Magnetic levitation compressor, air conditioner

Abstract

The present invention provides a magnetic levitation compressor and an air conditioner, wherein the magnetic levitation compressor includes: a rotating shaft; a magnetic levitation bearing, which is mounted on the radially outer side of the rotating shaft; the magnetic levitation bearing has a magnetic shell, and a storage space for accommodating a magnetic bearing assembly is formed in the magnetic shell. A cooling inlet and a cooling outlet are constructed on the magnetic shell, and both the cooling inlet and the cooling outlet are connected to the storage space so that a cooling medium is introduced into the storage space through the cooling inlet and then discharged through the cooling outlet. The present invention can introduce the cooling medium into the interior of the magnetic shell so that it is in full contact with the magnetic bearing assembly in the storage space, thereby achieving timely and efficient cooling of the heat inside the magnetic bearing, effectively reducing the temperature rise of the magnetic levitation bearing during operation. Compared with the prior art of introducing the cooling medium to the outer area of ​​the magnetic shell, the present invention has higher cooling efficiency and better temperature rise control effect.

Description

Technical Field

[0001] The invention belongs to the technical field of compressor design, and in particular relates to a magnetic suspension compressor and an air conditioner. Background Art

[0002] Magnetic bearings have a series of excellent qualities such as non-contact, wear-free, high speed, high precision, and no need for lubrication and sealing. They are high-tech products that integrate electromagnetism, electronic technology, control engineering, signal processing, and mechanics.

[0003] Magnetic bearings are categorized into three types: active, passive, and hybrid. Active magnetic bearings offer high stiffness and precision control, but require a large volume and consume a large amount of power to generate a specific unit of load capacity. Passive magnetic bearings utilize the attractive or repulsive forces between magnetic materials to levitate the rotor, resulting in relatively low stiffness and damping. Hybrid magnetic bearings use permanent magnets to provide a bias magnetic field, replacing the static bias magnetic field generated by electromagnets in active magnetic bearings. This reduces the ampere-turns of the control winding, shrinks the bearing size, and improves the bearing's load capacity. Hybrid magnetic bearings offer irreplaceable advantages in applications with strict requirements on volume and power consumption, and are primarily used in high- and ultra-high-speed applications. Therefore, key research areas will be the integration and miniaturization of magnetic levitation systems and improving the stability and reliability of control systems.

[0004] During the application process, the control winding of the magnetic bearing will generate a large amount of heat, so it needs to be cooled to reduce the temperature rise of the magnetic bearing and adjacent components and ensure the operational reliability of the components. In some related technologies, a high-pressure cooling airflow or refrigerant (coolant) is introduced to the position of the magnetic bearing to cool it. This cooling method allows a relatively small amount of cooling medium to enter the interior of the magnetic bearing, resulting in the internal heat of the magnetic bearing not being dissipated in time. In addition, in the technical solution of using refrigerant to cool the magnetic bearing, in order to improve the heat exchange efficiency of the refrigerant, it is often necessary to throttle the refrigerant before it is guided to the magnetic bearing position. The throttling component is designed separately on the refrigerant pipeline, making the structure of the cooling system relatively complex and not streamlined. Summary of the Invention

[0005] Therefore, the present invention provides a magnetic levitation compressor and an air conditioner, which can solve the technical problem in the prior art that the internal heat of the magnetic levitation bearing cannot be dissipated in time.

[0006] In order to solve the above problems, the present invention provides a magnetic levitation compressor, comprising:

[0007] shaft;

[0008] A magnetic bearing is mounted on the radial outer side of the rotating shaft. The magnetic bearing has a magnetic shell. A storage space for accommodating the magnetic bearing assembly is formed in the magnetic shell. A cooling inlet and a cooling outlet are constructed on the magnetic shell. Both the cooling inlet and the cooling outlet are connected to the storage space so that the cooling medium is introduced into the storage space through the cooling inlet and then discharged through the cooling outlet.

