Rotor shaft supporting device and compressor

Abstract

The invention discloses a rotor shaft supporting device and a compressor. The compressor comprises a bearing assembly, a thrust disc and a gas compression assembly. The bearing assembly comprises a support component, a magnetic pole plate and a protective bearing, the support component comprises a first magnetic pole part, a protective bearing mounting part and a sealing part, the first magnetic pole part and the sealing part are oppositely arranged in the axial direction of the protective bearing, the protective bearing is mounted on the protective bearing mounting part, and the first magnetic pole part is opposite to and connected with the magnetic pole plate; at least two of the first magnetic pole part, the protective bearing mounting part and the sealing part are integrally formed. At least two of the first magnetic pole part, the protective bearing mounting part and the sealing part are integrally formed, so that the at least two integrally formed parts share one part, and the size from the magnetic pole plate to the sealing part in the length direction of the rotor shaft is reduced.

Description

Technical Field

[0001] The present invention relates to the technical field of compressors, and in particular to a rotor shaft supporting device and a compressor. Background Art

[0002] This section merely provides background information related to the present disclosure and is not necessarily prior art.

[0003] High-power, high-pressure ratio compressors usually have high speeds and large rotor masses, making rotor dynamics design a difficult point. How to keep the compressor's operating frequency away from the rotor's natural frequency to solve the resonance problem has always been an industry challenge. Generally, the rotor's axial length is inversely proportional to the rotor's natural frequency.

[0004] Currently, the right magnetic pole plate of the compressor's axial magnetic bearing is connected to the protective bearing seat. A wheel back sealing plate is also installed between the protective bearing seat and the impeller, which seals the impeller's back. However, the right magnetic pole plate, protective bearing seat, and wheel back sealing plate of the axial magnetic bearing are arranged in sequence in the axial direction, occupying a large amount of axial space, which in turn increases the length of the rotor and affects the rotor's natural frequency. Summary of the Invention

[0005] The object of the present invention is to at least solve the problem of excessively long rotors in compressors. This object is achieved through the following technical solutions:

[0006] A first aspect of the present invention provides a compressor, comprising:

[0007] A bearing assembly includes a support member, a magnetic pole plate and a protective bearing. The support member includes a first magnetic pole portion, a protective bearing mounting portion and a sealing portion. The first magnetic pole portion and the sealing portion are arranged opposite to each other along the axial direction of the protective bearing. The protective bearing is mounted on the protective bearing mounting portion. The first magnetic pole portion is opposite to and connected to the magnetic pole plate. At least two of the first magnetic pole portion, the protective bearing mounting portion and the sealing portion are integrally formed.

[0008] In a compressor according to an embodiment of the present invention, at least two of the first magnetic pole portion, the protective bearing mounting portion, and the sealing portion are integrally formed. This allows the at least two integrally formed parts to share a portion, eliminating the need for screw connection. This reduces the length of the protective bearing from the magnetic pole plate to the sealing portion, making the structure more compact and reducing the axial space occupied by the bearing assembly within the compressor. This reduces the overall axial size of the compressor and reduces the length of the rotor. Furthermore, the first magnetic pole portion constitutes a portion of the axial magnetic bearing of the second magnetic pole portion. When the first magnetic pole portion and the protective bearing mounting portion are integrally formed, the concentricity of the protective bearing and the axial magnetic bearing can be improved. Furthermore, the integrally formed structure reduces the number of parts, facilitating assembly and disassembly.

[0009] In some embodiments of the present invention, the first magnetic pole portion and the protective bearing mounting portion are integrally formed; or, the protective bearing mounting portion and the sealing portion are integrally formed; or, the first magnetic pole portion and the sealing portion are integrally formed; or, the first magnetic pole portion, the protective bearing mounting portion and the sealing portion are integrally formed.

[0010] In some embodiments of the present invention, the compressor further comprises:

[0011] The gas compression component comprises an impeller, which is arranged on a side of the support component away from the magnetic pole plate. The wheel back of the impeller is opposite to the sealing part and rotates in sealing cooperation.

[0012] In some embodiments of the present invention, the protective bearing mounting portion has a bearing mounting hole, and the protective bearing is located in the bearing mounting hole and cooperates with the inner circumferential surface of the bearing mounting hole;

[0013] The protective bearing has a first shaft mounting hole;

[0014] The gas compression assembly further includes a rotor, which includes a rotor shaft. One end of the rotor shaft passes through the first shaft mounting hole and is fixedly connected to the impeller.

[0015] In some embodiments of the present invention, the magnetic pole plate has a second magnetic pole portion, and the second magnetic pole portion is arranged opposite to and spaced from the first magnetic pole portion along the axial direction of the protective bearing;

[0016] The gas compression assembly further includes a thrust plate, which is fixedly sleeved on the rotor shaft, is located between the first magnetic pole portion and the second magnetic pole portion, and is movable relative to the support member in an axial direction of the protective bearing, the first magnetic pole portion and the second magnetic pole portion are respectively configured to adjust the position of the thrust plate by magnetic force, and the thrust plate has a second shaft mounting hole;

[0017] The rotor shaft passes through the second shaft mounting hole and is fixedly connected to the thrust plate.

[0018] In some embodiments of the present invention, the sealing portion comprises:

[0019] The multiple circles of first protrusions are arranged coaxially with the protective bearing and are spaced apart along the radial direction of the rotor shaft;

[0020] The back of the impeller is provided with multiple circles of second protrusions, which are arranged coaxially with the rotor shaft. Along the radial direction of the rotor shaft, the multiple circles of second protrusions are arranged at intervals, and at least one circle of second protrusions is provided between two adjacent circles of first protrusions.

