CN220365739U - Centrifugal compressor - Google Patents

Abstract

The utility model relates to a centrifugal compressor, which comprises a shell, a rotor, an inner magnetic ring and an outer magnetic ring, wherein the rotor is arranged in the shell, the inner magnetic ring is arranged on the rotor, the outer magnetic ring is arranged on the shell, the outer magnetic ring is sleeved on the inner magnetic ring and has a gap with the inner magnetic ring in the radial direction of the rotor, and the magnetic poles on the inner peripheral surface of the outer magnetic ring and the outer peripheral surface of the inner magnetic ring are opposite. When the rotor bears external axial force, the centrifugal compressor balances the axial force borne by the rotor through the magnetic attraction between the inner magnetic ring and the outer magnetic ring, counteracts at least part of the axial force acted on the rotor, avoids dry grinding of the air-float thrust bearing on the rotor, reduces the heating condition of the air-float thrust bearing, and ensures the stability of the rotor under different working conditions of the centrifugal compressor.

Description

Centrifugal compressor

Technical Field

The utility model relates to the technical field of compressors, in particular to a centrifugal compressor.

Background

Dynamic pressure air bearing has wide application in air cycle machine, miniature gas turbine, industrial blower and compressor. The radial air bearing is used as a support in the occasion with the requirement of a clean air source, but unbalanced axial force is often still present in the air compressor, and the matched bearing is an air thrust bearing and is used for bearing the axial force. However, in the actual assembly, the situations of inconsistent theoretical calculation, overload, incapability of absolute and concentric shaft of stator assembly and the like exist, because the air bearing can form an effective air mould at a certain rotating speed, before the air mould is formed, the air bearing belongs to a dry grinding condition, so that the air bearing and a bearing bush are subjected to dry grinding during starting or overload, the damage to the air bearing is irreversible, the service life of the air bearing is reduced, and even the bearing is directly damaged in severe cases.

Disclosure of Invention

The present utility model aims to solve at least one of the technical problems in the related art to some extent. Therefore, the embodiment of the utility model provides a centrifugal compressor, which avoids dry grinding of an air-float thrust bearing on a rotor, reduces the heating condition of the air-float thrust bearing, and ensures the stability of the rotor under different working conditions of the centrifugal compressor.

The centrifugal compressor of the embodiment of the utility model comprises:

a housing;

the rotor is arranged in the shell;

an inner magnetic ring arranged on the rotor; and

the outer magnetic ring is arranged on the shell, the outer magnetic ring is sleeved on the inner magnetic ring and is provided with a gap with the inner magnetic ring in the radial direction of the rotor, and the magnetic poles on the inner peripheral surface of the outer magnetic ring are opposite to the magnetic poles on the outer peripheral surface of the inner magnetic ring.

When the rotor bears external axial force, the centrifugal compressor provided by the embodiment of the utility model balances the axial force borne by the rotor through the magnetic attraction between the inner magnetic ring and the outer magnetic ring, counteracts at least part of the axial force acted on the rotor, avoids dry grinding of the air-float thrust bearing on the rotor, reduces the heating condition of the air-float thrust bearing, and ensures the stability of the rotor under different working conditions of the centrifugal compressor.

In some embodiments, each of the inner magnetic ring and the outer magnetic ring is axially magnetized.

In some embodiments, the inner magnetic ring has a first radial cross section centered in its axial direction, the poles of the inner magnetic ring on either side of the first radial cross section in its axial direction being opposite; the outer magnetic ring has a second radial cross section at the center in the axial direction thereof, and the magnetic poles of the outer magnetic ring on both sides of the second radial cross section in the axial direction thereof are opposite.

In some embodiments, the first radial cross section and the second radial cross section are spaced apart in an axial direction of the rotor.

In some embodiments, the inner magnetic ring has a different dimension in its axial direction than the outer magnetic ring.