[0009] In some embodiments, the magnetic levitation compressor further comprises:

[0010] A compressor housing is provided with a cooling channel therein, the magnetic bearing includes a first bearing and a second bearing, the first bearing and the second bearing are respectively supported at the two end areas of the rotating shaft, the cooling channel has a first outlet connected to the cooling inlet of the first bearing, and a second outlet connected to the cooling inlet of the second bearing, the cooling channel also has a medium inlet connected to the cooling medium supply component, and the compressor housing is also provided with a reflux port allowing the cooling medium to reflux.

[0011] In some embodiments,

[0012] The compressor housing has a hollow cavity, the cooling outlet of the magnetic bearing is located close to the hollow cavity and communicated with the hollow cavity, and the cooling inlet is located away from the hollow cavity.

[0013] In some embodiments,

[0014] The cooling medium is a refrigerant, and a throttling hole is further configured on the magnetic shell. The first outlet or the second outlet is connected to the throttling hole, and the refrigerant throttled through the throttling hole enters the accommodating space through the cooling inlet.

[0015] In some embodiments,

[0016] There are multiple cooling inlets and / or cooling outlets, and the multiple cooling inlets and / or cooling outlets are arranged at intervals around the rotating shaft.

[0017] In some embodiments,

[0018] When the compressor casing has a hollow cavity, a closed cover is provided at the end of the compressor casing, the closed cover is connected to the side of the magnetic bearing away from the hollow cavity, and the cooling inlet and the outlet of the throttle hole are both located in the cover space of the closed cover.

[0019] In some embodiments,

[0020] A sensor connected to a side of the magnetic shell away from the hollow cavity is also provided in the housing space.

[0021] In some embodiments,

[0022] A flow channel is formed between the sensor and the mating surface of the connection area of ​​the magnetic conductive shell.

[0023] In some embodiments,

[0024] A protective bearing is provided on the radial inner side of the magnetic conductive shell, and the outlet of the flow passage is adapted to the position of the protective bearing.

[0025] In some embodiments,

[0026] The first bearing is an axial-radial composite bearing, and the second bearing is a radial bearing.

[0027] The present invention also provides an air conditioner, comprising the above-mentioned magnetic levitation compressor.

[0028] The present invention provides a magnetic levitation compressor and air conditioner. By constructing the aforementioned cooling inlet and cooling outlet on the magnetic shell, the cooling medium can be introduced into the interior of the magnetic shell and fully contacted with the magnetic bearing assembly in the accommodating space, thereby achieving timely and efficient cooling of the heat inside the magnetic bearing, effectively reducing the temperature rise of the magnetic levitation bearing during operation. Compared with the prior art of introducing the cooling medium to the outer area of ​​the magnetic shell, the present invention has higher cooling efficiency and better temperature rise control effect; the refrigerant flowing into the accommodating space can be throttled by phase change through the setting of the throttle hole, so that at least part of the liquid refrigerant is phase-changed into gaseous refrigerant, so that the refrigerant flowing into the accommodating space can undergo phase change after absorbing heat, thereby improving the cooling effect of the refrigerant on the magnetic bearing assembly; the throttle hole is directly constructed on the magnetic shell, and there is no need to separately configure a corresponding throttling element on the refrigerant pipeline, so that the system design is further simplified and the product manufacturing cost is saved. BRIEF DESCRIPTION OF THE DRAWINGS

[0029] Figure 1 Schematic diagram of the internal structure of a magnetic levitation compressor in an embodiment of the present invention (some components are omitted, such as the sealing covers and volute structures at both ends of the compressor housing). The magnetic levitation compressor shown in the figure is a two-stage refrigerant compressor;

[0030] Figure 2 Schematic diagram of the internal structure of the first bearing after being assembled with related components in an embodiment of the present invention;

[0031] Figure 3 for Figure 2 Schematic diagram of the disassembled structure of the first bearing (partial cross-section);