[0021] In some embodiments of the present invention, the multiple circles of first protrusions are arranged flush with one end facing away from the magnetic pole plate; and / or the multiple circles of second protrusions are arranged flush with one end facing the magnetic pole plate.

[0022] In some embodiments of the present invention, the sealing portion further comprises:

[0023] Multiple circles of first sealing teeth are arranged coaxially with the protective bearing and spaced apart along the radial direction of the rotor shaft. At least one circle of first sealing teeth is formed on the end of the first protrusion away from the magnetic pole plate.

[0024] In some embodiments of the present invention, the first sealing teeth formed on the first protrusion are multiple circles, and the first sealing teeth are inclined outward along the radial direction of the rotor shaft.

[0025] In some embodiments of the present invention, the ends of the multiple-ring first sealing teeth facing away from the magnetic pole plate are arranged flush.

[0026] In some embodiments of the present invention, the back of the impeller is provided with multiple circles of second sealing teeth, which are arranged coaxially with the rotor shaft. Along the radial direction of the rotor shaft, the multiple circles of second sealing teeth are arranged at intervals, and at least one circle of second sealing teeth is formed on one end of the second protrusion facing the magnetic pole plate.

[0027] In some embodiments of the present invention, the second sealing teeth formed on the second protrusion are multiple circles, and the second sealing teeth are inclined outward along the radial direction of the rotor shaft.

[0028] In some embodiments of the present invention, multiple circles of second sealing teeth are arranged flush with one end of the magnetic pole plate.

[0029] In some embodiments of the present invention, the support member has an air duct extending along the radial direction of the protective bearing, the air duct passes through the inner circumferential surface of the support member and the outer circumferential surface of the support member along the radial direction of the protective bearing, and along the axial direction of the protective bearing, the air duct is spaced apart from or adjacent to the protective bearing.

[0030] In some embodiments of the present invention, there are multiple air ducts, and the multiple air ducts are arranged at intervals along the circumferential direction of the protective bearing.

[0031] In some embodiments of the present invention, the support member has a cooling channel, and the cooling channel is provided with a cooling medium inlet and a cooling medium outlet.

[0032] In some embodiments of the present invention, the cooling channel is provided around the protective bearing.

[0033] In a second aspect, the present invention provides a rotor shaft support device comprising the bearing assembly of the first aspect. BRIEF DESCRIPTION OF THE DRAWINGS

[0034] Various other advantages and benefits will become apparent to those skilled in the art upon reading the detailed description of the preferred embodiment below. The accompanying drawings are for illustration purposes only and are not to be considered as limiting the present invention. The same reference numerals are used throughout the accompanying drawings to denote the same components. In the accompanying drawings:

[0035] Figure 1 、 Figure 3-Figure 6 sectional views of different embodiments of the compressor of the present invention passing through the axis of the rotor;

[0036] Figure 2 for Figure 1 A local enlarged view at location I;

[0037] Figure 7 A cross-sectional view of a support member of some embodiments of the compressor of the present invention passing through the axis of the rotor;

[0038] Figure 8 and Figure 9 for Figure 7 AA cross-sectional views of different embodiments;

[0039] Figure 10 This is an axonometric view of a support member of a compressor according to an embodiment of the present invention.

[0040] The reference numerals are as follows:

[0041] 95. Compressor;

[0042] 951, bearing assembly;

[0043] 9511, support member; 95111, first magnetic pole portion; 95112, protective bearing mounting portion; 951121, bearing mounting hole; 95113, cooling channel; 95114, cooling medium inlet; 95115, cooling medium outlet;

[0044] 95116, sealing portion; 951161, first protrusion; 951162, first sealing tooth; 95117, air duct;

[0045] 9512, magnetic pole plate; 95121, second magnetic pole portion; 95122, protective bearing; 951221, first shaft mounting hole;

[0046] 952, thrust plate; 9521, second shaft mounting hole;

[0047] 953, gas compression assembly; 9531, impeller; 95311, second protrusion; 95312, second sealing tooth; 9532, rotor; 95321, rotor shaft; 953211, first shaft segment; 953212, second shaft segment; 9533, spacer; 9534, shaft sleeve;

[0048] 954, casing assembly; 9541, casing; 9542, volute; 95421, suction chamber; 95422, compressed air duct;

[0049] 955. Axial bearing winding. DETAILED DESCRIPTION

[0050] Exemplary embodiments of the present disclosure will be described in more detail below with reference to the accompanying drawings. Although exemplary embodiments of the present disclosure are shown in the accompanying drawings, it should be understood that the present disclosure can be implemented in various forms and should not be limited by the embodiments described herein. Rather, these embodiments are provided to enable a more thorough understanding of the present disclosure and to fully convey the scope of the present disclosure to those skilled in the art.

[0051] It should be understood that the terms used herein are for the purpose of describing specific example embodiments only and are not intended to be limiting. Unless the context clearly indicates otherwise, the singular forms "one", "an" and "said" as used herein may also be meant to include plural forms. The terms "comprise", "include", "contain" and "have" are inclusive and therefore specify the presence of stated features, steps, operations, elements and / or parts, but do not exclude the presence or addition of one or more other features, steps, operations, elements, parts, and / or combinations thereof. The method steps, processes, and operations described herein are not to be construed as necessarily requiring them to be performed in the specific order described or illustrated, unless the order of execution is clearly indicated. It should also be understood that additional or alternative steps may be used.

