment ring, making it more suitable for the complex and variable pressure environment within the compressor.

[0173] In some embodiments, considering the safety of the compressor operation, the axial bearing assembly for the air suspension compressor, the axial load, and the deformation of the axial bearing, the axial dimension of the first gap 190a is ≥0.6 mm.

[0174] In some embodiments, considering the safety of the compressor operation, the axial bearing assembly for the air suspension compressor, the axial load, and the deformation of the axial bearing, the axial dimension of the second gap 190b is ≥0.6 mm.

[0175] Optionally, the housing 130 is an irregular cavity part, generally cast, and plays a supporting, protective and shock-absorbing role.

[0176] In some embodiments, a motor cavity 131 is formed in the housing 130 . The motor cavity 131 is located between the first axial end and the second axial end of the rotor 111 .

[0177] The motor cavity is provided with a stator 112. The stator 112 is composed of windings and is fixed inside the housing 130 to provide a magnetic field for the rotor 111.

[0178] The rotor 111 is a shaft-like, solid part, and when in operation, performs high-speed rotation in the magnetic field provided by the stator 112 .

[0179] In some embodiments, the gas pressure in the motor cavity 131 acts on the first adjustment ring 200 a , and the first adjustment ring 200 a is configured to offset part of the axial force generated by the pressure difference between the first gas pre-compression area A1 , the first gap 190 a and the gas in the motor cavity 131 .

[0180] In some embodiments, the gas pressure in the motor cavity 131 acts on the second adjustment ring 200 b , and the second adjustment ring 200 b is configured to offset part of the axial force generated by the pressure difference between the second gas pre-compression area A2 , the second gap 190 b and the gas in the motor cavity 131 .

[0181] According to the above embodiment, the adjustment ring can also adjust the pressure generated by the pressure difference between the compressed refrigerant gas and the motor cavity. The direction of the force is from the compressed gas cavity to the motor cavity, and its force-bearing area is the area of ​​the adjustment ring.

[0182] It can be seen from the above embodiments that the axial force of the compressor is complex and changeable, and the direction of the final total axial force is uncertain. It may be directed from the primary shaft (first impeller 120a) to the secondary shaft, or from the secondary shaft (second impeller 120b) to the primary shaft (first impeller 120a). By setting a first adjustment ring 200a at a position close to the first impeller 120a and setting a second adjustment ring 200b at a position close to the second impeller 120b, the impeller axial load is reduced by back-to-back impellers + double adjustment rings, thereby alleviating the problem of excessive axial force.

[0183] In some embodiments, the outer diameter of the first adjustment ring 200 a is less than or equal to the outer diameter of the first impeller 120 a .

[0184] In some embodiments, the outer diameter of the second adjustment ring 200b is less than or equal to the outer diameter of the second impeller 120b.

[0185] Through Figure 1 The air suspension compressor shown in the figure is subjected to stress analysis. The generation of axial forces includes the following situations:

[0186] 1) The axial force generated by the pressure difference before and after the impeller compresses the refrigerant, the direction of the force is from after compression to before compression.

[0187] 2) When the impeller rotates, the impeller structure generates an axial force. The direction of the axial force is not specified and is determined by the impeller profile.

[0188] 3) The pressure generated by the pressure difference between the compressed area of ​​the refrigerant gas and the motor cavity, the direction of the force is from the compressed gas cavity to the motor cavity.

[0189] As can be seen from the above-described axial force generation, the synthesis of the axial force on rotor 111 is complex, and the magnitude and direction of the total axial force vary under different operating conditions. The dual adjustment rings adjust two forces: the axial force on the impeller caused by the pressure differential between the refrigerant gas before and after compression, and the axial force on the adjustment ring caused by the pressure differential between the refrigerant gas after compression and the motor cavity. Therefore, the outer diameter of the adjustment ring must be designed according to different operating conditions. Different pressure differentials under different operating conditions generate different axial forces, and therefore different outer diameters of the adjustment rings are required.

[0190] In some embodiments, the air suspension compressor further includes an annular first diffuser 140a and a first comb-tooth seal structure 210a. The outer periphery of the first diffuser 140a is connected to the inner wall of the housing 130, and the first comb-tooth seal structure 210a is disposed between the inner periphery of the first diffuser 140a and the first adjustment ring 200a. The first comb-tooth seal structure 210a seals the motor cavity 121 and the first post-gas compression region B1.

