Axial magnetic suspension bearing and magnetic suspension rotating machine

Abstract

The utility model provides an axial magnetic suspension bearing and magnetic suspension rotating machinery, the axial magnetic suspension bearing comprises an outer cylinder, two axial stator assemblies and a thrust disc are assembled in a central through hole of the outer cylinder, each axial stator assembly comprises a stator iron core and a winding, the thrust disc is located between magnetic poles of the two stator iron cores, and the winding is arranged between the two stator iron cores. The magnetic poles of the stator iron core comprise an outer magnetic pole and an inner magnetic pole, a first overflowing ring groove is formed in the surface area, opposite to the outer magnetic pole, of the thrust disc, winding cooling flow channels are formed in the two axial stator assemblies, and the winding cooling flow channels are used for cooling windings at the corresponding positions. And the winding cooling flow channels of the two axial stator assemblies are communicated through the rotating grooves. According to the utility model, the thrust disc and the bearing winding can be effectively cooled.

Description

Technical Field

[0001] The utility model belongs to the technical field of magnetic levitation bearing design, and particularly relates to an axial magnetic levitation bearing and a magnetic levitation rotating machine. Background Art

[0002] At present, the heat dissipation of magnetic levitation blowers mainly relies on external cooling equipment, such as external cooling fans, water cooling systems, and heat exchangers, etc. The equipment maintenance cost is high, the structure system is complex, and potential safety hazards are increased. Or in the form of negative pressure, air is sucked from the blower to guide the heat out, which cannot more effectively achieve the heat dissipation of internal components, especially the heat dissipation of axial magnetic bearings is insufficient, affecting the stable operation of magnetic levitation blowers.

[0003] The axial magnetic bearing realizes the axial movement of the rotating shaft. It is necessary to have an axial force-bearing component on the rotating shaft, which is the thrust disk. The materials of the axial magnetic bearing and the thrust disk are pure iron solid structures, with relatively large self-losses, general thermal conductivity, and narrow space. If not effectively cooled, it will generate serious heat. Usually, in order to avoid excessive temperature rise of the axial magnetic bearing, forced air cooling is often applied externally to dissipate heat from the magnetic bearing. The cooling air is input from the outside and passes through the gap between the bearing stator and the thrust disk to dissipate heat from the axial magnetic bearing, but the heat dissipation efficiency is not high. Summary of the Utility Model

[0004] Therefore, the utility model provides an axial magnetic levitation bearing and a magnetic levitation rotating machine, which can solve the technical problems of serious heating and low heat dissipation efficiency of the axial magnetic bearing in the existing magnetic levitation rotating machine.

[0005] To solve the above problems, the present utility model provides an axial magnetic levitation bearing, which includes an outer cylinder. A first axial stator assembly, a second axial stator assembly and a thrust disc are assembled in the central through hole of the outer cylinder. The first axial stator assembly includes a first stator core and a first winding assembled on the first stator core. The second axial stator assembly includes a second stator core and a second winding assembled on the second stator core. The thrust disc is located between the magnetic poles of the first stator core and the magnetic poles of the second stator core. The magnetic poles of the first stator core include a first outer magnetic pole and a first inner magnetic pole. The magnetic poles of the second stator core include a second outer magnetic pole and a second inner magnetic pole. A first overflow ring groove is formed on the surface area of the first outer magnetic pole and the thrust disc facing each other. A first overflow ring groove is also formed on the surface area of the second outer magnetic pole and the thrust disc facing each other. And the first overflow ring groove is coaxially arranged with the thrust disc. A winding cooling flow channel is formed in both the first axial stator assembly and the second axial stator assembly. The winding cooling flow channel is used to cool the first winding and the second winding. And the winding cooling flow channels respectively provided in the first axial stator assembly and the second axial stator assembly are communicated through the first overflow ring groove.

[0006] In some embodiments, the first overflow ring groove is formed on the magnetic pole end faces of the first outer magnetic pole and the second outer magnetic pole. Any radial plane perpendicular to the axis of the thrust disc is defined as a radial plane. When projected on the radial plane, the outer circular contour of the thrust disc is within the groove width range of the first overflow ring groove.

[0007] In some embodiments, a second overflow ring groove is further formed on the magnetic pole end faces of the first outer magnetic pole and the second outer magnetic pole. The first overflow ring groove and the second overflow ring groove are concentrically arranged, and the first overflow ring groove is located radially outside the second overflow ring groove.

[0008] In some embodiments, the first outer magnetic pole includes a first cover plate portion extending radially inward along the thrust disc. The second outer magnetic pole includes a second cover plate portion extending radially inward along the thrust disc. The first overflow ring groove and the second overflow ring groove are formed on the first cover plate portion and the second cover plate portion.

[0009] In some embodiments, the second overflow ring groove penetrates to the radial inner ring wall of the first cover plate portion or the second cover plate portion.