[0052] Although the terms first, second, third, etc. can be used in the text to describe multiple elements, components, regions, layers and / or sections, these elements, components, regions, layers and / or sections should not be limited by these terms. These terms can only be used to distinguish an element, component, region, layer or section from another region, layer or section. Unless the context clearly indicates otherwise, terms such as "first", "second" and other numerical terms do not imply order or sequence when used in the text. Therefore, the first element, component, region, layer or section discussed below can be referred to as the second element, component, region, layer or section without departing from the teaching of the example embodiments.

[0053] For ease of description, spatially relative terms may be used herein to describe the relationship of one element or feature relative to another element or feature as shown in the figures, such as "inside," "outside," "inside," "outside," "below," "beneath," "above," and the like. Such spatially relative terms are intended to include different orientations of the device in use or operation in addition to the orientation depicted in the figures. For example, if the device in the figures is flipped, an element described as "below" or "below" another element or feature would then be oriented as "above" or "above" another element or feature. Thus, the example term "below" can include both above and below orientations. The device may be otherwise oriented (rotated 90 degrees or in other orientations) and the spatially relative descriptors used herein are interpreted accordingly.

[0054] like Figure 1 、 Figure 3-Figure 6 As shown, according to an embodiment of the present application, a compressor 95 is proposed, comprising a bearing assembly 951, a thrust plate 952, and a gas compression assembly 953. The bearing assembly 951 comprises a support member 9511, a magnetic pole plate 9512, and a protective bearing 95122. The support member 9511 comprises a first magnetic pole portion 95111, a protective bearing mounting portion 95112, and a sealing portion 95116. The first magnetic pole portion 95111 and the sealing portion 95116 are disposed opposite each other along the axial direction of the protective bearing 95122. The protective bearing 95122 is mounted on the protective bearing mounting portion 95112. The first magnetic pole portion 95111 is opposite to and connected to the magnetic pole plate 9512. At least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116 are integrally formed.

[0055] The sealing portion 95116 has a sealing structure for sealingly cooperating with the impeller 9531 of the compressor 95 .

[0056] The sealing portion 95116 can be a plurality of annular protrusions or groove structures that seal with the impeller 9531.

[0057] The magnetic pole plate 9512 and the support member 9511 are made of magnetic conductive materials, which can be, but are not limited to, magnetic conductive materials such as iron-cobalt alloy, neodymium iron boron or low carbon steel.

[0058] According to the compressor 95 of this embodiment of the present invention, at least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116 are integrally formed. This allows the at least two integrally formed components to share a portion, eliminating the need for screw connections. This reduces the axial dimension of the protective bearing 95122 from the magnetic pole plate 9512 to the sealing portion 95116, making the structure more compact and reducing the axial space occupied by the bearing assembly 951 within the compressor 95. This reduces the overall axial dimension of the compressor 95 and the length of the rotor 9532. Furthermore, the first magnetic pole portion 95111 forms part of the axial magnetic bearing of the second magnetic pole portion 95121. When the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 are integrally formed, the concentricity of the protective bearing 95122 and the axial magnetic bearing can be improved. Furthermore, the integrally formed structure reduces the number of parts, facilitating assembly and disassembly.

[0059] In some embodiments of the present invention, please refer to Figure 4 The first magnetic pole portion 95111 and the protective bearing mounting portion 95112 are integrally formed.

[0060] In this embodiment, the sealing portion 95116 is a separate piece, and the sealing portion 95116 can be connected to the protective bearing mounting portion 95112 by fasteners such as screws, rivets or welding.

[0061] As a result, the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 share a portion. Compared to a structure where the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 are separate, the dimensions of the first magnetic pole portion 95111 and the protective bearing mounting portion 95112 along the axial direction of the protective bearing 95122 can be reduced, while also improving the concentricity of the protective bearing 95122 and the axial magnetic suspension bearing. Furthermore, the one-piece structure reduces the number of parts and improves assembly and disassembly efficiency.

[0062] In some embodiments of the present invention, please refer to Figure 5 , the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed.

[0063] In this embodiment, the first magnetic pole portion 95111 is a separate piece, and the first magnetic pole portion 95111 can be connected to the protective bearing mounting portion 95112 by screws, rivets or welding.

[0064] This allows the protective bearing mounting portion 95112 and the sealing portion 9511 to share a portion. This reduces the axial dimensions of the protective bearing mounting portion 95112 and the sealing portion 9511 along the protective bearing 95122 compared to separate structures. Furthermore, the integrated structure reduces the number of parts and improves assembly and disassembly efficiency.

[0065] In some embodiments of the present invention, please refer to Figure 6 , the first magnetic pole portion 95111 and the sealing portion 95116 are integrally formed.

[0066] The protective bearing mounting portion 95112 can be connected to the first magnetic pole portion 95111 by screw connection or welding.

[0067] In this way, the number of parts can be reduced and the efficiency of assembly and disassembly can be improved.

[0068] In some embodiments of the present invention, please refer to Figure 1 The first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed.

[0069] This allows the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116 to share a portion. This reduces the overall dimensions of the first magnetic pole portion 95111, the protective bearing mounting portion 95112, and the sealing portion 95116 along the axial direction of the protective bearing 95122, compared to a structure where all three are separate. Furthermore, the integrated structure reduces the number of parts and improves assembly and disassembly efficiency.