[0191] In some embodiments, the material hardness of the first adjustment ring 200 a is greater than that of the first diffuser 140 a to prevent the first adjustment ring 200 a from causing dry friction and seizure with the mating first diffuser 140 a during rotation of the rotor 111 .

[0192] Optionally, a difference between the material hardness of the first adjustment ring 200 a and the material hardness of the first diffuser 140 a is ≥15 HRC.

[0193] In some embodiments, the air suspension compressor further includes an annular second diffuser 140b and a second comb-tooth seal structure 210b. The outer periphery of the second diffuser 140b is connected to the inner wall of the housing 130, and the second comb-tooth seal structure 210b is disposed between the inner periphery of the second diffuser 140b and the second adjustment ring 200b. The second comb-tooth seal structure 210b seals the motor cavity 121 and the second post-gas compression region B2.

[0194] In some embodiments, the material hardness of the second adjustment ring 200 b is greater than that of the second diffuser 140 b to prevent the second adjustment ring 200 b from causing dry friction and seizure with the second diffuser 140 b during rotation of the rotor 111 .

[0195] Optionally, a difference between the material hardness of the second adjustment ring 200 b and the material hardness of the second diffuser 140 b is ≥15 HRC.

[0196] In some embodiments, the air suspension compressor further includes an axial bearing assembly 170, which is located at a first axial end of the rotor 111 and near the axial center of the housing 130 relative to the first adjustment ring 200a. The axial bearing assembly 170 is provided to balance the axial force of the rotor 111.

[0197] In some embodiments, the inner diameter of the axial bearing assembly 170 is the same as the inner diameter of the first adjustment ring 200 a , and the outer diameter of the axial bearing assembly 170 is larger than the outer diameter of the first adjustment ring 200 a .

[0198] In some embodiments, the axial bearing assembly 170 includes a thrust plate 172 , a first axial bearing 171 , and a second axial bearing 173 .

[0199] The thrust plate 172 is disposed on the rotor 111 and is configured to rotate along with the rotor 111 .

[0200] The first axial bearing 171 is located between the thrust plate 172 and the first adjustment ring 200 a.

[0201] The second axial bearing 173 is located on a side of the thrust plate 172 away from the first axial bearing 171 .

[0202] In some embodiments, the air suspension compressor further includes a first radial bearing 160a, which is located at a first axial end of the rotor 111 and near the axial center of the housing 130 relative to the axial bearing assembly 170. The radial force applied to the rotor 111 is adjusted by providing the first radial bearing 160a.

[0203] In some embodiments, the air suspension compressor further includes a first bearing seat 180 a , the first bearing seat 180 a is connected to the inner wall of the housing 130 , and the first radial bearing 160 a is disposed on the first bearing seat 180 a .

[0204] The outer periphery of the first diffuser 140 a is connected to the inner wall of the housing 130 , and the first adjustment ring 200 a is located between the inner periphery of the first diffuser 140 a and the rotor 111 .

[0205] The axial bearing assembly 170 is located between the first diffuser 140a and the first bearing seat 180a and has a compact structure.

[0206] In some embodiments, a thrust plate 172 is disposed on the rotor 111 and is configured to rotate with the rotor 111. A first axial bearing 171 is located between the thrust plate 172 and the first adjustment ring 200a and is connected to the first diffuser 140a. A second axial bearing 173 is located between the thrust plate 172 and the first bearing seat 180a and is connected to the first bearing seat 180a.

[0207] The thrust plate 172 is fixed to the rotor 111, which drives the thrust plate 172 to rotate at high speed. When axial force is applied to the first impeller 120a, a dynamic pressure film forms in the small gap between the thrust plate 172 and the first axial bearing 171, supporting the axial force. Similarly, when axial force is applied to the second impeller 120b, a dynamic pressure film also forms on the surface of the second axial bearing 173, supporting the axial force.