[0010] In some embodiments, a first through hole penetrating the inner and outer sides is formed in the first stator yoke. A first annular gap is formed between the radially inner circle of the first winding and the radially outer annular wall of the first inner magnetic pole. A first overcurrent gap is formed between the end face of the first winding away from the first cover plate portion and the inner end face of the first stator yoke. The first through hole, the first overcurrent gap, and the first annular gap form the winding cooling flow path of the first axial stator assembly; a second through hole penetrating the inner and outer sides is formed in the second stator yoke. A second annular gap is formed between the radially inner circle of the second winding and the radially outer annular wall of the second inner magnetic pole. A second overcurrent gap is formed between the end face of the second winding away from the second cover plate portion and the inner end face of the second stator yoke. The second through hole, the second overcurrent gap, and the second annular gap form the winding cooling flow path of the second axial stator assembly.

[0011] In some embodiments, the first stator core further includes a first stator yoke between the first outer magnetic pole and the first inner magnetic pole. The second stator core further includes a second stator yoke between the second outer magnetic pole and the second inner magnetic pole. The first stator yoke has a first outer convex ring protruding from the radially outer annular wall of the first outer magnetic pole. The second stator yoke has a second outer convex ring protruding from the radially outer annular wall of the second outer magnetic pole. The first axial stator assembly is assembled in the outer cylinder via the first outer convex ring, and the second axial stator assembly is assembled in the outer cylinder via the second outer convex ring to form a cooling cavity between the first outer magnetic pole and the outer cylinder and between the second outer magnetic pole and the outer cylinder. The first overcurrent ring groove of the first axial stator assembly communicates with the first overcurrent ring groove of the second axial stator assembly through the cooling cavity.

[0012] In some embodiments, the outer cylinder has a bearing exhaust hole, and the bearing exhaust hole communicates the cooling cavity and the external space of the outer cylinder.

[0013] The present utility model further provides a magnetic levitation rotating machine, including a rotating shaft and an axial magnetic levitation bearing for defining the axial displacement of the rotating shaft. The axial magnetic levitation bearing is the above-mentioned axial magnetic levitation bearing. The first end of the rotating shaft is connected to a blower turbine, and the second end of the rotating shaft is connected to a cooling impeller. The cooling air flow introduced into the magnetic levitation rotating machine by the cooling impeller and / or a part of the air flow at the blower turbine can enter the axial magnetic levitation bearing through the winding cooling flow path and flow out of the axial magnetic levitation bearing through the first overcurrent ring groove.

[0014] In some embodiments, the magnetic levitation rotating machine further includes a cylinder body, and a motor stator capable of driving the rotating shaft to rotate is assembled in the cylinder body. A stator cooling flow path is formed in a region corresponding to the motor stator in the cylinder body.

[0015] The axial magnetic suspension bearing and the magnetic suspension rotating machine provided by the utility model have the following beneficial effects:

[0016] In this technical solution, by forming a first overcurrent ring groove on the surface area (i.e., the left end face and the right end face) of the thrust disk opposite to the first outer magnetic pole and the second outer magnetic pole, the width of the partial air gap area between the magnetic pole and the thrust disk can be increased. Furthermore, it can ensure that the cooling air flow can smoothly circulate inside the axial magnetic suspension bearing, and there is a large amount of cooling fluid, achieving the purpose of efficiently cooling the thrust disk. At the same time, winding cooling channels are arranged in each axial stator assembly and are connected to the aforementioned first overcurrent ring groove, so that the cooling fluid entering the bearing can efficiently cool the windings at the same time, thereby effectively ensuring the operation reliability of the magnetic suspension bearing. At the same time, the technical solution of the utility model is simple and easy to implement, and the manufacturing cost is relatively low. It should be emphasized that the overcurrent ring groove in this technical solution is an annular groove coaxial with the thrust disk. When the thrust disk rotates, there will be no magnetic field alternation in the circumferential direction, thereby avoiding the occurrence of eddy current heating caused by the magnetic field alternation when the rotor rotates due to the formation of a groove with a radial shape structure in the circumferential direction. BRIEF DESCRIPTION OF THE DRAWINGS

[0017] In order to more clearly illustrate the embodiments of the present utility model or the technical solutions in the prior art, the following will briefly introduce the drawings required for use in the description of the embodiments or the prior art. The drawings in the following description are only exemplary. For those of ordinary skill in the art, without creative efforts, other implementation drawings can also be obtained based on the provided drawings.

[0018] Figure 1 is a schematic diagram of the internal structure (half-section) of an axial magnetic suspension bearing according to an embodiment of the present utility model;

[0019] Figure 2 is the Figure 1 schematic diagram of the internal circulation of the axial magnetic suspension bearing in which the cooling air flow circulates (arrow indication);

[0020] Figure 3 is a schematic diagram of the internal structure (half-section) of an axial magnetic suspension bearing according to another embodiment of the present utility model;

[0021] Figure 4 is a schematic diagram of the internal structure of the first embodiment of the magnetic suspension rotating machine of the present utility model, and the arrows in the figure show the flow path of the cooling air flow;

[0022] Figure 5 is a schematic diagram of the internal structure of the second embodiment of the magnetic suspension rotating machine of the present utility model, and the arrows in the figure show the flow path of the cooling air flow;

[0023] Figure 6 It is a schematic diagram of the internal structure of the third embodiment of the magnetic levitation rotating machine of the present utility model. The arrows in the figure show the flow path of the cooling air flow;

[0024] Figure 7 It is a schematic diagram of the internal structure of the fourth embodiment of the magnetic levitation rotating machine of the present utility model. The arrows in the figure show the flow path of the cooling air flow.