[0070] In some embodiments of the present invention, please refer to Figure 1 The gas compression assembly 953 includes an impeller 9531, which is arranged on the side of the support member 9511 away from the magnetic pole plate 9512. The back of the impeller 9531 is opposite to the sealing part 95116 and rotates in a sealed manner.

[0071] This can reduce the possibility of gas leaking into the compressor 95 and causing pressure instability, thereby improving the stability of the pressure output of the compressor 95.

[0072] In some embodiments of the present invention, please refer to Figure 1The protective bearing mounting portion 95112 has a bearing mounting hole 951121. The protective bearing 95122 is located within the bearing mounting hole 951121 and engages with the inner circumferential surface of the bearing mounting hole 951121. The protective bearing 95122 has a first shaft mounting hole 951221. The gas compression assembly 953 also includes a rotor 9532. The rotor 9532 includes a rotor shaft 95321. One end of the rotor shaft 95321 passes through the first shaft mounting hole 951221 and is fixedly connected to the impeller 9531.

[0073] The fit between the protective bearing 95122 and the bearing mounting hole 951121 can be a transition fit or an interference fit to ensure the concentricity of the protective bearing 95122 and the bearing mounting hole 951121.

[0074] The protective bearing 95122 can protect the rotor 9532 and the stator when the power is suddenly cut off, thereby preventing the rotor 9532 from colliding with the stator when the power is suddenly cut off during the suspended operation, and supporting the rotor 9532.

[0075] In some embodiments of the present invention, please refer to Figure 1 The magnetic pole plate 9512 has a second magnetic pole portion 95121, which is spaced apart from and opposite to the first magnetic pole portion 95111 along the axial direction of the protective bearing 95122. The gas compression assembly 953 also includes a thrust plate 952, which is fixedly mounted on the rotor shaft 95321. The thrust plate 952 is located between the first magnetic pole portion 95111 and the second magnetic pole portion 95121 and is movable relative to the support member 9511 along the axial direction of the protective bearing 95122. The first magnetic pole portion 95111 and the second magnetic pole portion 95121 are respectively configured to adjust the position of the thrust plate 952 through magnetic force. The thrust plate 952 has a second shaft mounting hole 9521, and the rotor shaft 95321 passes through the second shaft mounting hole 9521 and is fixedly connected to the thrust plate 952.

[0076] The rotor shaft 95321 can be fixedly connected to the thrust plate 952 by interference fit or threaded connection.

[0077] In compressor 95, rotor shaft 95321 is also supported by two sets of radial magnetic bearings. These two sets of radial magnetic bearings, combined with the circumferential permanent magnets of rotor 9532, magnetically pull rotor 9532 upward, levitating it. Compressor 95 also includes a housing assembly 954 and two sets of radial magnetic bearings. Housing assembly 954 defines a housing cavity within which bearing assembly 951, thrust plate 952, and gas compression assembly 953 are located. A stator is also located within the cavity, rotatably engaged with rotor 9532. Rotor 9532 rotates under the influence of the stator's magnetic field, operating in the same manner as an electric motor and will not be further elaborated here.

[0078] Please refer to Figure 1 The casing assembly 954 includes a casing 9541 and a volute 9542. At least one end of the casing 9541 is connected to the volute 9542. The volute 9542 has an intake chamber 95421 and a compressed air duct 95422. The intake chamber 95421 and the compressed air duct 95422 are communicated. An air inlet is provided at one end of the intake chamber 95421 along the axial direction of the rotor shaft 95321. The impeller 9531 is arranged in the intake chamber 95421 and is located on the intake side of the compressed air duct 95422. The exhaust port of the impeller 9531 is communicated with the intake side of the compressed air duct 95422. The gas compressed by the impeller 9531 enters the channel of the volute 9542 and is discharged through the volute 9542. To reduce gas leakage into the housing cavity of casing 9541, a seal 95116 is required to engage with the wheel back of impeller 9531 in a rotating seal to reduce gas leakage and maintain the stability of the pressure output of compressor 95. Casing assembly 954 has a housing cavity, and the bearing assembly and thrust plate are both located within the housing cavity.

[0079] To reduce resistance to rotor 9532's rotation and minimize wear on the bearings supporting it, two sets of radial magnetic bearings are mounted on rotor 9532, spaced apart along the axial direction of rotor 9532. The magnetic fields generated by the radial magnetic bearings interact with the permanent magnets in rotor 9532, levitating rotor 9532. Rotor 9532 then rotates via the stator, achieving its suspended rotation. Rotor 9532 may experience axial movement during rotation, which can cause wear and tear on rotor 9532.

[0080] The support member 9511 can be connected to the housing assembly 954, specifically to any one of the housing 9541 and the volute 9542. Optionally, the connection method between the support member 9511 and the housing assembly 954 includes but is not limited to screw connection, welding or riveting.

[0081] Therefore, the position of the thrust disk 952 needs to be adjusted via the first magnetic pole portion 95111 and the second magnetic pole portion 95121 to change the axial position of the rotor 9532 so that the rotor 9532 does not interfere with the rotor 9532 in the suspended state. The bearing assembly 951 also includes an axial bearing winding 955, which is located between the first magnetic pole portion 95111 and the second magnetic pole portion 95121 and is disposed on the outer circumference of the thrust disk 952. The axial bearing winding 955 generates magnetic force, which is then guided by the magnetic pole plate 9512 and the support member 9511. The first magnetic pole portion 95111 and the second magnetic pole portion 95121 generate magnetic force, causing the thrust disk 952 to generate a force along the axial direction of the rotor 9532, thereby changing the position of the thrust disk 952 to adjust the axial position of the rotor 9532. The first magnetic pole portion 95111, the second magnetic pole portion 95121 and the axial bearing winding 955 form an axial magnetic levitation bearing (thrust magnetic levitation bearing), which has the same working principle as the axial magnetic levitation in the prior art and will not be repeated here.