[0032] Figure 4 Schematic diagram of the internal structure of the first bearing in another embodiment of the present invention, in which a protective bearing is provided at the front iron core and the rear iron core respectively;

[0033] Figure 5 for Figure 4 Schematic diagram of the magnetic circuit flow direction of the first bearing in (axial cross section);

[0034] Figure 6 for Figure 5 A partial enlarged view of point A in the middle;

[0035] Figure 7 for Figure 4 Schematic diagram of the magnetic circuit flow direction of the first bearing in FIG (radial plane projection);

[0036] Figure 8 Schematic diagram of the internal structure of the first bearing in another embodiment of the present invention, in which two protective bearings are provided at the rear core;

[0037] Figure 9 Schematic diagram of the internal structure of the second bearing in an embodiment of the present invention;

[0038] Figure 10 for Figure 9 Schematic diagram of the disassembled structure of the second bearing (partial cross-section);

[0039] Figure 11 Schematic diagram of the first structure of the bearing rotor in an embodiment of the present invention;

[0040] Figure 12 Schematic diagram of the second structure of the bearing rotor in an embodiment of the present invention;

[0041] Figure 13 Schematic diagram of the third structure of the bearing rotor in the embodiment of the present invention;

[0042] Figure 14 Schematic diagram of the fourth structure of the bearing rotor in the embodiment of the present invention;

[0043] Figure 15 Schematic diagram of a fifth structure of a bearing rotor in an embodiment of the present invention;

[0044] Figure 16 Schematic diagram of the sixth structure of the bearing rotor in an embodiment of the present invention;

[0045] Figure 17 Schematic diagram of the seventh structure of the bearing rotor in the embodiment of the present invention.

[0046] The reference numerals indicate:

[0047] 11. Cooling inlet; 12. Cooling outlet; 21. First bearing; 22. Second bearing; 3. Throttle hole; 4. Flow passage; 5. Protective bearing; 51. Bearing gland;

[0048] 101, rotating shaft; 103, compressor housing; 1031, cooling channel; 1032, medium inlet; 1033, return port; 1041, motor stator; 1051, first impeller; 1052, second impeller; 1061, first sensor; 1062, second sensor; 1063, sensor mounting base; 107, gasket; 108, balancing plate;

[0049] 913, bearing rotor collar; 915, bearing rotor front baffle; 916, front iron core; 917, rear iron core; 918, permanent magnet; 919, magnetic ring; 920, positioning ring; 921, axial coil winding bobbin; 9211, female socket; 9212, male socket; 922, axial winding; 923, radial stator core; 924, radial winding; 925, radial rotor laminations; 927, thrust plate; 928, bearing rotor rear baffle; 933, locking nut; 935, bearing inner positioning ring;

[0050] 81. Radial bearing housing; 82. Radial bearing assembly. DETAILED DESCRIPTION

[0051] To make the objectives, technical solutions, and advantages of the present invention more clear, the technical solutions of the present invention will be clearly and completely described below in conjunction with specific embodiments of the present invention and corresponding drawings. Obviously, the embodiments described are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by ordinary technicians in this field without making creative efforts are within the scope of protection of the present invention.

[0052] It should be noted that the terms "first," "second," and the like in the specification and claims of the present invention and the accompanying drawings are used to distinguish similar objects and are not necessarily used to describe a specific order or precedence. It should be understood that the terms used in this manner are interchangeable where appropriate, such that the embodiments of the present invention described herein can be practiced in orders other than those illustrated or described herein.