In some embodiments, the casing includes a housing, a first cover and a second cover, the first cover is located at one side of the housing, one end of the rotor in the axial direction is rotationally connected with the first cover, the second cover is located at the other side of the housing, the other end of the rotor in the axial direction is rotationally connected with the second cover, the first cover and/or the second cover is provided with the outer magnetic ring, and the outer magnetic ring has a second radial cross section in the center in the axial direction;

the rotor includes a magnetic steel having a third radial cross section at a center in an axial direction thereof, the magnetic steel being spaced apart from the inner magnetic ring in an axial direction thereof, the inner magnetic ring having a first radial cross section at a center in an axial direction thereof;

the centrifugal compressor further comprises a stator which is arranged in the shell, the stator is sleeved on the rotor and has a gap with the rotor in the radial direction, the stator has a fourth radial cross section at the center of the stator in the axial direction, the third radial cross section is spaced from the fourth radial cross section, the offset direction of the third radial cross section and the fourth radial cross section is the same as the offset direction of the first radial cross section and the second radial cross section, or the first radial cross section and the second radial cross section are on the same plane.

In some embodiments, the centrifugal compressor further comprises:

the first turbine is provided with a first volute and a first impeller, the first volute is arranged on the first cover, and the first impeller is arranged on the rotor; and

and the first gasket is arranged between the first volute and the first cover and/or between the first cover and the shell.

In some embodiments, the centrifugal compressor further comprises:

the second turbine is provided with a second volute and a second impeller, the second volute is arranged on the second cover, and the second impeller is arranged on the rotor; and

and the second gasket is arranged between the second cover and the shell and/or between the second cover and the second volute.

In some embodiments, the first cover is integrally formed with the housing, and the first gasket is disposed between the first volute and the first cover.

In some embodiments, the centrifugal compressor further comprises an air bearing disposed on the rotor.

Drawings

Fig. 1 is a schematic view of a structure of a first-stage centrifugal compressor according to an embodiment of the present utility model.

FIG. 2 is one of the schematic diagrams of an inner magnetic ring and an outer magnetic ring;

FIG. 3 is a second schematic illustration of an inner magnetic ring and an outer magnetic ring;

fig. 4 is a schematic structural view of a two-stage centrifugal compressor according to an embodiment of the present utility model.

Reference numerals:

a centrifugal compressor 100;

a casing 1, a casing 11, a first casing 12, a second casing 13;

rotor 2, magnetic steel 21, third radial cross section 211;

an inner magnetic ring 3, a first radial cross section 31, an outer magnetic ring 4, a second radial cross section 41, a stator 5, a fourth radial cross section 51, a first gasket 71, a second gasket 72, a first turbine 8, a first volute 81, a first impeller 82, a second turbine 9, a second volute 91, a second impeller 92, and an air bearing 10.

Detailed Description

Reference will now be made in detail to embodiments of the present utility model, examples of which are illustrated in the accompanying drawings. The embodiments described below by referring to the drawings are illustrative and intended to explain the present utility model and should not be construed as limiting the utility model.

As shown in fig. 1 to 4, a centrifugal compressor 100 of an embodiment of the present utility model includes a casing 1, a rotor 2, an inner magnet ring 3, and an outer magnet ring 4. The rotor 2 is arranged in the casing 1, the inner magnetic ring 3 is arranged on the rotor 2, the outer magnetic ring 4 is arranged on the casing 1, the outer magnetic ring 4 is sleeved on the inner magnetic ring 3 and has a gap with the inner magnetic ring 3 in the radial direction of the rotor 2, and the magnetic poles on the inner peripheral surface of the outer magnetic ring 4 and the outer peripheral surface of the inner magnetic ring 3 are opposite.

The magnetic poles of the inner peripheral surface of the inner magnetic ring 3 and the outer peripheral surface of the outer magnetic ring 4 are opposite, and the magnetic pole distribution of the inner magnetic ring 3 and the outer magnetic ring 4 comprises the following conditions: (1) each of the inner magnet ring 3 and the outer magnet ring 4 is radially magnetized, for example, referring to fig. 2, the outer circumferential surface of the inner magnet ring 3 is N-stage, the inner circumferential surface of the outer magnet ring 4 is S-stage, and accordingly, the inner circumferential surface of the inner magnet ring 3 is S-stage, and the outer circumferential surface of the outer magnet ring 4 is N-stage. (2) Each of the inner magnet ring 3 and the outer magnet ring 4 is axially magnetized, for example, referring to fig. 3, one end (left end) of the inner magnet ring 3 in the axial direction of the rotor 2 is N-stage, the other end (right end) of the inner magnet ring 3 in the axial direction of the rotor 2 is S-pole, one end (left end) of the outer magnet ring 4 in the axial direction of the rotor 2 is S-pole, and the other end (left end) of the outer magnet ring 4 in the axial direction of the rotor 2 is N-pole.