[0082] In some embodiments of the present invention, please refer to Figure 2 The sealing portion 95116 includes multiple circles of first protrusions 951161, which are coaxially arranged with the protective bearing 95122 and spaced apart radially along the rotor shaft 95321. The back of the impeller 9531 is provided with multiple circles of second protrusions 95311, which are coaxially arranged with the rotor shaft 95321 and spaced apart radially along the rotor shaft 95321. At least one circle of second protrusions 95311 is provided between two adjacent circles of first protrusions 951161.

[0083] The profile of the cross section of the first protrusion 951161 and the second protrusion 95311 passing through the axis of the protective bearing 95122 can be, but is not limited to, a rectangle, an arc, a triangle, an ellipse, etc., and can also be other irregular shapes.

[0084] In one example, multiple circles of first protrusions 951161 are flush with one end facing away from the magnetic pole plate 9512, and multiple circles of second protrusions 95311 are flush with one end facing the magnetic pole plate 9512, which can reduce the size of the sealing portion 95116 along the axial direction of the rotor shaft 95321. In another example, along the radial direction of the rotor shaft 95321 from the inside to the outside, the size of the multiple circles of first protrusions 951161 from the end facing away from the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually decreases, and the size of the multiple second protrusions 95311 from the end facing the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually increases; or, along the radial direction of the rotor shaft 95321 from the inside to the outside, the size of the multiple circles of first protrusions 951161 from the end facing away from the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually increases, and the size of the multiple second protrusions 95311 from the end facing the magnetic pole plate 9512 to the end of the magnetic pole plate 9512 along the axial direction of the rotor shaft 95321 gradually decreases, which can also form a labyrinth seal to reduce gas leakage.

[0085] The first protrusion 951161 and the second protrusion 95311 cooperate to form a labyrinth seal, extending the path for gas to pass through. When the gas passes through the mating surface between the first protrusion 951161 and the second protrusion 95311, the pressure loss will hinder the passage of the gas, thereby reducing gas leakage.

[0086] In some embodiments of the present invention, please refer to Figure 2 , the multiple circles of first protrusions 951161 are arranged flush with one end away from the magnetic pole plate 9512; and / or, the multiple circles of second protrusions 95311 are arranged flush with one end toward the magnetic pole plate 9512.

[0087] Thus, the size of the sealing portion 95116 along the axial direction of the rotor shaft 95321 can be reduced, making the structure compact, which is conducive to reducing the length of the rotor shaft 95321.

[0088] In some embodiments of the present invention, please refer to Figure 2 The sealing portion 95116 also includes multiple circles of first sealing teeth 951162, which are coaxially arranged with the protective bearing 95122. Along the radial direction of the rotor shaft 95321, the multiple circles of first sealing teeth 951162 are arranged at intervals, and at least one circle of first sealing teeth 951162 is formed at the end of the first protrusion 951161 away from the magnetic pole plate 9512.

[0089] Optionally, in a half-section of the first sealing tooth 951162 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section decreases from the root to the end away from the root, from the root to the connection end of the first sealing tooth 951162. For example, the outer contour of the half-section can be trapezoidal or hemispherical, or can be a structure constructed of any of a spline curve, a straight line, or an arc.

[0090] In other examples, the first sealing teeth 951162 may also be rectangular.

[0091] Therefore, when the gas passes through the first sealing teeth 951162, the gas is disturbed, causing a pressure drop in the gas, thereby significantly reducing the leakage.

[0092] In some embodiments of the present invention, please refer to Figure 2 The first sealing teeth 951162 formed on the first protrusion 951161 are multiple circles, and the first sealing teeth 951162 are inclined outward along the radial direction of the rotor shaft 95321.

[0093] Among the multiple first sealing teeth 951162 forming the same circle of first protrusions 951161, a circle of grooves is formed between two adjacent circles of first sealing teeth 951162. The width of the grooves in the radial direction of the first sealing teeth 951162 gradually increases from the bottom of the grooves to the notch of the grooves. In a half-section of the first sealing teeth 951162 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section of the first sealing teeth 951162 decreases from the root to the end away from the root.

[0094] The first sealing tooth 951162 is tilted outward in the radial direction of the rotor shaft 95321, which means that the end of the first sealing tooth 951162 away from its root is offset relative to its root in the radial direction of the rotor shaft 95321, that is, the first sealing tooth 951162 can be an inclined tooth structure.

[0095] By tilting the first sealing teeth 951162 in multiple turns, a tortuous airflow channel is formed, which prevents the high-pressure side gas from leaking to the low-pressure side. Specifically, when the high-pressure gas passes through the sealing portion 95116, it must pass through the gap between the first protrusion 951161 and the second protrusion 95311 in sequence. Because the first sealing teeth 951162 are radially spaced and tilted outward, the direction of gas flow is forced to change. Every time the gas passes through the gap between the first sealing teeth 951162, the pressure drop occurs due to the throttling effect. After passing through multiple turns of the first sealing teeth 951162, the leakage amount is greatly attenuated. In addition, when the impeller 9531 rotates, an air film is formed in the tiny gap between the back of the impeller 9531 and the sealing first sealing teeth 951162. The first sealing teeth 951162 can reduce the disturbance of the rotating airflow on the sealing gap, avoiding fluctuations in the leakage amount caused by unstable airflow in the gap.