[0053] See also Figure 1 and Figure 17 As shown, according to an embodiment of the present invention, a magnetic levitation compressor is provided, comprising:

[0054] The shaft 101 is connected to an impeller at at least one end thereof, and radial rotor laminations 925 are mounted on the shaft body of the shaft 101. Figure 1As shown, taking a two-stage compressor as an example, an impeller is connected to each end of the rotating shaft 101, namely a first impeller 1051 and a second impeller 1052. The two impellers are respectively located in corresponding volutes (not shown in the figure), and the fluid discharge port of one is connected to the fluid intake port of the other, so as to achieve the purpose of two-stage compression;

[0055] The magnetic levitation bearing is mounted on the radial outer side of the rotating shaft 101 to suspend the rotating shaft 101 at a preset position through magnetic force. The magnetic levitation bearing has a magnetic shell, and a accommodating space (not labeled in the figure) for accommodating a magnetic bearing assembly (not labeled in the figure) is formed in the magnetic shell. A cooling inlet 11 and a cooling outlet 12 are constructed on the magnetic shell. The cooling inlet 11 and the cooling outlet 12 are both connected to the accommodating space to introduce the cooling medium into the accommodating space through the cooling inlet 11 and then discharge it through the cooling outlet 12.

[0056] In this technical solution, by constructing the aforementioned cooling inlet 11 and cooling outlet 12 on the magnetic shell, the cooling medium can be introduced into the interior of the magnetic shell and fully contacted with the magnetic bearing assembly in the accommodating space, thereby achieving timely and efficient cooling of the internal heat of the magnetic bearing, effectively reducing the temperature rise of the magnetic levitation bearing during operation. Compared with the prior art of introducing the cooling medium to the outer area of ​​the magnetic shell, the present invention has higher cooling efficiency and better temperature rise control effect.

[0057] In a specific embodiment, the connection between the cooling inlet 11 and the accommodating space is located on a side of the magnetic bearing assembly away from the air gap formed between the magnetic bearing assembly and the rotating shaft 101, that is, on a radially outward side of the magnetic bearing assembly. The aforementioned magnetic bearing assembly can specifically be the stator core of the magnetic suspension bearing and its corresponding housing components, such as the control winding and permanent magnets wound thereon.

[0058] See further Figure 1 As shown, the first impeller 1051 and the second impeller 1052 are respectively sleeved on the two axial ends of the rotating shaft 101, and the reliable connection between the two impellers is effectively achieved by arranging corresponding gaskets 107.

[0059] It can be understood that the magnetic levitation compressor also includes: a compressor housing 103, which is used as the main assembly space for motor components such as the motor stator 1041 and the rotating shaft 101, forming a relatively closed cavity. In some embodiments, a cooling flow channel 1031 is constructed in the compressor housing 103, and the magnetic levitation bearing includes a first bearing 21 and a second bearing 22. The first bearing 21 and the second bearing 22 are respectively supported at the two end areas of the rotating shaft 101 to Figure 1Based on the orientation shown, the first bearing 21 is at the right end position of the rotating shaft 101, and the second bearing 22 is at the left end position of the rotating shaft 101. The cooling channel 1031 has a first outlet connected to the cooling inlet 11 of the first bearing 21, and a second outlet connected to the cooling inlet 11 of the second bearing 22. The cooling channel 1031 also has a medium inlet 1032 connected to the cooling medium supply component. The compressor housing 103 is also constructed with a return port 1033 that allows the cooling medium to flow back.

[0060] like Figure 1 As shown in , cooling channel 1031 includes a first channel segment 6b corresponding to the cooling inlet 11 of the first bearing 21 and a second channel segment 6a corresponding to the cooling inlet 11 of the second bearing 22. In this technical solution, cooling channel 1031 is used to separate the cooling flow at the two bearing positions, simplifying the design of the cooling pipeline. In specific applications, the outlet of the cooling medium supply component is connected to the medium inlet 1032, and the inlet of the cooling medium supply component can be connected to the return port 1033, thereby forming a cooling cycle for the cooling medium and achieving efficient cooling of the cooling medium.

[0061] The compressor housing 103 has a hollow cavity, within which a motor stator 1041 is mounted. This stator 1041 is mounted radially outwardly of the radial rotor laminations 925. An alternating magnetic field between the stator and the rotor laminations converts external electrical energy into rotational kinetic energy for the shaft 101. The cooling outlet 12 of the magnetic bearing is located near and connected to the hollow cavity, while the cooling inlet 11 is located away from the cavity. It should be noted that the radial rotor laminations 925 can reduce eddy current losses within them.