[0025] The reference numerals are:

[0026] 1. Outer cylinder; 11. Bearing exhaust hole; 2. First axial stator assembly; 21. First stator core; 211. First outer magnetic pole; 2111. First cover part; 212. First inner magnetic pole; 213. First stator yoke part; 2131. First through hole; 22. First winding; 3. Second axial stator assembly; 31. Second stator core; 311. Second outer magnetic pole; 3111. Second cover part; 312. Second inner magnetic pole; 313. Second stator yoke part; 3131. Second through hole; 32. Second winding; 4. Thrust disk; 51. First overflow ring groove; 53. Second overflow ring groove; 100. Rotating shaft; 101. Axial magnetic levitation bearing; 102. Blower turbine; 1021. Turbine volute; 1022. Front end cover; 103. Cooling impeller; 1031. Rear end cover; 1032. Deflector; 104. Radial magnetic levitation bearing; 1041. Front housing; 1042. Rear housing; 105. Motor stator; 106. Cylinder body; 1061. Exhaust hole; 1062. Stator cooling flow channel. Detailed implementation manners

[0027] Next, the technical solutions in the embodiments of the present utility model will be clearly and completely described in conjunction with the accompanying drawings in the embodiments of the present utility model. Obviously, the described embodiments are only a part of the embodiments of the present utility model, rather than all the embodiments. The following description of at least one exemplary embodiment is actually only illustrative and in no way limits the present utility model and its application or use. Based on the embodiments of the present utility model, all other embodiments obtained by those of ordinary skill in the art without creative efforts shall fall within the protection scope of the present utility model.

[0028] In the description of the present utility model, it should be understood that the orientation or positional relationship indicated by orientation words such as "front, rear, upper, lower, left, right", "lateral, vertical, perpendicular, horizontal" and "top, bottom", etc. is usually based on the orientation or positional relationship shown in the drawings. It is only for the convenience of describing the present utility model and simplifying the description. Without contrary description, these orientation words do not indicate and imply that the device or element referred to must have a specific orientation or be constructed and operated in a specific orientation. Therefore, it should not be construed as a limitation on the protection scope of the present utility model; the orientation words "inside, outside" refer to the inside and outside relative to the contour of each component itself.

[0029] For ease of description, spatial relative terms such as "above...", "over...", "on the upper surface of...", "above-mentioned", etc. can be used here to describe the spatial positional relationship between a device or feature shown in the drawings and other devices or features. It should be understood that the spatial relative terms are intended to include different orientations in use or operation in addition to the orientation described in the drawings for the device. For example, if the device in the drawing is inverted, the device described as "above other devices or structures" or "over other devices or structures" will then be positioned as "below other devices or structures" or "under other devices or structures". Thus, the exemplary term "above..." can include both the orientations of "above..." and "below...". The device can also be positioned in other different ways (rotated 90° or in other orientations), and the corresponding explanations for the spatial relative descriptions used here are made accordingly.

[0030] In addition, it should be noted that using words such as "first", "second", etc. to limit components is only for the convenience of distinguishing the corresponding components. Without additional statement, the above-mentioned words have no special meaning. Therefore, it should not be construed as a limitation on the protection scope of the present utility model.

[0031] See in conjunction with Figures 1 to 7As shown, according to an embodiment of the present utility model, an axial magnetic levitation bearing is provided, which includes an outer cylinder 1 (in some cases, the outer cylinder 1 can be the cylinder 106 hereinafter). A first axial stator assembly 2, a second axial stator assembly 3 and a thrust disc 4 are assembled in the central through hole of the outer cylinder 1. The first axial stator assembly 2 includes a first stator core 21 and a first winding 22 assembled on the first stator core 21. The second axial stator assembly 3 includes a second stator core 31 and a second winding 32 assembled on the second stator core 31. The thrust disc 4 is located between the magnetic poles of the first stator core 21 and the magnetic poles of the second stator core 31, and corresponding air gaps are respectively formed between the thrust disc 4 and the first stator core 21 and between the thrust disc 4 and the second stator core 31. The magnetic poles of the first stator core 21 include a first outer magnetic pole 211 and a first inner magnetic pole 212. The magnetic poles of the second stator core 31 include a second outer magnetic pole 311 and a second inner magnetic pole 312. A first overcurrent ring groove 51 is formed on the surface areas of the first outer magnetic pole 211 and the thrust disc 4 facing each other. A first overcurrent ring groove 51 is also formed on the surface areas of the second outer magnetic pole 311 and the thrust disc 4 facing each other. And the first overcurrent ring groove 51 is coaxially arranged with the thrust disc 4. Winding cooling channels (not labeled in the figure) are formed in both the first axial stator assembly 2 and the second axial stator assembly 3. The winding cooling channels are used to cool the first winding 22 and the second winding 32. And the winding cooling channels respectively provided in the first axial stator assembly 2 and the second axial stator assembly 3 are communicated through the first overcurrent ring groove 51.