The inner peripheral surface of the outer magnetic ring 4 of the centrifugal compressor 100 of the embodiment of the utility model and the magnetic poles on the outer peripheral surface of the inner magnetic ring 3 are opposite, so that the force towards the outer magnetic ring 4 is formed on the inner magnetic ring 3, the force towards the inner magnetic ring 3 is formed on the outer magnetic ring 4, and the inner magnetic ring 3 and the outer magnetic ring 4 are attracted mutually. When the rotor 2 is subjected to external axial force and deflects in the axial direction, the inner magnetic ring 3 is driven to deflect, so that the relative position of the inner magnetic ring 3 and the outer magnetic ring 4 is changed, the force on the inner magnetic ring 3, which is formed on the axial direction of the rotor 2 and faces the outer magnetic ring 4, balances the magnetic attraction force with the axial force on the rotor 2, which is applied to the rotor 2 and deflects the inner magnetic ring 3, and drives the rotor 2 to reset, so that the air-float thrust bearing on the rotor 2 is prevented from dry grinding.

When the rotor 2 bears external axial force, the centrifugal compressor 100 of the embodiment of the utility model balances the magnetic attraction force between the inner magnetic ring 3 and the outer magnetic ring 4 and the axial force borne by the rotor 2, counteracts at least part of the axial force acting on the rotor 2, avoids dry grinding of an air-bearing thrust bearing on the rotor 2, reduces the heating condition of the air-bearing thrust bearing, and ensures the stability of the rotor 2 under different working conditions of the centrifugal compressor 100.

In order to make the solution of the present application easier to understand, the description will be given taking the case where the axial direction of the rotor 2 is the same as the left-right direction as shown in fig. 1 to 4.

The centrifugal compressor 100 of the embodiment of the utility model comprises a casing 1, a rotor 2, an inner magnetic ring 3, an outer magnetic ring 4, a stator 5, a first turbine 8, a first gasket 71 and an air bearing 10.

The casing 1 includes a housing 11, a first cover 12 and a second cover 13, the first cover 12 is located at one side (left side) of the housing 11, one end (left end) of the rotor 2 in the axial direction thereof is rotatably connected with the first cover 12, the second cover 13 is located at the other side (right side) of the housing 11, and the other end (right end) of the rotor 2 in the axial direction thereof is rotatably connected with the second cover 13.

The rotor 2 includes a magnetic steel 21, the magnetic steel 21 having a third radial cross section 211 at the center in the axial direction thereof, the center of the magnetic steel 21 in the axial direction thereof being located on the third radial cross section 211 of the magnetic steel 21.

An air bearing 10 is provided on the rotor 2 to counteract at least a portion of the axial force exerted on the rotor 2, and to balance the axial force of the rotor 2.

An inner magnetic ring 3 is provided on the rotor 2, and a magnetic steel 21 is spaced apart from the inner magnetic ring 3 in the axial direction thereof. The outer magnetic ring 4 is arranged on the shell 1, the outer magnetic ring 4 is sleeved on the inner magnetic ring 3 and has a gap with the inner magnetic ring 3 in the radial direction of the rotor 2, the magnetic poles on the inner peripheral surface of the outer magnetic ring 4 and the outer peripheral surface of the inner magnetic ring 3 are opposite, and the inner magnetic ring 3 and the outer magnetic ring 4 are attracted mutually.

Further, the first cover 12 is provided with an outer magnetic ring 4, and the inner magnetic ring 3 is located at the end of the rotor 2. Alternatively, the second cover 13 is provided with an outer magnetic ring 4, and an inner magnetic ring is located at the other end of the rotor 2, as shown in fig. 1. Or, each of the first cover 12 and the second cover 13 is provided with an outer magnetic ring 4, and correspondingly, each of the one end and the other end of the rotor 2 is provided with an inner magnetic ring 3, so that the size of the axial force borne by the rotor 2 which can be counteracted is further improved, and the stability of the rotor 2 is further improved.