[0208] In some embodiments, a third gap is formed between the first diffuser 140a and the first bearing seat 180a near the rotor 111, and the axial bearing assembly 170 is located in the third gap. The first diffuser 140a and the first bearing seat 180a are in close contact with each other at locations away from the rotor 111, resulting in a compact structure that does not occupy excessive axial space of the rotor 111, thereby preventing the rotor 111 from being too long.

[0209] In some embodiments, rotor 111 includes a first shaft segment and a second shaft segment. The diameter of the first shaft segment is smaller than that of the second shaft segment. First adjustment ring 200a and axial bearing assembly 170 are located in the first shaft segment, and first radial bearing 160a is located in the second shaft segment. Axial bearing assembly 170 is axially limited by first adjustment ring 200a and a step between the first and second shaft segments.

[0210] In some embodiments, the air suspension compressor further includes a second radial bearing 160 b , which is located at the second axial end of the rotor 111 and close to the axial center of the housing 130 relative to the second adjustment ring 200 b .

[0211] In some embodiments, the air suspension compressor further includes a second diffuser 140 b , the outer periphery of the second diffuser 140 b is connected to the inner wall of the casing 130 , and the second adjustment ring 200 b is located between the inner periphery of the second diffuser 140 b and the rotor 111 .

[0212] In some embodiments, the air suspension compressor further includes a second bearing seat 180b, which is connected to the inner wall of the housing 130, and the second radial bearing 160b is disposed on the second bearing seat 180b; the second bearing seat 180b is fitted with the second diffuser 140b, making the internal structure of the air suspension compressor compact and shortening the overall length.

[0213] The first bearing seat 180a and the second bearing seat 180b are machined parts, fixed in the housing 130, and mainly play a fixing and supporting role.

[0214] In some embodiments, the rotor 111 has shaft sections with different diameters, and the diameter of the shaft section of the rotor 111 where the second adjustment ring 200 b is located is smaller than the diameter of the shaft section of the rotor 111 where the second radial bearing 160 b is located.

[0215] In some embodiments, the air suspension compressor further includes a first volute 150a. The first volute 150a is disposed at a first axial end of the housing 130 and surrounds the first impeller 120a. The first gas pre-compression region A1 and the first gas post-compression region B1 are located within the first volute 150a and communicate with each other. The first gas pre-compression region A1 and the first gas post-compression region B1 form a first gas pre-compression chamber and a first gas post-compression chamber within the first volute 150a, respectively.

[0216] In some embodiments, the air suspension compressor further includes a second volute 150b, which is disposed at the second axial end of the housing 130 and surrounds the second impeller 120b. The second gas pre-compression region A2 and the second gas post-compression region B2 are located within the second volute 150b and communicate with each other. The second gas pre-compression region A2 and the second gas post-compression region B2 correspondingly form a second gas pre-compression chamber and a second gas post-compression chamber within the second volute 150b.

[0217] The following is combined with Figures 1 to 4 Some specific embodiments of an air suspension compressor are described.

[0218] like Figure 1 As shown, the rotor 111 is rotatably disposed in the housing 130. The first axial end of the housing 130 is provided with a first volute 150a, and the second axial end of the housing 130 is provided with a second volute 150b. The first axial end and the second axial end are opposite ends of the housing 130 along the axial direction of the rotor 111.

[0219] A first impeller 120a is provided at the first axial end of the rotor 111. The first impeller 120a is located within the first volute 150a. The first impeller 120a forms a first gas pre-compression region A1 and a first gas post-compression region B1 that correspond to the first gas pre-compression chamber and the first gas post-compression chamber within the first volute 150a, respectively. The first volute 150a is provided with a first air inlet 151a and a first air outlet 152a. The first air inlet 151a communicates with the first gas pre-compression chamber, while the first air outlet 152a communicates with the first gas post-compression chamber.

[0220] A second impeller 120b is provided at the second axial end of the rotor 111. The second impeller 120b is located within the second volute 150b. The second impeller 120b forms a second gas pre-compression region A2 and a second gas post-compression region B2 that correspond to the second gas pre-compression chamber and the second gas post-compression chamber within the second volute 150b, respectively. The second volute 150b is provided with a second air inlet 151b and a second air outlet 152b. The second air inlet 151b communicates with the second gas pre-compression chamber, while the second air outlet 152b communicates with the second gas post-compression chamber.