[0062] See also Figure 1 As shown, in this technical solution, the cooling inlet 11 is arranged on a side away from the hollow cavity, and the cooling outlet 12 is connected to the hollow cavity, so that the cooling medium can be discharged into the hollow cavity after heat exchange inside the magnetic bearing and further contact and exchange heat with the motor stator 1041, the rotating shaft 101 and the radial rotor laminations 925 therein, thereby reducing the temperature rise inside the compressor.

[0063] The aforementioned cooling medium can be reasonably selected according to the operating conditions, for example, it can be compressed cooling gas, lubricating oil, etc. In a more preferred embodiment, the cooling medium is refrigerant, and a throttling hole 3 is also constructed on the magnetic shell. The first outlet or the second outlet is connected to the throttling hole 3, and the refrigerant throttled through the throttling hole 3 enters the accommodating space through the cooling inlet 11. It can be understood that the aperture of the aforementioned throttling hole 3 should be smaller than the flow channel aperture at the upstream position in the refrigerant flow direction, so that the refrigerant flowing into it can be throttled by phase change.

[0064] In this technical solution, the throttle hole 3 is provided to throttle the refrigerant flowing into the accommodating space by phase change, so that at least part of the liquid refrigerant is phase-changed into a gaseous refrigerant, so that the refrigerant flowing into the accommodating space can undergo a phase change after absorbing heat, thereby improving the cooling effect of the refrigerant on the magnetic bearing assembly. It should be noted that, in this technical solution, the throttle hole 3 is directly constructed on the magnetic shell, and there is no need to separately configure a corresponding throttling element on the refrigerant pipeline, which further simplifies the system design and saves product manufacturing costs.

[0065] When the cooling medium is a refrigerant, the aforementioned cooling medium supply component can specifically be a refrigeration system cycle of an air conditioner. At this time, it can be specifically designed that the medium inlet 1032 is connected to the liquid outlet pipe of the condenser, and the return port 1033 is connected to the air intake of the compressor (for example, the first-stage air intake).

[0066] In some embodiments, there are multiple cooling inlets 11 and / or cooling outlets 12 , and the multiple cooling inlets 11 and / or cooling outlets 12 are arranged at intervals around the rotating shaft 101 .

[0067] In this technical solution, the cooling inlet 11 and the cooling outlet 12 are arranged at circumferential intervals on the annular rotating shaft 101, which can ensure sufficient contact and balanced heat exchange cooling of the refrigerant on the components in the accommodating space, further improving the cooling effect.

[0068] In a preferred embodiment, a closed cover (not shown in the figure) is provided at the end of the compressor casing 103, which is connected to the side of the magnetic bearing away from the hollow cavity, and the cooling inlet 11 and the outlet of the throttle hole 3 are both located in the cover space of the closed cover.

[0069] In this technical solution, the sealed cover space formed by the aforementioned closed cover objectively forms a temporary storage for the refrigerant flowing out of the throttle hole 3 and evenly distributes the refrigerant to multiple cooling inlets 11, and each throttle hole 3 at each magnetic levitation bearing only needs to be provided with one corresponding to the cooling channel 1031.

[0070] See also Figure 1As shown, in a preferred embodiment, a sensor connected to the side of the magnetic shell away from the hollow cavity is further provided in the housing space. For different magnetic bearings, the aforementioned sensors may be the same or different. Specifically, in a specific embodiment, the sensor includes a first sensor 1061 corresponding to the first bearing 21 and a second sensor 1062 corresponding to the second bearing 22. The first sensor 1061 and the second sensor 1062 are respectively used for real-time detection of the radial and / or axial displacement of the area adjacent to the rotating shaft 101, so as to be able to feed back the corresponding displacement signal to the control component of the magnetic levitation compressor. The control component can control the first bearing 21 and the second bearing 22 according to the obtained displacement signal to adjust the radial and axial position of the rotating shaft 101. See further. Figure 1 As shown, a balancing disk 108 is mounted on the rotating shaft 101 between the first sensor 1061 and the first impeller 1051 .