The inner magnetic ring 3 and the outer magnetic ring 4 are simple to process, the distribution of the inner magnetic ring 3 on the rotor 2 and the distribution position of the outer magnetic ring 4 on the shell 1 are high in selectivity, good in flexibility and good in adaptability.

In some embodiments, each of the inner magnet ring 3 and the outer magnet ring 4 is axially magnetized. The magnetic pole distribution of each of the inner magnetic ring 3 and the outer magnetic ring 4 is distributed along the axial direction, the axial magnetic attraction force which can be generated is large, and the effect of balancing the axial force which is applied to the rotor 2 is good. Compared with the radially magnetized magnetic ring manufactured by adopting the mode of magnetic powder and plastic injection molding, the axially magnetized inner magnetic ring 3 and the axially magnetized outer magnetic ring 4 can be made of more molding materials, have wide selection range and are easy to manufacture, and when the residual magnetism of the materials of the inner magnetic ring 3 and the outer magnetic ring 4 is large, for example, platinum-iron permanent magnet alloy, the generated axial magnetic attraction force is large.

The magnetic attraction force between the axially magnetized inner magnetic ring 3 and the outer magnetic ring 4 is large, and in some embodiments, the inner magnetic ring 3 has a first radial cross section 31 at the center in the axial direction thereof, the center of the inner magnetic ring 3 in the axial direction thereof is located on the first radial cross section 31 of the inner magnetic ring 3, the magnetic poles of the inner magnetic ring 3 on both sides of the first radial cross section 31 in the axial direction thereof are opposite, that is, there is a pair of magnetic poles on the inner magnetic ring 3, and the boundary line of the two magnetic poles on the inner magnetic ring 3 is located on the first radial cross section 31 of the inner magnetic ring 3. The outer magnet ring 4 has a second radial cross section 41 at its center in the axial direction, the center of the outer magnet ring 4 in its axial direction being located on the second radial cross section 41 of the outer magnet ring 4, the poles of the outer magnet ring 4 on both sides of the second radial cross section 41 in its axial direction being opposite, that is, the outer magnet ring 4 has a pair of poles, and the parting line of the two poles on the outer magnet ring 4 is located on this second radial cross section 41 of the outer magnet ring 4. The inner magnetic ring 3 and the outer magnetic ring 4 have simple structure and low manufacturing cost.

In some embodiments, the first radial cross section 31 and the second radial cross section 41 are spaced apart in the axial direction of the rotor 2, so that an axial magnetic attraction force is formed between the inner magnetic ring 3 and the outer magnetic ring 4, and the axial force acting on the rotor 2 with corresponding magnitude can be counteracted, so that the axial force of the rotor 2 is balanced, thereby reducing the radial design size of the air thrust bearing 10, reducing the loss of the air thrust bearing 10 and reducing the heating condition of the air thrust bearing 10.

In the orientation shown in fig. 1 and 3, when the first radial cross section 31 is shifted to the right, the first radial cross section 31 is located to the right of the second radial cross section 41, the magnetic attraction force on the inner magnetic ring 3 is to the left, and when the first radial cross section 31 is shifted to the left, the first radial cross section 31 is located to the left of the second radial cross section 41, the magnetic attraction force on the inner magnetic ring 3 is to the right.

Specifically, referring to fig. 1, when the outer magnet ring 4 is located on the second cover 13 and the inner magnet ring is located on the other end of the rotor 2, when the first radial cross section 31 is located on the side of the second radial cross section 41 facing away from the first cover 12 (the first radial cross section 31 is located on the right side of the second radial cross section 41), the magnetic attraction force on the inner magnet ring 3 faces the first cover 12, the magnetic attraction force on the inner magnet ring 3 faces the left, and when the first radial cross section 31 is located on the side of the second radial cross section 41 adjacent to the first cover 11 (the first radial cross section 31 is located on the left side of the second radial cross section 41), the magnetic attraction force on the inner magnet ring 3 faces the second cover 13, and the magnetic attraction force on the inner magnet ring 3 faces the right.