[0221] A first adjustment ring 200a is installed at the first axial end of the rotor 111. The first adjustment ring 200a is located near the axial center of the housing 130 relative to the first impeller 120a. A first diffuser 140a is installed within the housing 130, with a first comb seal 210a located between the first diffuser 140a and the first adjustment ring 200a. A first bearing seat 180a is installed on one side of the first diffuser 140a near the axial center of the housing 130. A first radial bearing 160a is located on the first axial seat 180a. An axial bearing assembly 170 is installed between the first diffuser 140a and the first axial seat 180a near the rotor 111. The axial bearing assembly 170 includes a thrust plate 172, a first axial bearing 171, and a second axial bearing 173. The thrust plate 172 is installed on the rotor 111 and is configured to rotate with the rotor 111. The first axial bearing 171 is located between the thrust plate 172 and the first adjustment ring 200a and is connected to the first diffuser 140a. The second axial bearing 173 is located between the thrust plate 172 and the first bearing seat 180a and is connected to the first bearing seat 180a.

[0222] A second adjustment ring 200b is provided at the second axial end of the rotor 111. The second adjustment ring 200b is located near the axial center of the housing 130 relative to the second impeller 120b. A second diffuser 140b is installed within the housing 130, with a second comb seal structure 210b located between the second diffuser 140b and the second adjustment ring 200b. A second bearing seat 180b is provided on one side of the second diffuser 140b near the axial center of the housing 130, with a second radial bearing 160b mounted on the second axial seat 180b.

[0223] The rotor 111 rotates at high speed, driving the first impeller 120a to rotate. As the first impeller 120a rotates at high speed, refrigerant gas enters the first volute 150a through the first air inlet 151a. The first impeller 120a, in conjunction with the first diffuser 140a, compresses the refrigerant gas. After being compressed by the first impeller 120a and the first diffuser 140a, the refrigerant gas becomes high-temperature, high-pressure refrigerant gas.

[0224] like Figure 2 As shown, a pressure difference is formed between the first gas pre-compression area A1 and the first gas post-compression area B1, and the back of the first impeller 120a is subjected to a horizontal force F1, pushing the first impeller 120a toward the first air inlet 151a.

[0225] Both the first diffuser 140a and the second diffuser 140b are part of the stator 112 and are fixed to the inner wall of the housing 130. A first adjustment ring 200a is fixed to a first axial end of the rotor 111. A first gap 190a between the first adjustment ring 200a and the first impeller 120a contains compressed gas, forming a small air cavity. The first adjustment ring 200a rotates with the rotor 111, reducing the force applied to the first impeller 120a.

[0226] Because both the first impeller 120a and the first adjustment ring 200a are rotors 111 and rotate with them, the gas generates forces Fx1 of equal magnitude and opposite directions on the first impeller 120a and the first adjustment ring 200a, respectively. These forces cancel each other out. At this point, the pressure area exerted by Fx1 on the first impeller 120a equals the area of ​​the first impeller 120a minus the area of ​​the first adjustment ring 200a. Therefore, the force area exerted on the first impeller 120a can be adjusted by increasing the outer diameter of the first adjustment ring 200a. A larger first adjustment ring 200a results in a smaller Fx1.

[0227] like Figure 3 As shown, due to the relatively low pressure in the motor cavity 131, the compressed refrigerant gas creates a pressure differential with the gas in the motor cavity 131, generating a pressure Fx3 on the first adjustment ring 200a. The force applied to the first adjustment ring 200a is applied over the entire area of ​​the first adjustment ring 200a, and the force is directed toward the motor cavity 131. The force applied to the first adjustment ring 200a is adjusted by adjusting its size. The smaller the first adjustment ring 200a, the smaller the force applied to the first adjustment ring 200a, and the smaller Fx3.

[0228] As can be seen above, the size of the first adjustment ring 200a affects the sizes of F1 and Fx3. The size of the first adjustment ring 200a requires a comprehensive evaluation based on the compressor power and operating conditions, as the pressure differential between the impeller shroud and impeller back, or the pressure under different operating conditions, varies with different cooling capacities and operating conditions.