[0032] In this technical solution, by forming the first overcurrent ring groove 51 on the surface areas of the thrust disc 4 facing the first outer magnetic pole 211 and the second outer magnetic pole 311 (i.e., the left end face and the right end face), the width of a partial air gap area between the magnetic poles and the thrust disc 4 can be increased. Furthermore, it can ensure that the cooling air flow can smoothly flow through the inside of the axial magnetic levitation bearing, and there is a large amount of cooling fluid, achieving the purpose of efficiently cooling the thrust disc 4. At the same time, winding cooling channels are arranged in each axial stator assembly and are communicated with the aforementioned first overcurrent ring groove 51, so that the cooling fluid entering the bearing can efficiently cool the windings at the same time. Furthermore, the operation reliability of the magnetic levitation bearing is effectively ensured. At the same time, the technical solution of the present utility model is simple and easy to implement, and the manufacturing cost is relatively low. It should be emphasized that the overcurrent ring groove in this technical solution is a circular groove coaxially arranged with the thrust disc 4. When the thrust disc 4 rotates, no magnetic field alternation will be formed in the circumferential direction. Furthermore, the occurrence of the phenomenon of eddy current heating caused by the magnetic field alternation when the rotor rotates due to the formation of a groove with a radial shape structure in the circumferential direction can be eliminated.

[0033] It can be understood that the foregoing first overflow ring groove 51 can be specifically formed on the left and right end faces of the thrust disk 4. In a specific embodiment, specifically refer to Figure 1 and Figure 2 As shown, the first overflow ring groove 51 is formed on the magnetic pole end faces of the first outer magnetic pole 211 and the second outer magnetic pole 311. Define any radial plane perpendicular to the axis of the thrust disk 4 as the radial plane. Projecting on the radial plane, the outer circular contour of the thrust disk 4 is within the groove width range of the first overflow ring groove 51, so that the cooling air flow entering the bearing can flow out more smoothly through the first overflow ring groove 51. In this technical solution, the overflow ring groove is formed on the magnetic pole end face. During the operation of the bearing, the position of its overflow ring groove is relatively stationary, so the occurrence of eddy current heating phenomenon can be effectively prevented.

[0034] In some embodiments, a second overflow ring groove 53 is further formed on the magnetic pole end faces of the first outer magnetic pole 211 and the second outer magnetic pole 311. The first overflow ring groove 51 and the second overflow ring groove 53 are concentrically arranged, and the first overflow ring groove 51 is radially outside the second overflow ring groove 53.

[0035] In this technical solution, by arranging the second overflow ring groove 53 radially inside the first overflow ring groove 51, the flow area of the cooling air flow flowing into the bearing can be further increased, and then the cooling air flow rate entering the bearing can be further improved, and the cooling and heat dissipation effect is better.

[0036] In some embodiments, the first outer magnetic pole 211 includes a first cover plate portion 2111 extending radially inward along the thrust disk 4, and the second outer magnetic pole 311 includes a second cover plate portion 3111 extending radially inward along the thrust disk 4. The first overflow ring groove 51 and the second overflow ring groove 53 are formed on the first cover plate portion 2111 and the second cover plate portion 3111.

[0037] The foregoing first cover plate portion 2111 and second cover plate portion 3111 are specifically both an annular plate, which is used as a part of the stator core to conduct the magnetic circuit formed by the corresponding windings. Since it extends radially inward along the thrust disk 4, the outer diameter of the corresponding thrust disk 4 can be designed smaller, so that the eccentric mass of the rotating shaft can be reduced, which is beneficial to improving the dynamic balance performance of the rotating shaft. And forming the foregoing first overflow ring groove 51 and second overflow ring groove 53 on the first cover plate portion 2111 and the second cover plate portion 3111 can minimize the adverse influence on the magnetic field due to the setting of the grooves by adjusting the areas of the first cover plate portion 2111 and the second cover plate portion 3111.

[0038] In some embodiments, the second overcurrent ring groove 53 penetrates through to the radial inner ring wall of the first cover plate portion 2111 or the second cover plate portion 3111, ensuring that the cooling air flow entering the bearing through the winding cooling channels on the inner magnetic poles can more smoothly enter the air gap between the outer magnetic poles and the thrust disk 4.

[0039] In some embodiments, the first stator core 21 further includes a first stator yoke portion 213 between the first outer magnetic pole 211 and the first inner magnetic pole 212, and the second stator core 31 further includes a second stator yoke portion 313 between the second outer magnetic pole 311 and the second inner magnetic pole 312. The first stator yoke portion 213 has a first outwardly protruding ring (not labeled in the figure) protruding from the radial outer ring wall of the first outer magnetic pole 211, and the second stator yoke portion 313 has a second outwardly protruding ring (not labeled in the figure) protruding from the radial outer ring wall of the second outer magnetic pole 311. The first axial stator assembly 2 is assembled into the outer cylinder 1 via the first outwardly protruding ring, and the second axial stator assembly 3 is assembled into the outer cylinder 1 via the second outwardly protruding ring to form a cooling cavity (not labeled in the figure) between the first outer magnetic pole 211 and the outer cylinder 1 and between the second outer magnetic pole 311 and the outer cylinder 1. The winding cooling channels of the first axial stator assembly 2 communicate with the winding cooling channels of the second axial stator assembly 3 via the cooling cavity.