[0096] In some embodiments of the present invention, please refer to Figure 2 The back of the impeller 9531 is provided with multiple circles of second sealing teeth 95312, which are coaxially arranged with the rotor shaft 95321. Along the radial direction of the rotor shaft 95321, the multiple circles of second sealing teeth 95312 are arranged at intervals, and at least one circle of second sealing teeth 95312 is formed on one end of the second protrusion 95311 facing the magnetic pole plate 9512.

[0097] Optionally, in a half-section of the second sealing tooth 95312 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section decreases from the root to the end away from the root, from the root to the connection end of the first sealing tooth 951162. For example, the outer contour of the half-section can be trapezoidal or hemispherical, or can be a structure constructed of any of a spline curve, a straight line, or an arc.

[0098] In other examples, the second sealing teeth 95312 may also be rectangular.

[0099] By staggered arrangement of multiple circles of first protrusions 951161 and second protrusions 95311, and provision of multiple circles of first sealing teeth 951162 and multiple circles of second sealing teeth 95312, a complex return path is formed inside the sealing area, so that the gas must undergo multiple changes in direction and throttling resistance before it can leak out, thereby significantly increasing the sealing impedance and reducing the leakage rate.

[0100] In some embodiments of the present invention, please refer to Figure 2 The second sealing teeth 95312 formed on the second protrusion 95311 are multiple circles, and the second sealing teeth 95312 are inclined outward along the radial direction of the rotor shaft 95321.

[0101] Among the multiple second sealing teeth 95312 forming the same circle of first protrusions 951161, a circle of grooves is formed between two adjacent circles of second sealing teeth 95312. The width of the grooves gradually increases in the radial direction of the second sealing teeth 95312 from the bottom of the grooves to the notch of the grooves. In a half-section of the second sealing teeth 95312 passing through the axis of the rotor shaft 95321, the radial dimension of the half-section of the second sealing teeth 95312 decreases from the root to the end away from the root.

[0102] The second sealing teeth 95312 are tilted outwardly in the radial direction of the rotor shaft 95321, which means that the end of the second sealing teeth 95312 away from the root thereof is offset relative to the root thereof in the radial direction of the rotor shaft 95321, that is, the second sealing teeth 95312 may have an inclined tooth structure.

[0103] The labyrinth gas flow passage is formed by the multiple turns of the inclined second sealing teeth 95312, which hinders the high pressure gas from leaking to the low pressure side. Specifically, when the high pressure gas passes through the sealing portion 95116, it needs to pass through the gap between the first protrusion 951161 and the second protrusion 95311 in sequence. Since the second sealing teeth 95312 are radially spaced and inclined outward, the gas flow direction is forced to change, and the pressure of the gas is reduced due to the throttling effect every time it passes through the gap between the second sealing teeth 95312. After passing through multiple turns of the second sealing teeth 95312, the leakage is greatly attenuated. Moreover, when the impeller 9531 rotates, the small gap between the back of the impeller 9531 and the sealing second sealing teeth 95312 forms a gas film, and the second sealing teeth 95312 can reduce the disturbance of the rotating gas flow to the sealing gap, avoiding fluctuations in the leakage caused by unstable gas flow in the gap.

[0104] In some embodiments of the present application, please refer to Figure 3 The support member 9511 has a cooling passage 95113, which is provided with a cooling medium inlet 95114 and a cooling medium outlet 95115.

[0105] In an example, please refer to Figure 8 The cooling passage 95113 can include a circumferential passage that surrounds the rotor shaft 95321, and the circumferential passage is a passage that surrounds the rotor shaft 95321 once. Specifically, the cooling medium inlet 95114 and the cooling medium outlet 95115 are located on opposite sides of the cooling passage 95113 in the radial direction of the rotor shaft 95321, i.e., the cooling medium inlet 95114 and the cooling medium outlet 95115 face opposite directions, and they are arranged at substantially 180° apart in the circumferential direction of the rotor shaft 95321.

[0106] In another example, please refer to Figure 9 The cooling passage 95113 includes an arc-shaped passage that extends in the circumferential direction of the rotor shaft 95321, the cooling medium inlet 95114 communicates with one end of the arc-shaped passage, and the cooling medium outlet 95115 communicates with both ends of the arc-shaped passage. A blocking portion is formed between the two ends of the arc-shaped passage to block the two ends of the arc-shaped passage to form a discontinuous passage in the circumferential direction of the rotor shaft 95321.

[0107] In yet another example, the cooling passage 95113 can be a spiral flow passage that extends in the circumferential direction of the rotor shaft 95321.

[0108] The cooling passage 95113 can be filled with a liquid medium or a gas. The liquid medium can be, but is not limited to, water or oil.

[0109] At least two of the first magnetic pole portion 95111, the protective bearing mounting portion 95112 and the sealing portion 95116 are integrally formed, which can reduce the size between the magnetic pole plate 9512 and the sealing portion 95116 along the axial direction of the rotor shaft 95321, and reduce the transmission path of the cooling channel 95113, which is beneficial to improving the heat exchange efficiency between the cooling channel 95113 and the first magnetic pole portion 95111 and the second magnetic pole portion 95121, thereby better improving the temperature of the axial magnetic levitation bearing (thrust magnetic levitation bearing) when the compressor 95 is working.