[0229] Generally speaking, the inner diameter of the first adjustment ring 200a must not be smaller than the outer diameter of the rotor 111 at the mating location, and the outer diameter of the first adjustment ring 200a must not be larger than the outer diameter of the first impeller 120a.

[0230] like Figure 1 As shown, rotor 111 rotates at high speed, driving second impeller 120b to rotate. When second impeller 120b rotates at high speed, refrigerant gas enters second volute 150b through second air inlet 151b. Second impeller 120b, in conjunction with second diffuser 140b, compresses the refrigerant gas. After being compressed by second impeller 120b and second diffuser 140b, the refrigerant gas becomes high-temperature, high-pressure refrigerant gas.

[0231] like Figure 3 As shown, similar to the force analysis at the first impeller 120a, a pressure difference is formed between the second gas pre-compression area A2 and the second gas post-compression area B2, and the back of the second impeller 120b is subjected to a horizontal force F2, pushing the second impeller 120b toward the second air inlet 151b.

[0232] The second adjustment ring 200b is fixed to the second axial end of the rotor 111. The second gap 190b between the second adjustment ring 200b and the second impeller 120b contains compressed gas, forming a small secondary air cavity. The second adjustment ring 200b rotates with the rotor 111, reducing the force applied to the second impeller 120b.

[0233] Since both the second impeller 120b and the second adjustment ring 200b are rotors 111 and rotate with them, the gas generates equal and opposite forces Fx2 on the second impeller 120b and the second adjustment ring 200b, respectively. These forces cancel each other out. At this point, the pressure area of ​​F2 on the second impeller 120b equals the area of ​​the second impeller 120b minus the area of ​​the second adjustment ring 200b. Therefore, the pressure area of ​​the second impeller 120b can be adjusted by increasing the outer diameter of the second adjustment ring 200b. A larger second adjustment ring 200b results in a smaller F2.

[0234] It can be seen that the force analysis of the second adjustment ring 200b is similar to that of the first adjustment ring 200a.

[0235] By means of the back-to-back first impeller 120a and the second impeller 120b, F1 and F2 are in opposite directions, which can offset a part of the axial force to a certain extent, thereby reducing the axial force.

[0236] The material of the first adjustment ring 200a and the second adjustment ring 200b should be slightly harder than the material used for the diffuser at the corresponding position. Generally, the hardness difference between the two materials should be ≥15HRC to prevent the adjustment rings from causing dry friction and seizure with the mating diffuser during the rotation of the rotor 111.

[0237] Taking into account the safety of compressor operation, considering the structure of the axial bearing assembly for the air suspension compressor, the axial load and the deformation of the axial bearing, the distance between the impeller, the diffuser and the adjusting ring should be ≥0.6mm.

[0238] In summary, the axial load composite matching structure of the back-to-back impellers and the double adjustment rings can reduce the axial force of the rotor 111, alleviate the axial bearing load, and thicken the bearing air film, thereby keeping the bearing within the safety factor range and greatly reducing the risk of bearing failure.

[0239] Some embodiments of the present invention further provide a refrigeration device, which includes the air suspension compressor in any of the above embodiments.

[0240] In the air suspension compressor in the above embodiment, the rotor 111 of the motor 110 is provided with an adjustment ring, which is located in the gas compression area B1, B2 and has an adjustment gap (first gap 190a, second gap 190b) between the adjustment ring and the impeller. When the rotor 111 of the motor 110 drives the adjustment ring and the impeller to rotate, the gas in the adjustment gap will generate pressure on the adjustment ring. The pressure is opposite in direction and has the same magnitude as the axial force borne by the part of the back of the impeller opposite to the adjustment ring. This can offset part of the axial force generated by the gas pressure difference between the gas compression area B1, B2 and the gas compression area A1, A2, thereby ensuring that the gas film formed by the axial bearing assembly 170 has a certain thickness, thereby reducing the probability of failure of the axial bearing assembly 170, thereby improving the reliability of the operation of the air suspension compressor.

[0241] As an example, the refrigeration equipment involved in the present invention may be an electrical appliance such as an air conditioner or a refrigerator.

[0242] Based on the above-mentioned embodiments of the present invention, unless explicitly denied, the technical features of one embodiment may be beneficially combined with one or more other embodiments.