[0040] In this technical solution, by providing an outwardly protruding ring on the stator yoke portion along its radial direction, a corresponding cooling cavity is formed between the stator core and the outer cylinder 1. At the same time, the cooling air flows in the two axial stator assemblies communicate with this cooling cavity, so that the stator core can be cooled more efficiently and sufficiently, further preventing the temperature rise of the bearing from being too high.

[0041] In some embodiments, the outer cylinder 1 is provided with a bearing exhaust hole 11, and the bearing exhaust hole 11 communicates the cooling cavity and the external space of the outer cylinder 1, so that the cooling air flow entering the bearing can cool and dissipate heat from the inner magnetic poles, windings, thrust disk 4 and outer magnetic poles in sequence and then be discharged to the external environment.

[0042] In some embodiments, a first through hole 2131 penetrating the inner and outer sides is formed in the first stator yoke 213. A first annular gap (not labeled in the figure) is formed between the radially inner circle of the first winding 22 and the radially outer annular wall of the first inner magnetic pole 212. A first flow-through gap (not labeled in the figure) is formed between the end face of the first winding 22 away from the first cover plate portion 2111 and the inner end face of the first stator yoke 213. The first through hole 2131, the first flow-through gap, and the first annular gap form the winding cooling flow path of the first axial stator assembly 2. A second through hole 3131 penetrating the inner and outer sides is formed in the second stator yoke 313. A second annular gap (not labeled in the figure) is formed between the radially inner circle of the second winding 32 and the radially outer annular wall of the second inner magnetic pole 312. A second flow-through gap (not labeled in the figure) is formed between the end face of the second winding 32 away from the second cover plate portion 3111 and the inner end face of the second stator yoke 313. The second through hole 3131, the second flow-through gap, and the second annular gap form the winding cooling flow path of the second axial stator assembly 3.

[0043] In this technical solution, the winding cooling flow path and the aforementioned cooling cavity are respectively located on the radial inner and outer sides of the winding, enabling full and efficient cooling of the radial inner and outer sides of the axial stator assembly. Since the winding cooling flow path is in communication with the first flow-through annular groove 51, the cooling of the axial magnetic suspension bearing in the present invention is more comprehensive, balanced, and sufficient.

[0044] According to an embodiment of the present invention, there is also provided a magnetic levitation rotating machine, such as a blower, an air compressor, etc., including a rotating shaft 100 and an axial magnetic suspension bearing 101 for defining the axial displacement of the rotating shaft 100. The axial magnetic suspension bearing 101 is the aforementioned axial magnetic suspension bearing. The first end of the rotating shaft 100 is connected to a blower turbine 102, and the second end of the rotating shaft 100 is connected to a cooling impeller 103. The cooling air flow introduced into the magnetic levitation rotating machine by the cooling impeller 103 and / or a part of the air flow at the blower turbine 102 can enter the axial magnetic suspension bearing through the winding cooling flow path and flow out of the axial magnetic suspension bearing through the first flow-through annular groove 51. Thus, the pressure air flow generated by the cooling impeller 103 or the blower turbine 102 can be introduced into the axial magnetic suspension bearing to cool and dissipate heat the components inside the bearing, effectively preventing the bearing temperature from rising too high. It should be noted that in the present invention, since the cooling impeller 103 and the blower turbine share the same rotating shaft 100, when the magnetic levitation rotating machine is operating, the rotation of the cooling impeller 103 can be synchronously achieved, and thus external air can be introduced into the magnetic levitation rotating machine. That is, the direct drive of the cooling impeller 103 by the rotating shaft 100 is realized, without the need to separately configure a corresponding cooling structure for the cooling of the bearing, and without the need to separately provide a dedicated controller for the cooling impeller 103. The control logic is simple, and the heat dissipation reliability is high.

[0045] In some embodiments, the magnetic levitation rotating machine further includes a cylinder body 106, and a motor stator 105 capable of driving the rotating shaft 100 to rotate is assembled in the cylinder body 106. A stator cooling flow channel 1062 is formed in a region corresponding to the position of the cylinder body 106 and the motor stator 105. At this time, the cooling air flow driven by the cooling impeller 103 can flow through the air gap between the motor stator and rotor and the stator cooling flow channel 1062, so that the inner and outer sides of the motor stator 105 can be cooled and dissipated simultaneously.

[0046] Figures 4 to 7 The situation where only the cooling air flow driven by the cooling impeller 103 is used to cool the components in the magnetic levitation rotating machine is shown. The arrows in each figure indicate the flow path of the cooling air flow, and the aforementioned flow path varies according to the setting position of the exhaust hole 1061. In Figures 4 to 7 In the embodiments shown in each figure, the cooling impeller 103 rotates to drive the external air flow to enter the cylinder body 106 along the guide plate 1032. And Figure 4 、 Figure 5 and Figure 7 also show a way that a part of the cooling air flow is also led out from the blower turbine 102. That is, in a preferred embodiment, the cooling air flow is provided by the combined action of the cooling impeller 103 and the blower turbine. In this way, the introduction of the cooling air flow can be realized from both axial ends of the magnetic levitation rotating machine, so as to ensure the comprehensive cooling of the components in the magnetic levitation rotating machine, such as the aforementioned axial magnetic levitation bearing 101, radial magnetic levitation bearing 104, and motor stator 105.