In some embodiments, the dimension of the inner magnetic ring 3 in the axial direction is different from the dimension of the outer magnetic ring 4 in the axial direction, so that the rotor can adapt to different structural layouts on the rotor 2 and the casing 1 (the first cover 12 and/or the second cover 13 of the casing 1), and the applicability is good.

Specifically, the first radial cross section 31 of the inner magnetic ring 3 and the second radial cross section 41 of the outer magnetic ring 4 are located on the same plane, the axial dimension of the inner magnetic ring 3 is smaller than that of the outer magnetic ring 4, the occupied space of the inner magnetic ring 3 on the rotor 2 is small, and the rotor 2 is beneficial to keeping a relatively compact structural layout. Accordingly, the axial dimension of the outer magnetic ring 3 is smaller than the axial dimension of the inner magnetic ring 3, which is beneficial for the casing 1 (the first casing 12 and/or the second casing 13 of the casing 1) to maintain a relatively compact structural layout. In addition, when the first radial cross section 31 of the inner magnetic ring 3 and the second radial cross section 41 of the outer magnetic ring 4 are spaced apart in the axial direction of the rotor 2, it is not only possible to facilitate the rotor 2 or the casing 1 to maintain a relatively compact structural layout, but also to have the effect of balancing at least a part of the axial force of the rotor 2.

The stator 5 is mounted in the housing 11, the stator 5 being fitted over the rotor 2 with play in its radial direction with respect to the rotor 2, the stator 5 having a fourth radial cross section 51 centered in its axial direction, the center of the stator 5 in its axial direction being located on this fourth radial cross section 51 of the stator 5.

In some embodiments, the third radial cross section 211 and the fourth radial cross section 51 are spaced apart in the axial direction of the rotor 2. While the radial cross section of the center of the rotor in the axial direction of the centrifugal compressor 100 in the related art coincides with the radial cross section of the center of the stator in the axial direction thereof, there is no axial force therebetween, the centrifugal compressor 100 of the embodiment of the present utility model arranges the magnetic steel 21 and the stator 5 in a staggered manner, so that a magnetic pulling force in the axial direction of the rotor 2 can be generated, thereby balancing the axial force acting on the rotor 2.

The direction and the magnitude of the magnetic pulling force can be adjusted by adjusting the offset direction and the offset distance of the magnetic steel 21.

Referring to fig. 1, when the first radial cross section 31 and the second radial cross section 41 are on the same plane, when the third radial cross section 211 is located on the side of the fourth radial cross section 51 facing away from the second cover 13 in the axial direction of the rotor 2 (the third radial cross section 211 is located on the left side of the fourth radial cross section 51), the generated magnetic pulling force is directed toward the second cover 13, and the magnetic pulling force is directed to the right. When the third radial cross section 211 is located on the side of the fourth radial cross section 51 facing away from the first cover 12 in the axial direction of the rotor 2 (the third radial cross section 211 is located on the right side of the fourth radial cross section 51), the generated magnetic pull force is directed toward the first cover 12, and the magnetic pull force is directed toward the left.

In other embodiments, the direction of the magnetic pulling force formed on the magnetic steel 21 is the same as the direction of the magnetic attraction force formed on the inner magnetic ring 3 when the direction of the offset of the third radial cross section 211 and the fourth radial cross section 51 is the same as the direction of the offset of the first radial cross section 31 and the second radial cross section 41, so that the magnetic pulling force and the magnetic attraction force can be overlapped, the axial force which can be offset by the rotor 2 is further improved, and the size of the air bearing 10 can be further reduced.

For example, in the orientation shown in fig. 1, 3 and 4, the first radial cross section 31 is located to the left of the second radial cross section 41, the resulting magnetic attraction force is to the right, the third radial cross section 211 is located to the left of the fourth radial cross section 51, the resulting magnetic attraction force is to the right, the magnetic attraction force is superimposed with the magnetic pulling force, and the axial force acting on the rotor 2 is balanced. Alternatively, the first radial cross section 31 is located to the right of the second radial cross section 41, creating a magnetic attraction force to the left, the third radial cross section 211 is located to the right of the fourth radial cross section 51, creating a magnetic attraction force to the left, which is superimposed with a magnetic pulling force, balancing the axial force acting on the rotor 2.