[0243] 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 the preferred embodiments, ordinary technicians in the field should understand that the specific implementation methods of the present invention can still be modified or some technical features can be replaced by equivalents without departing from the spirit of the technical solution of the present invention. They should all be included in the scope of the technical solution for protection of the present invention.

Claims

1. An air suspension compressor, characterized in that: include: Housing (130); A rotor (111) rotatably disposed in the housing (130); a first impeller (120a) disposed at a first axial end of the rotor (111), the first impeller (120a) being configured to rotate to form a first gas front compression region (A1) in front of the first impeller (120a) and a first gas rear compression region (B1) behind the first impeller (120a); a second impeller (120b) disposed at a second axial end of the rotor (111), the second impeller (120b) being configured to rotate to form a second gas front compression region (A2) in front of the second impeller (120b) and a second gas rear compression region (B2) behind the second impeller (120b); a first adjustment ring (200a) fixedly disposed at a first axial end of the rotor (111), forming a first gap (190a) between the first adjustment ring (200a) and the first impeller (120a), the first gap (190a) being located in the first gas post-compression region (B1), and the first adjustment ring (200a) being configured to offset a portion of the axial force generated by the gas pressure difference between the first gas pre-compression region (A1) and the first gap (190a); as well as a second adjustment ring (200b) fixedly disposed at a second axial end of the rotor (111), wherein a second gap (190b) is formed between the second adjustment ring (200b) and the second impeller (120b), wherein the second gap (190b) is located in the second gas post-compression region (B2), and the second adjustment ring (200b) is configured to offset a portion of the axial force generated by the gas pressure difference between the second gas pre-compression region (A2) and the second gap (190b); an annular first diffuser (140a), wherein the first adjustment ring (200a) is located between the inner periphery of the first diffuser (140a) and the rotor (111); An annular second diffuser (140b), wherein the second adjustment ring (200b) is located between the inner periphery of the second diffuser (140b) and the rotor (111).

2. The air suspension compressor according to claim 1, characterized in that: A motor cavity (131) is formed in the housing (130); The gas pressure in the motor cavity (131) acts on the first adjustment ring (200a), and the first adjustment ring (200a) is configured to offset part of the axial force generated by the pressure difference between the first gas pre-compression area (A1), the first gap (190a) and the gas in the motor cavity (131), and / or, The gas pressure in the motor cavity (131) acts on the second adjustment ring (200b), and the second adjustment ring (200b) is configured to offset part of the axial force generated by the pressure difference between the second gas front compression area (A2), the second gap (190b) and the gas in the motor cavity (131).

3. The air suspension compressor according to claim 1, characterized in that: The outer diameter of the first adjustment ring (200a) is smaller than or equal to the outer diameter of the first impeller (120a), and / or the outer diameter of the second adjustment ring (200b) is smaller than or equal to the outer diameter of the second impeller (120b).

4. The air suspension compressor according to claim 1, characterized in that: Also includes: a first comb-teeth sealing structure (210a), the outer periphery of the first diffuser (140a) is connected to the inner wall of the housing (130), the first comb-teeth sealing structure (210a) is provided between the inner periphery of the first diffuser (140a) and the first adjustment ring (200a), and / or, A second comb-teeth sealing structure (210b), the outer periphery of the second diffuser (140b) is connected to the inner wall of the housing (130), and the second comb-teeth sealing structure (210b) is provided between the inner periphery of the second diffuser (140b) and the second adjustment ring (200b).

5. The air suspension compressor according to claim 1, characterized in that: It also includes an axial bearing assembly (170), which is located at a first axial end of the rotor (111) and close to the axial middle of the housing (130) relative to the first adjustment ring (200a).

6. The air suspension compressor according to claim 5, characterized in that: The inner diameter of the axial bearing assembly (170) is the same as the inner diameter of the first adjustment ring (200a), and the outer diameter of the axial bearing assembly (170) is larger than the outer diameter of the first adjustment ring (200a).

7. The air suspension compressor according to claim 5, characterized in that: The axial bearing assembly (170) comprises: A thrust plate (172) is provided on the rotor (111); a first axial bearing (171) located between the thrust plate (172) and the first adjustment ring (200a); and The second axial bearing (173) is located on a side of the thrust plate (172) away from the first axial bearing (171).