[0047] The path of the cooling air flow of the magnetic levitation rotating machine of the present invention will be further described below in conjunction with each figure:

[0048] First Embodiment:

[0049] See Figure 4As shown in the figure, an active pure air-cooled heat dissipation system is adopted. The cold air is provided by the cooling impeller without an additional heat dissipation drive motor. The cooling impeller 103 is assembled at the rear end of the rotor (i.e., the second end of the rotating shaft 100, the same below). The rear radial bearing (i.e., the radial magnetic levitation bearing 104 near the second end of the rotating shaft 100, the same below) is located between the cooling impeller 103 and the motor stator 105. The front radial bearing (i.e., the radial magnetic levitation bearing 104 near the first end of the rotating shaft 100, the same below) is placed at the front end of the rotor. The axial bearing (i.e., the axial magnetic levitation bearing 101, the same below) is located between the front radial bearing and the front end cover 1022. A deflector 1032 for guiding the cooling impeller and a rear end cover 1031 are assembled on the rear housing 1042 to increase the air flow conduction and reduce the flow resistance. Several corresponding ventilation holes or ventilation grooves are opened on parts such as the rear housing 1042, the cylinder (i.e., the cylinder 106, the same below), and the front housing 1041 to facilitate the air flow conduction. The cooling gas of the cooling impeller passes through the flow channel on the rear housing 1042, passes through the rotor flow channel (i.e., the air gap between the stator and the rotor), cools the motor rotor, and then is divided into two paths for cooling at the front radial bearing: The first path: After entering the axial stator inner circulation channel hole and the right-side annular groove of the thrust disk or the magnetic pole on the stator (i.e., the winding cooling flow channel and the overflow annular groove in the second axial stator assembly), it converges with the main impeller leakage gas that has passed through the main impeller (i.e., the blower turbine 102) leakage flow channel (i.e., the cooling air flow diverted by the blower turbine) → the axial stator inner circulation channel hole and the left-side annular groove of the thrust disk or the magnetic pole on the stator (i.e., the winding cooling flow channel and the overflow annular groove in the first axial stator assembly), and then is discharged from the bearing exhaust hole 11; The second path: It cools the motor stator 105 through the motor stator flow channel (i.e., the stator cooling flow channel 1062, the same below) outside the motor stator and is discharged from the exhaust hole 1061 opened on the cylinder. This flow channel structure arrangement effectively cools the heating components such as the stator, rotor, radial bearing, and axial bearing. At the same time, for the high-heating components such as the thrust disk or the axial bearing stator, a ring groove structure is provided on the upper magnetic pole of the thrust disk or the axial bearing stator, and a flow channel hole is added on the inner ring of the axial bearing stator. At the high rotational speed of the rotor, the gas flow channel is increased, the cooling flow rate and speed of the incoming cooling air are increased, and the cooling of the axial magnetic bearing and the thrust disk is accelerated. The entire heat dissipation system has a simple structure, an efficient and reliable heat dissipation process, and improves the stability of the magnetic levitation system.

[0050] Second Embodiment:

[0051] See Figure 5As shown in the figure, an active pure air-cooling system is adopted. The cold air is provided by the cooling impeller without an additional heat dissipation drive motor. The cooling impeller 103 is assembled at the rear end of the rotor. The rear radial bearing is located between the cooling impeller 103 and the motor stator 105. The front radial bearing is placed at the front end of the rotor. The axial bearing is located between the front radial bearing and the motor stator 105. A deflector 1032 for guiding the cooling impeller and a rear end cover 1031 are assembled on the rear housing to increase the air flow conduction and reduce the flow resistance. Several corresponding ventilation holes or ventilation grooves are provided on parts such as the rear housing 1042, the cylinder, and the front housing 1041 to facilitate the air flow conduction. The cooling gas of the cooling impeller is divided into three paths through the flow channel on the rear housing 1042. The first path: through the axial cooling flow channel (not marked in the figure) in the cylinder → the axial bearing; the second path: through the motor stator flow channel on the cylinder → the axial bearing; the third path: through the motor rotor flow channel (i.e., the air gap between the motor stator and rotor) → the axial bearing; the three paths of cooling gas pass through the axial stator inner circulation channel holes and the magnetic poles or thrust disc ring grooves on the axial stator on both sides of the axial bearing and then are discharged from the bearing exhaust hole 11. This flow channel structure layout effectively cools the heat-generating components such as the stator, rotor, radial bearing, and axial bearing. At the same time, for the high-heat-generating components such as the thrust disc or the axial bearing stator, a ring groove structure is provided on the magnetic poles of the thrust disc or the axial bearing, and a flow channel hole is added to the inner ring of the axial bearing stator. At the high rotational speed of the rotor, the gas flow channel is increased, the cooling flow rate and speed are increased, and the cooling of the axial magnetic bearing and the thrust disc is accelerated. The entire heat dissipation system has a simple structure, an efficient and reliable heat dissipation process, and improves the stability of the magnetic levitation system.