[0071] It should be noted that, in this technical solution, the sensor is arranged in the cover space, and the refrigerant after throttling phase change can be used to effectively cool it down, thereby ensuring the operational reliability of the sensor.

[0072] See also Figure 2 As shown, in this technical solution, the first sensor 1061 is connected to the magnetic shell through the corresponding sensor mounting base 1063. In another feasible embodiment, see Figure 9 As shown, the second sensor 1062 may also be directly connected to the magnetically conductive housing.

[0073] In another feasible embodiment, a flow channel 4 is formed between the connecting area matching surface of the sensor and the magnetic conductive shell, such as Figure 9 As shown, a plurality of grooves extending radially thereof are provided on the side surface of the magnetic shell away from the hollow cavity, and the second sensor 1062 is connected to the side surface, and the aforementioned flow channel 4 is formed between the two. The flow channel 4 guides the refrigerant throttled by the throttle hole 3 to the corresponding cooling inlets 11 to enter the accommodating space, thereby further simplifying the structural design while achieving efficient cooling of the sensor.

[0074] In some embodiments, a protective bearing 5 is provided on the radial inner side of the magnetic shell to provide physical protection for the magnetic shell after the rotating shaft 101 becomes unstable during operation, thereby preventing damage to the magnetic bearing. It can be understood that the radial clearance and axial clearance between the aforementioned protective bearing 5 and the rotating shaft 101 should both be smaller than the radial clearance or axial clearance of the corresponding magnetic bearing. As a preferred embodiment, the outlet of the flow channel 4 is adapted to the position of the protective bearing 5. The aforementioned adaptation means that the refrigerant flowing out of the outlet of the flow channel 4 can flow directly to the position of the protective bearing 5, so that the protective bearing 5 can be cooled in time.

[0075] The following combination Figure 1 、 Figure 2 as well as Figure 9 The cooling flow direction of the cooling medium in the present invention is further explained:

[0076] For the second bearing 22, the cooling fluid flows to the second bearing 22 through the 6-a section of the cooling flow channel 1031 on the compressor housing 103, and in the flow channel 5-a ( Figure 9 The throttling phase changes at the throttling hole 3 indicated by (in the middle), and the cooling fluid can be distributed to the periphery of the sensor at 5-b. Four cooling features 5-c (i.e., cooling inlets 11) are provided on the radial bearing housing 81. When the refrigerant flows through the radial bearing housing 81, it can cool the sensor and the radial bearing assembly 82. It can also be distributed around 5-d, so that it can cool both the sensor and the electromagnetic bearing winding. Finally, it passes through the stator slot 5-e (in the middle). Figure 1 This structure can be reflected in the figure), the gap 5-f flows to the internal motor components.

[0077] For the first bearing 21, the cooling fluid undergoes a throttling phase change through the throttling hole 3 (the position indicated by 9-a) on the rear core 917. At 9-b, the cooling fluid can be distributed to the periphery of the rear core 917. Four or more cooling holes and cooling grooves 9-g are provided on the rear core 917, which allow the cooling fluid to pass smoothly to cool the radial winding 924 and the axial winding 922. At the flow channels 9-b, 9-h, 9-e, and 9-f, the cooling fluid can flow axially and cool in one direction. This cooling scheme design allows the refrigerant to flow through the parts that need to be cooled in the flow channel in turn, fully contacting with the windings, cores and other parts, and fully cooling them. In the three-degree-of-freedom radial and axial integrated cooling scheme, the refrigerant flows through the radial coils and axial coils in the three-degree-of-freedom bearing at the same time, achieving the purpose of cooling the radial and axial directions at the same time.