In some embodiments, the first turbine 8 has a first volute 81 and a first impeller 82, the first volute 81 is provided on the first cover 12, the first impeller 82 is provided on the rotor 2, the first impeller 82 is located on the one end of the rotor 2, and the centrifugal compressor 100 of the embodiment of the utility model is a one-stage compressor. The first gasket 71 is provided between the first scroll 81 and the first cover 12 and/or between the first cover 12 and the housing 11.

When the first gasket 71 is added between the first scroll case 81 and the first casing 12, the distance between the first scroll case 81 and the casing 11 in the axial direction of the rotor 2 becomes large, and when the first gasket 71 is added between the first casing 12 and the casing 11, the distance between each of the first scroll case 81 and the first casing 12 and the casing 11 in the axial direction of the rotor 2 becomes large, and the one end of the rotor 2 is moved in a direction away from the second casing 13 (i.e., leftward) without changing the fitting gap between the first scroll case 81 and the first impeller 82 and the fitting position of the one end of the rotor 2 with the first impeller 82, and the third radial cross section 211 of the magnetic steel 21 is shifted in the direction of the first casing 12 (i.e., leftward), and the direction of the generated magnetic pulling force is directed toward the second casing 13 (i.e., the direction of the magnetic pulling force is directed toward the right).

Alternatively, when the thickness of the first gasket 71 between the first volute 81 and the first cover 12 and/or between the first cover 12 and the housing 11 is m, the third radial cross section 211 of the magnetic steel 21 and the fourth radial cross section 51 of the stator 5 are located on the same plane, and if the thickness of the first gasket 71 is adjusted to increase the value of m, the one end of the rotor 2 is driven to move away from the direction of the second cover 13 (i.e., to the left), the third radial cross section 211 of the magnetic steel 21 is biased away from the direction of the second cover 13 (i.e., to the left), and the direction of the generated magnetic pulling force is directed toward the second cover 13 (i.e., the direction of the magnetic pulling force is directed toward the right). If the thickness of the first spacer 71 is adjusted to decrease the value of m, the one end of the rotor 2 is driven to move in the direction of the second cover 13 (i.e., rightward), the third radial cross section 211 of the magnetic steel 21 is biased in the direction of the second cover 13 (i.e., rightward), and the direction of the generated magnetic pulling force is directed away from the second cover 13 (i.e., the direction of the magnetic pulling force is directed leftward).

The centrifugal compressor 100 of the embodiment of the utility model adjusts the dislocation distance and the offset direction of the magnetic steel 21 by adjusting the thickness of the first gasket 7, and then adjusts the magnitude and the direction of the magnetic pulling force.

Further, the first cover 12 is integrally formed with the housing 11, and the first gasket 71 is provided between the first scroll 81 and the first cover 12.

In some embodiments, the centrifugal compressor 100 further includes a second turbine 9 and a second gasket 72, the second turbine 9 has a second volute 91 and a second impeller 92, the second volute 91 is provided on the second cover 13, the second impeller 92 is provided on the rotor 2, and the second impeller 92 is located on the other end of the rotor 2, and the centrifugal compressor 100 of the embodiment of the present utility model is a two-stage compressor, as shown with reference to fig. 4.

The second gasket 72 is provided between the second cover 13 and the housing 11 and/or between the second cover 13 and the second scroll 91.

When the thickness of the first gasket 71 between the first volute 81 and the first cover 12 is m' and the thickness of the second gasket 72 between the second cover 13 and the housing 11 and/or between the second cover 13 and the second volute 91 is n, the third radial cross section 211 of the magnetic steel 21 is on the same plane as the fourth radial cross section 51 of the stator 5.