[0052] Third Embodiment:

[0053] See Figure 6As shown in the figure, an active pure air-cooled heat dissipation system is adopted. The cold air is provided by the cooling impeller without an additional heat dissipation drive motor. The cooling impeller 103 is assembled at the rear end of the rotor. The rear radial bearing is located between the cooling impeller 103 and the motor stator 105. The front radial bearing is placed at the front end of the rotor. The axial bearing is located between the front radial bearing and the motor stator 105. A deflector 1032 for guiding the cooling impeller and a rear end cover 1031 are assembled on the rear housing to increase the air flow conduction and reduce the flow resistance. Several corresponding ventilation holes or ventilation grooves are provided on parts such as the rear housing 1042, the cylinder body, and the front housing 1041 to facilitate the air flow conduction. The cooling gas of the cooling impeller is divided into two paths for cooling when entering the motor rotor flow path. The first path: After cooling the motor stator through the motor stator flow path on the cylinder body, it is discharged through the exhaust hole 1061. The second path: After passing through the axial stator inner circulation channel hole → the magnetic pole or thrust disk ring groove on the axial stator, it converges with the main impeller leakage gas passing through the main impeller leakage flow path → the axial stator inner circulation channel hole and the magnetic pole or thrust disk ring groove on the axial stator and is discharged from the bearing exhaust hole 11. This flow path structure layout effectively cools the heating components such as the stator, rotor, radial bearing, and axial bearing. At the same time, for the high-heat components such as the thrust disk or the axial bearing stator, a ring groove structure is provided on the magnetic pole of the thrust disk or the axial bearing, and a flow channel hole is added to the inner ring of the axial bearing stator. At the high rotational speed of the rotor, the gas flow channel is increased, the cooling flow rate and speed are increased, and the cooling of the axial magnetic bearing and the thrust disk is accelerated. The entire heat dissipation system has a simple structure, an efficient and reliable heat dissipation process, and improves the stability of the magnetic levitation system.

[0054] Fourth Embodiment:

[0055] See Figure 7As shown, an active pure air-cooled heat dissipation system is adopted. The cold air is provided by the cooling impeller without an additional heat dissipation drive motor. The cooling impeller 103 is assembled at the rear end of the rotor. The rear radial bearing is located between the cooling impeller 103 and the motor stator 105. The front radial bearing is placed at the front end of the rotor. The axial bearing is located between the front radial bearing and the motor stator 105. A deflector 1032 for guiding the flow of the cooling impeller and a rear end cover 1031 are assembled on the rear housing to increase the air flow conduction and reduce the flow resistance. Moreover, several corresponding ventilation holes or ventilation grooves are provided on parts such as the rear housing 1042, the cylinder body, and the front housing 1041 to facilitate the air flow conduction. The cooling gas of the cooling impeller passes through the rear housing 1042, then through the motor stator flow channel and the motor rotor flow channel on the cylinder body, and then through the axial stator inner circulation channel hole and the right annular groove of the thrust disc or the magnetic pole on the stator, and then merges with the main impeller leakage gas passing through the main impeller leakage flow channel, the axial stator inner circulation channel hole, and the left annular groove of the thrust disc or the magnetic pole on the axial stator, and then is discharged from the bearing exhaust hole 11. This flow channel structure arrangement effectively cools the heating components such as the stator, the rotor, the radial bearing, and the axial bearing. At the same time, for the high-heating components such as the thrust disc or the axial bearing stator, an annular groove structure is provided on the upper magnetic pole of the thrust disc or the axial bearing, and a flow channel hole is added to the inner ring of the axial bearing stator. At the high rotational speed of the rotor, the gas flow channel is increased, the cooling flow rate and speed are increased, and the cooling of the axial magnetic bearing and the thrust disc is accelerated. The entire heat dissipation system has a simple structure, an efficient and reliable heat dissipation process, and improves the stability of the magnetic levitation system.

[0056] It is easy for those skilled in the art to understand that, on the premise of no conflict, the advantageous technical features of the above various methods can be freely combined and superimposed.

[0057] The above are only the preferred embodiments of the present invention and are not intended to limit the present invention. Any modifications, equivalent replacements, and improvements made within the spirit and principle of the present invention shall be included in the protection scope of the present invention. The above is only the preferred implementation manner of the present invention. It should be noted that for those of ordinary skill in the art, without departing from the technical principle of the present invention, several improvements and modifications can still be made, and these improvements and modifications should also be regarded as within the protection scope of the present invention.

Claims

1. An axial magnetic bearing, comprising an outer cylinder (1), wherein a first axial stator assembly (2), a second axial stator assembly (3) and a thrust plate (4) are assembled in a central through hole of the outer cylinder (1), wherein the first axial stator assembly (2) comprises a first stator core (21) and a first winding (22) assembled on the first stator core (21), and the second axial stator assembly (3) comprises a second stator core (31) and a second winding (32) assembled on the second stator core (31), and the thrust plate (4) is located between the magnetic poles of the first stator core (21) and the magnetic poles of the second stator core (31), and characterized in that: The magnetic poles of the first stator core (21) include a first outer magnetic pole (211) and a first inner magnetic pole (212); the magnetic poles of the second stator core (31) include a second outer magnetic pole (311) and a second inner magnetic pole (312); a first current ring groove (51) is formed on the surface area where the first outer magnetic pole (211) and the thrust plate (4) are opposite to each other; and a first current ring groove (51) is also formed on the surface area where the second outer magnetic pole (311) and the thrust plate (4) are opposite to each other. A flow ring groove (51) is provided, and the first flow ring groove (51) is coaxially arranged with the thrust plate (4), and winding cooling channels are formed in the first axial stator component (2) and the second axial stator component (3), and the winding cooling channels are used to cool the first winding (22) and the second winding (32), and the winding cooling channels respectively provided in the first axial stator component (2) and the second axial stator component (3) are connected via the first flow ring groove (51).