[0078] After entering the compressor, the refrigerant is split at 6-a and 6-b, cooling the first bearing 21 and the second bearing 22 at the same time. After cooling, it flows out from 6-c. The compressor has a simple appearance and structure, and there is only one inlet and outlet for bearing cooling.

[0079] In some embodiments, the first bearing 21 is a composite axial-radial bearing, and the second bearing 22 is a radial bearing. This composite axial-radial bearing allows the prior art axial magnetic bearing and radial magnetic bearing to be integrated into one, shortening the rotor's axial dimension, thereby increasing the rotor's maximum speed and broadening the compressor's operating range. In this case, the first sensor 1061 has both radial and axial detection capabilities.

[0080] The following combination Figures 2 to 8 The specific structure of the first bearing 21 in the present invention will be further described. It can be understood that the first bearing 21 in the present invention is a composite bearing with three degrees of freedom in the axial and radial directions.

[0081] by Figure 3 Taking an embodiment shown as an example, the radial winding 924 is embedded in the radial stator core 923 to form a radial bearing assembly, and the axial coil winding frame 921 with the coil wound is placed on both sides of the radial bearing assembly and is at the outside of the radial winding 924 (that is, the radial outside). The axial coil winding frames 921 on both sides are provided with a male seat 9212 and a female seat 9211 that cooperate with each other. The male seat 9212 and the female seat 9211 are plugged into each other to achieve interference fit or gluing connection between the two. The magnetic ring 919 and the rear core 917 form an assembly, and the magnetic ring 919 is sleeved on the outside of the radial stator core 923. However, this is not limited to interference fit and gluing. The entire assembly is formed, with the inner diameter of the positioning ring 920 matingly connected to the outer side of the magnetic ring 919, providing radial centering and positioning. The inner diameter of the positioning ring 920 also mates with the axial end face of the magnetic ring 919, providing axial positioning. The permanent magnet 918 is placed between the magnetic ring 919 and the rear core 917. The rear core 917, permanent magnet 918, magnetic ring 919, positioning ring 920, axial coil bobbin 921, axial winding 922, radial stator core 923, and radial winding 924 form a three-degree-of-freedom axial-radial composite magnetic bearing. Regarding the first bearing 21, the front core 916 and rear core 917 are assembled together to form the aforementioned magnetic housing.

[0082] See also Figures 4 to 6As shown, there is a radial electromagnetic gap (g1) between the radial stator core 923 and the radial rotor lamination 925, an axial electromagnetic gap (g2) between the front core 916 and the bearing rotor front baffle 915, an axial electromagnetic gap g3 (not shown in the figure) between the rear core 917 and the bearing rotor rear baffle 928, an axial protective gap (g4) between the protective bearing 5 connected to the radial inner side of the front core 916 and the front end face of the thrust plate 927, and an axial protective gap g5 (not shown in the figure) between the protective bearing 5 connected to the radial inner side of the rear core 917 and the rear end face of the thrust plate 927. The gap values ​​g2>g4 and g3>g5 can have a protective effect. There is a radial protective gap g6 between the protective bearing 5 and the thrust plate 927 (rotating shaft 101), and the protective gap value g1>g6.

[0083] The axial bearing control logic of the first bearing 21 is as follows: Figure 5 As shown, and reference Figure 5 In the view orientation, the front axial permanent magnetic circuit (9-29-1) and the axial control magnetic circuit (9-30), when the sensor detects that the axial air gap g2>g3, the controller controls the direction of the current in the bearing to superimpose the axial control magnetic circuit (9-30) and the front axial permanent magnetic circuit (9-29-1), and the bearing front side bearing output Ff (front bearing output)>Fr (rear bearing output), and the thrust plate 927 assembly moves to the left. Similarly, when the sensor detects that the axial air gap g2<g3, the controller controls the direction of the current in the bearing to change, and the thrust plate 927 can be moved to the right. The radial control strategy is the same as the axial control strategy and can be combined Figure 7 The directions of the magnetic circuits shown are adjusted, which will not be described here. 9-31 in the figure refers to the radial control magnetic circuit.