8. The air suspension compressor according to claim 5, characterized in that: The invention also includes a first radial bearing (160a), which is located at a first axial end of the rotor (111) and close to the axial middle of the housing (130) relative to the axial bearing assembly (170).

9. The air suspension compressor according to claim 8, characterized in that: The outer periphery of the first diffuser (140a) is connected to the inner wall of the housing (130); and The air suspension compressor further comprises: a first bearing seat (180a) connected to the inner wall of the housing (130), and the first radial bearing (160a) is provided on the first bearing seat (180a); Wherein, the axial bearing assembly (170) is located between the first diffuser (140a) and the first bearing seat (180a).

10. The air suspension compressor according to claim 9, characterized in that: The axial bearing assembly (170) includes a thrust plate (172), a first axial bearing (171) and a second axial bearing (173); the thrust plate (172) is provided on the rotor (111); the first axial bearing (171) is located between the thrust plate (172) and the first adjustment ring (200a), and is connected to the first diffuser (140a); the second axial bearing (173) is located between the thrust plate (172) and the first bearing seat (180a), and is connected to the first bearing seat (180a).

11. The air suspension compressor according to claim 9, characterized in that: A third gap is formed between the first diffuser (140a) and the first bearing seat (180a) at a position close to the rotor (111), the axial bearing assembly (170) is located in the third gap, and the first diffuser (140a) and the first bearing seat (180a) are in contact with each other at a position away from the rotor (111).

12. The air suspension compressor according to claim 8, characterized in that: The rotor (111) comprises a first shaft segment and a second shaft segment, the diameter of the first shaft segment is smaller than the diameter of the second shaft segment, the first adjustment ring (200a) and the axial bearing assembly (170) are located in the first shaft segment, and the first radial bearing (160a) is located in the second shaft segment.

13. The air suspension compressor according to claim 1, characterized in that: It also includes a second radial bearing (160b), which is located at the second axial end of the rotor (111) and close to the axial middle of the housing (130) relative to the second adjustment ring (200b).

14. The air suspension compressor according to claim 13, characterized in that: The outer periphery of the second diffuser (140b) is connected to the inner wall of the housing (130); and The air suspension compressor further includes: a second bearing seat (180b) connected to the inner wall of the housing (130); the second radial bearing (160b) is arranged on the second bearing seat (180b); and the second bearing seat (180b) is fitted with the second diffuser (140b).

15. The air suspension compressor according to claim 13, characterized in that: The rotor (111) has shaft sections with different diameters, and the diameter of the shaft section of the rotor (111) where the second adjustment ring (200b) is located is smaller than the diameter of the shaft section of the rotor (111) where the second radial bearing (160b) is located.

16. The air suspension compressor according to claim 1, characterized in that: Also includes: a first volute (150a) provided at a first axial end of the housing (130) and surrounding the first impeller (120a), wherein the first gas pre-compression region (A1) and the first gas post-compression region (B1) are located within the first volute (150a) and are in communication with each other; and / or The second volute (150b) is provided at the second axial end of the housing (130) and surrounds the second impeller (120b); the second gas pre-compression area (A2) and the second gas post-compression area (B2) are located in the second volute (150b) and are connected to each other.

17. The air suspension compressor according to claim 4, characterized in that: The material hardness of the first adjustment ring (200a) is greater than the material hardness of the first diffuser (140a); and / or, The material hardness of the second adjustment ring (200b) is greater than the material hardness of the second diffuser (140b).

18. The air suspension compressor according to claim 17, characterized in that: The difference between the material hardness of the first adjustment ring (200a) and the material hardness of the first diffuser (140a) is ≥15HRC; and / or, The difference between the material hardness of the second adjustment ring (200b) and the material hardness of the second diffuser (140b) is ≥15HRC.

19. The air suspension compressor according to claim 1, characterized in that: The axial dimension of the first gap (190a) is ≥0.6 mm, and / or the axial dimension of the second gap (190b) is ≥0.6 mm.

20. A refrigeration device, characterized in that: The refrigeration equipment comprises the air suspension compressor according to any one of claims 1 to 19.

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