[0110] In some embodiments of the present invention, please refer to Figure 10 The support member 9511 has an air duct 95117 extending along the radial direction of the protective bearing 95122. The air duct 95117 penetrates the inner circumferential surface of the support member 9511 and the outer circumferential surface of the support member 9511 along the radial direction of the protective bearing 95122. Along the axial direction of the protective bearing 95122, the air duct 95117 is spaced apart from or adjacent to the protective bearing 95122.

[0111] Optionally, the dimension of the air duct 95117 along the circumferential direction of the protective bearing 95122 is W, and the dimension W decreases from the outside to the inside in the radial direction of the support member 9511. In other embodiments, the dimension W along the radial direction of the support member 9511 from the outside to the inside can also be a constant value.

[0112] Housing assembly 954 is provided with an air inlet and an exhaust port, each connected to air duct 95117. These ports can be connected to circulating cooling systems to cool components such as protective bearing 95122, the axial magnetic bearing, and the rotor. A fan and heat exchanger can be connected to the cooling circuit. The exhaust gas is cooled by the heat exchanger and then passed through the fan to the air inlet via the cooling circuit, completing the cooling cycle.

[0113] By setting up the air duct 95117, the protective bearing 95122, the axial magnetic bearing, the rotor 9532 and other components can be cooled to prevent the compressor 95 from working unstably due to high temperature during operation.

[0114] In some embodiments of the present invention, there are multiple air ducts 95117 , and the multiple air ducts 95117 are arranged at intervals along the circumferential direction of the protective bearing 95122 .

[0115] Thereby, the cooling area can be increased to further improve the cooling effect.

[0116] In some embodiments of the present invention, please refer to Figure 7-Figure 9 , the cooling channel 95113 is arranged around the protective bearing 95122.

[0117] Optionally, the cooling channel 95113 can be a flat channel, i.e., the size of the cooling channel 95113 along the axial direction of the rotor shaft 95321 is smaller than the size of the cooling channel 95113 along the radial direction of the rotor shaft 95321, so as to increase the cooling area and improve the cooling effect.

[0118] In this way, the length of the cooling channel 95113 can be increased to improve the heat exchange effect of the cooling channel 95113 and the axial magnetic suspension bearing (thrust magnetic suspension bearing).

[0119] In some embodiments of the present application, the impeller 9531 is in interference fit with the rotor shaft 95321 to have high coaxiality between the impeller 9531 and the rotor shaft 95321. One end of the impeller 9531 is provided with a through hole, and the impeller 9531 is threadedly connected with the end portion of the rotor shaft 95321 by means of a screw, a part of the screw being located in the through hole.

[0120] In some embodiments of the present application, please refer to Figure 1 and Figure 2 The rotor shaft 95321 comprises a first shaft segment 953211 and a second shaft segment 953212, a first shaft shoulder is formed between the first shaft segment 953211 and the second shaft segment 953212, and the diameter of the first shaft segment 953211 is larger than that of the second shaft segment 953212. The protection bearing 95122 is in clearance fit with the first shaft segment 953211. The impeller 9531 is in interference fit with the second shaft segment 953212. The impeller 9531 can abut against the first shaft shoulder, or a spacer sleeve 9533 can be arranged between the impeller 9531 and the first shaft shoulder, the impeller 9531 abuts against the spacer sleeve 9533, the spacer sleeve 9533 abuts against the first shaft shoulder, and the spacer sleeve 9533 is in clearance fit with the rotor shaft 95321. Through the spacer sleeve 9533, the clearance between the inner ring of the protection bearing 95122 and the spacer sleeve 9533 along the axial direction of the protection bearing 95122 can be conveniently adjusted.

[0121] In some embodiments of the present application, please refer to Figure 1 and Figure 2Compressor 95 also includes a sleeve 9534, which is located between thrust plate 952 and impeller 9531. The outer circumference of sleeve 9534 has a clearance fit with the inner ring of protective bearing 95122, while the inner circumference of sleeve 9534 has an interference fit or transition fit with rotor shaft 95321. One end of sleeve 9534 abuts thrust plate 952, while the other end abuts impeller 9531. Spacer 9533 abuts sleeve 9534. Along the axial direction of rotor shaft 95321, the dimension between sleeve 9534 and thrust plate 952 is greater than the dimension of protective bearing 95122, allowing axial movement between thrust plate 952 and rotor shaft 95321. In other embodiments, the sleeve 9534 may not be provided, and the inner ring of the protective bearing 95122 is clearance-fitted with the first shaft segment 953211. The interference force between the thrust plate 952 and the first shaft segment 953211 is utilized to enable the thrust plate 952 and the rotor shaft 95321 to move axially together through the axial magnetic bearing.

[0122] In some embodiments of the present invention, the thrust disk 952 has a first abutment portion, which abuts against one end of the sleeve 9534. Along the radial direction of the rotor shaft 95321, the first abutment portion is spaced apart from the outer ring of the protective bearing 95122. Along the axial direction of the rotor shaft 95321, the end of the protective bearing 95122 facing the thrust disk 952 is spaced apart from the first abutment portion.

[0123] According to an embodiment of the present invention, a rotor shaft support device is provided, including the bearing assembly 951 in each of the above embodiments.

[0124] Since the rotor shaft support device includes all the technical features of the above-mentioned bearing assembly 951, the effects are the same as those described above and will not be repeated here.