If the thickness of the first spacer 71 is adjusted to increase the value of m' by x, the one end of the rotor 2 is driven to move away from the second cover 13 (i.e., to the left), the third radial cross section 211 of the magnetic steel 21 is biased away from the second cover 13 (i.e., to the left), the direction of the generated magnetic pulling force is directed toward the second cover 13 (i.e., the direction of the magnetic pulling force is directed toward the right), and the thickness of the second spacer 72 is reduced by x, the second volute 91 and the second impeller 92 are moved toward the direction approaching the first cover 12, so that the assembly gap between the second volute 91 and the second impeller 92 and/or the assembly position of the second impeller 92 and the other end of the rotor 2 can be prevented from being changed.

If the thickness of the first spacer 71 is adjusted to decrease the value of m by y, the thickness of the second spacer 72 increases by y, so that the one end of the rotor 2 is driven to move toward the second cover 13 (i.e., rightward), and the direction of the generated magnetic pulling force is away from the second cover 13 (i.e., the direction of the magnetic pulling force is leftward).

Compared with the mode of directly changing the position of the magnetic steel on the rotor to realize the deflection of the magnetic steel, the centrifugal compressor 100 provided by the embodiment of the utility model has the advantages that the first gasket 71 and the second gasket 72 are arranged to realize the deflection of the magnetic steel, the manufacture of the first gasket 71 and the second gasket 72 is simple, the processing cost is low, the gaskets with different thicknesses can be produced in batches, the quick assembly of the centrifugal compressor 100 is convenient, the accurate control of the deflection of the magnetic steel 33 by the centrifugal compressor 100 is convenient, the applicability is strong, the modification to the structure and the size of the rotor is small, the production cost of the centrifugal compressor 100 can be reduced, and the production efficiency of the centrifugal compressor 100 is improved.

In the description of the present utility model, it should be understood that the terms "center", "longitudinal", "lateral", "length", "width", "thickness", "upper", "lower", "front", "rear", "left", "right", "vertical", "horizontal", "top", "bottom", "inner", "outer", "clockwise", "counterclockwise", "axial", "radial", "circumferential", etc. indicate orientations or positional relationships based on the orientations or positional relationships shown in the drawings are merely for convenience in describing the present utility model and simplifying the description, and do not indicate or imply that the device or element being referred to must have a specific orientation, be configured and operated in a specific orientation, and therefore should not be construed as limiting the present utility model.

Furthermore, the terms "first," "second," and the like, are used for descriptive purposes only and are not to be construed as indicating or implying a relative importance or implicitly indicating the number of technical features indicated. Thus, a feature defining "a first" or "a second" may explicitly or implicitly include at least one such feature. In the description of the present utility model, the meaning of "plurality" means at least two, for example, two, three, etc., unless specifically defined otherwise.

In the present utility model, unless explicitly specified and limited otherwise, the terms "mounted," "connected," "secured," and the like are to be construed broadly, and may be, for example, fixedly connected, detachably connected, or integrally formed; may be mechanically connected, may be electrically connected or may be in communication with each other; either directly or indirectly, through intermediaries, or both, may be in communication with each other or in interaction with each other, unless expressly defined otherwise. The specific meaning of the above terms in the present utility model can be understood by those of ordinary skill in the art according to the specific circumstances.

In the present utility model, unless expressly stated or limited otherwise, a first feature "up" or "down" a second feature may be the first and second features in direct contact, or the first and second features in indirect contact via an intervening medium. Moreover, a first feature being "above," "over" and "on" a second feature may be a first feature being directly above or obliquely above the second feature, or simply indicating that the first feature is level higher than the second feature. The first feature being "under", "below" and "beneath" the second feature may be the first feature being directly under or obliquely below the second feature, or simply indicating that the first feature is less level than the second feature.

For purposes of this disclosure, the terms "one embodiment," "some embodiments," "example," "a particular example," or "some examples," etc., mean that a particular feature, structure, material, or characteristic described in connection with the embodiment or example is included in at least one embodiment or example of the utility model. In this specification, schematic representations of the above terms are not necessarily directed to the same embodiment or example. Furthermore, the particular features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples. Furthermore, the different embodiments or examples described in this specification and the features of the different embodiments or examples may be combined and combined by those skilled in the art without contradiction.