2. The axial magnetic bearing according to claim 1, characterized in that: The first flow ring groove (51) is formed on the magnetic end faces of the first outer magnetic pole (211) and the second outer magnetic pole (311), and any radial plane perpendicular to the axis of the thrust disk (4) is defined as a radial plane. When projected on the radial plane, the outer circular contour of the thrust disk (4) is within the groove width range of the first flow ring groove (51).

3. The axial magnetic bearing according to claim 2, characterized in that: A second flow ring groove (53) is also formed on the magnetic end faces of the first outer magnetic pole (211) and the second outer magnetic pole (311); the first flow ring groove (51) and the second flow ring groove (53) are arranged concentrically, and the first flow ring groove (51) is located radially outside the second flow ring groove (53).

4. The axial magnetic bearing according to claim 3, characterized in that: The first outer magnetic pole (211) includes a first cover plate portion (2111) extending radially inward along the thrust plate (4), the second outer magnetic pole (311) includes a second cover plate portion (3111) extending radially inward along the thrust plate (4), and the first flow ring groove (51) and the second flow ring groove (53) are formed on the first cover plate portion (2111) and the second cover plate portion (3111).

5. The axial magnetic bearing according to claim 4, characterized in that: The second flow annular groove (53) passes through the radial inner annular wall of the first cover plate portion (2111) or the second cover plate portion (3111).

6. The axial magnetic bearing according to claim 4, characterized in that: The first stator core (21) further comprises a first stator yoke (213) located between the first outer magnetic pole (211) and the first inner magnetic pole (212); the second stator core (31) further comprises a second stator yoke (313) located between the second outer magnetic pole (311) and the second inner magnetic pole (312); the first stator yoke (213) comprises a first outer protruding ring protruding from a radial outer ring wall of the first outer magnetic pole (211); and the second stator yoke (313) comprises a first outer protruding ring protruding from a radial outer ring wall of the second outer magnetic pole (311). A second outer convex ring of the radial outer ring wall, the first axial stator component (2) is assembled in the outer cylinder (1) via the first outer convex ring and the second axial stator component (3) is assembled in the outer cylinder (1) via the second outer convex ring to form a cooling cavity between the first outer magnetic pole (211) and the outer cylinder (1) and between the second outer magnetic pole (311) and the outer cylinder (1), and the first flow ring groove (51) of the first axial stator component (2) and the first flow ring groove (51) of the second axial stator component (3) are connected through the cooling cavity.

7. The axial magnetic bearing according to claim 6, characterized in that: The first stator yoke (213) is formed with a first through hole (2131) penetrating the inside and outside thereof, a first annular gap is formed between the radial inner circle of the first winding (22) and the radial outer annular wall of the first inner magnetic pole (212), a first flow gap is formed between the end surface of the first winding (22) away from the first cover plate (2111) and the inner end surface of the first stator yoke (213), and the first through hole (2131), the first flow gap and the first annular gap form the winding cooling flow channel of the first axial stator assembly (2); The second stator yoke (313) is provided with a second through hole (3131) penetrating the inner and outer sides thereof; a second annular gap is formed between the radial inner circle of the second winding (32) and the radial outer annular wall of the second inner magnetic pole (312); a second flow gap is formed between the end surface of the second winding (32) away from the second cover plate (3111) and the inner end surface of the second stator yoke (313); the second through hole (3131), the second flow gap and the second annular gap form the winding cooling channel of the second axial stator assembly (3).

8. The axial magnetic bearing according to claim 6, characterized in that: The outer cylinder (1) is provided with a bearing exhaust hole (11), and the bearing exhaust hole (11) is connected to the cooling cavity and the external space of the outer cylinder (1).

9. A magnetically suspended rotating machine, comprising a rotating shaft (100) and an axial magnetically suspended bearing (101) for limiting the axial displacement of the rotating shaft (100), characterized in that: The axial magnetic bearing (101) is an axial magnetic bearing according to any one of claims 1 to 8, the first end of the rotating shaft (100) is connected to the blower turbine (102), and the second end of the rotating shaft (100) is connected to the cooling impeller (103), and the cooling airflow introduced into the magnetically suspended rotating machinery by the cooling impeller (103) and / or part of the airflow at the blower turbine (102) can enter the axial magnetic bearing through the winding cooling channel and flow out of the axial magnetic bearing through the first flow ring groove (51).

10. The magnetic levitation rotating machine according to claim 9, characterized in that: It also includes a cylinder (106), in which a motor stator (105) capable of driving the rotating shaft (100) to rotate is assembled, and a stator cooling channel (1062) is formed in an area of ​​the cylinder (106) corresponding to the position of the motor stator (105).

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