[0125] The above description is merely a preferred embodiment of the present invention, but the scope of protection of the present invention is not limited thereto. Any changes or substitutions that can be easily conceived by a person skilled in the art within the technical scope disclosed in the present invention should be included in the scope of protection of the present invention. Therefore, the scope of protection of the present invention should be based on the scope of protection of the claims.

Claims

1. A compressor, characterized in that: include: A bearing assembly, the bearing assembly includes a support member, a magnetic pole plate and a protective bearing, the support member includes a first magnetic pole portion, a protective bearing mounting portion and a sealing portion, the first magnetic pole portion and the sealing portion are arranged opposite to each other along the axial direction of the protective bearing, the protective bearing is mounted on the protective bearing mounting portion, the first magnetic pole portion is opposite to and connected to the magnetic pole plate, and at least two of the first magnetic pole portion, the protective bearing mounting portion and the sealing portion are integrally formed.

2. The compressor according to claim 1, characterized in that The first magnetic pole portion and the protective bearing mounting portion are integrally formed; or the protective bearing mounting portion and the sealing portion are integrally formed; or the first magnetic pole portion and the sealing portion are integrally formed; or the first magnetic pole portion, the protective bearing mounting portion and the sealing portion are integrally formed.

3. The compressor according to claim 1, characterized in that The compressor further comprises: The gas compression component comprises an impeller, wherein the impeller is arranged on a side of the support component away from the magnetic pole plate, and the wheel back of the impeller is opposite to the sealing part and rotates and seals with it.

4. The compressor according to claim 3, characterized in that The protective bearing mounting portion has a bearing mounting hole, and the protective bearing is located in the bearing mounting hole and matches the inner circumferential surface of the bearing mounting hole; The protective bearing has a first shaft mounting hole; The gas compression assembly further includes a rotor, which includes a rotor shaft. One end of the rotor shaft passes through the first shaft mounting hole and is fixedly connected to the impeller.

5. The compressor according to claim 4, characterized in that The magnetic pole plate has a second magnetic pole portion, and the second magnetic pole portion is opposite to and spaced from the first magnetic pole portion along the axial direction of the protective bearing; The gas compression assembly further includes a thrust plate, the thrust plate being fixedly sleeved on the rotor shaft, the thrust plate being located between the first magnetic pole portion and the second magnetic pole portion and being movable relative to the support member along the axial direction of the protective bearing, the first magnetic pole portion and the second magnetic pole portion being respectively configured to adjust the position of the thrust plate by magnetic force, and the thrust plate having a second shaft mounting hole; The rotor shaft is passed through the second shaft mounting hole and is fixedly connected to the thrust plate.

6. The compressor according to claim 4, characterized in that The sealing portion includes: A plurality of circles of first protrusions are arranged coaxially with the protective bearing, and the plurality of circles of first protrusions are arranged at intervals along the radial direction of the rotor shaft; The back of the impeller is provided with multiple circles of second protrusions, which are arranged coaxially with the rotor shaft. Along the radial direction of the rotor shaft, the multiple circles of second protrusions are arranged at intervals, and at least one circle of the second protrusions is provided between two adjacent circles of the first protrusions.

7. The compressor according to claim 6, characterized in that The multiple circles of first protrusions are arranged flush with one end facing away from the magnetic pole plate; and / or the multiple circles of second protrusions are arranged flush with one end facing the magnetic pole plate.

8. The compressor according to claim 6, characterized in that The sealing portion further comprises: Multiple circles of first sealing teeth are coaxially arranged with the protective bearing and spaced apart along the radial direction of the rotor shaft. At least one circle of the first sealing teeth is formed on the end of the first protrusion away from the magnetic pole plate.

9. The compressor according to claim 8, characterized in that The first sealing teeth formed on the first protrusion are multiple circles, and the first sealing teeth are inclined outward along the radial direction of the rotor shaft; And / or, the multiple circles of first sealing teeth are arranged flush with one end facing away from the magnetic pole plate.

10. The compressor according to claim 8, characterized in that The back of the impeller is provided with multiple circles of second sealing teeth, which are arranged coaxially with the rotor shaft. Along the radial direction of the rotor shaft, the multiple circles of second sealing teeth are arranged at intervals, and at least one circle of the second sealing teeth is formed on one end of the second protrusion facing the magnetic pole plate.

11. The compressor according to claim 10, characterized in that The second sealing teeth formed on the second protrusion are multiple circles, and the second sealing teeth are inclined outward along the radial direction of the rotor shaft; And / or, the multiple circles of second sealing teeth are arranged flush with one end of the magnetic pole plate.

12. The compressor according to any one of claims 1 to 11, characterized in that: The support member has an air duct extending along the radial direction of the protective bearing, the air duct passes through the inner circumferential surface of the support member and the outer circumferential surface of the support member along the radial direction of the protective bearing, and along the axial direction of the protective bearing, the air duct is spaced apart from or adjacent to the protective bearing.

13. The compressor according to claim 12, characterized in that There are multiple air ducts, and the multiple air ducts are arranged at intervals along the circumferential direction of the protective bearing.

14. The compressor according to any one of claims 1 to 11, characterized in that: The support member has a cooling channel provided with a cooling medium inlet and a cooling medium outlet.

15. The compressor according to claim 14, characterized in that The cooling channel is arranged around the protective bearing.

16. A rotor shaft support device, characterized in that: Comprising the bearing assembly according to any one of claims 1-15.

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