While embodiments of the present utility model have been shown and described above, it will be understood that the above embodiments are illustrative and not to be construed as limiting the utility model, and that variations, modifications, alternatives and variations may be made to the above embodiments by one of ordinary skill in the art within the scope of the utility model.

Claims (10)

1. A centrifugal compressor, comprising:

a housing (1);

a rotor (2), wherein the rotor (2) is arranged in the shell (1);

an inner magnetic ring (3), wherein the inner magnetic ring (3) is arranged on the rotor (2); and

the outer magnetic ring (4) is arranged on the shell (1), the outer magnetic ring (4) is sleeved on the inner magnetic ring (3) and is provided with a gap with the inner magnetic ring (3) in the radial direction of the rotor (2), and the inner peripheral surface of the outer magnetic ring (4) is opposite to the magnetic pole on the outer peripheral surface of the inner magnetic ring (3).

2. Centrifugal compressor according to claim 1, wherein each of the inner magnetic ring (3) and the outer magnetic ring (4) is axially magnetized.

3. Centrifugal compressor according to claim 2, wherein the inner magnetic ring (3) has a first radial cross section in its axial centre, the poles of the inner magnetic ring (3) being opposite on both sides of the first radial cross section in its axial direction; the outer magnet ring (4) has a second radial cross section at the center in the axial direction thereof, and the poles of the outer magnet ring (4) on both sides of the second radial cross section in the axial direction thereof are opposite.

4. A centrifugal compressor according to claim 3, wherein the first radial cross section and the second radial cross section are spaced apart in the axial direction of the rotor (2).

5. Centrifugal compressor according to claim 3 or 4, wherein the inner magnetic ring (3) has a different dimension in its axial direction than the outer magnetic ring (4).

6. The centrifugal compressor according to claim 1, wherein,

the casing (1) comprises a casing (11), a first casing (12) and a second casing (13), wherein the first casing (12) is positioned on one side of the casing (11), one axial end of the rotor (2) is rotationally connected with the first casing (12), the second casing (13) is positioned on the other axial side of the casing (11), the other axial end of the rotor (2) is rotationally connected with the second casing (13), the first casing (12) and/or the second casing (13) is provided with the outer magnetic ring (4), and the outer magnetic ring (4) has a second radial cross section at the axial center of the outer magnetic ring;

the rotor (2) comprises a magnetic steel (21), the magnetic steel (21) having a third radial cross section at the center in its axial direction, the magnetic steel (21) being axially spaced apart from the inner magnetic ring (3), the inner magnetic ring (3) having a first radial cross section at the center in its axial direction;

the centrifugal compressor further comprises a stator (5), wherein the stator (5) is installed in the shell (11), the stator (5) is sleeved on the rotor (2) and has a gap with the rotor (2) in the radial direction, the stator (5) has a fourth radial cross section at the center in the axial direction, the third radial cross section is spaced from the fourth radial cross section, the offset direction of the third radial cross section and the fourth radial cross section is the same as the offset direction of the first radial cross section and the second radial cross section, or the first radial cross section and the second radial cross section are on the same plane.

7. The centrifugal compressor according to claim 6, further comprising:

a first turbine (8), the first turbine (8) having a first volute (81) and a first impeller (82), the first volute (81) being provided on the first cover (12), the first impeller (82) being provided on the rotor (2); and

and a first gasket (71), wherein the first gasket (71) is arranged between the first volute (81) and the first cover (12) and/or between the first cover (12) and the shell (11).

8. The centrifugal compressor according to claim 7, further comprising:

a second turbine (9), wherein the second turbine (9) is provided with a second volute (91) and a second impeller (92), the second volute (91) is arranged on the second cover (13), and the second impeller (92) is arranged on the rotor (2); and

-a second gasket (72), said second gasket (72) being arranged between said second cover (13) and said housing (11) and/or between the second cover (13) and said second volute (91).

9. The centrifugal compressor according to claim 7, wherein the first cover (12) is integrally formed with the housing (11), the first gasket (71) being provided between the first volute (81) and the first cover (12).

10. Centrifugal compressor according to claim 1, further comprising an air bearing (10) provided on the rotor (2).