[0084] In the first bearing 21 of this technical solution, the radial permanent magnetic circuit and the axial permanent magnetic circuit are generated by a single permanent magnet 918. The protective bearing 5 can be a deep groove ball bearing or an angular contact ball bearing (used in pairs), providing both radial and axial protection. Angular contact bearings are generally used in pairs and are typically made of steel, ceramic, or hybrid ceramic. The outer ring of the protective bearing 5 is radially interference-fitted with the front iron core 916 and the rear iron core 917 to limit axial movement of the outer ring of the protective bearing 5, or other limiting methods are employed, such as gluing or clamping with a bearing clamp.

[0085] Specifically, the specific installation method of the aforementioned protective bearing 5 can also be various, such as Figure 1 As shown in FIG, the first bearing 21 and the second bearing 22 are each equipped with only one protective bearing 5, wherein a bearing cover 51 is used to limit the axial position of the protective bearing 5; and Figure 4The first bearing 21 in the embodiment is provided with a protective bearing 5 on the radial inner side of the front iron core 916 and the rear iron core 917, thereby achieving more comprehensive protection; Figure 8 The figure shows a form in which two protective bearings 5 ​​are arranged on one side of the bearing at the same time. A corresponding bearing pressure cover 51 is provided on the side of the protective bearing 5 away from the magnetic shell to limit the outer ring of the bearing, and an inner positioning ring 935 of the bearing is used to limit the inner ring of the protective bearing 5, which is connected to the rotating shaft 101 as a whole through a locking nut 933.

[0086] Figures 11 to 17 Schematic diagrams of the structures of several bearing rotors in the embodiments of the present invention are given in FIG.

[0087] According to an embodiment of the present invention, there is further provided an air conditioner comprising the above-mentioned magnetic levitation compressor.

[0088] Throughout this specification, reference to terms such as "one embodiment," "some embodiments," "illustrative embodiments," "examples," "specific examples," or "some examples" means that a specific feature, structure, material, or characteristic described in conjunction with that embodiment or example is included in at least one embodiment or example of the present invention. In this specification, illustrative uses of the above terms do not necessarily refer to the same embodiment or example. Furthermore, the specific features, structures, materials, or characteristics described may be combined in any suitable manner in any one or more embodiments or examples.

[0089] While embodiments of the present invention have been shown and described, it will be appreciated by those skilled in the art that various changes, modifications, substitutions, and variations may be made to the embodiments without departing from the principles and spirit of the invention, and that the scope of the invention is defined by the claims and their equivalents.

Claims

1. A magnetic levitation compressor, characterized in that: include: shaft (101); A magnetic bearing is mounted on the radial outer side of the rotating shaft (101), the magnetic bearing having a magnetic shell, a housing space for accommodating a magnetic bearing assembly formed in the magnetic shell, a cooling inlet (11) and a cooling outlet (12) configured on the magnetic shell, the cooling inlet (11) and the cooling outlet (12) both being in communication with the housing space so that a cooling medium is introduced into the housing space via the cooling inlet (11) and then discharged via the cooling outlet (12); further comprising a compressor housing (103), a cooling channel (1031) configured in the compressor housing (103), the magnetic bearing comprising a first bearing (21) and a second bearing (22), the first bearing (21) and the second bearing (22) being supported at both end regions of the rotating shaft (101), the cooling channel (1031) having the same cooling inlet as the first bearing (21). (11) is connected to the first outlet of the magnetic bearing and the second outlet is connected to the cooling inlet (11) of the second bearing (22), and the compressor housing (103) has a hollow cavity; the cooling medium is a refrigerant, and a throttling hole (3) is also constructed on the magnetic shell, the first outlet or the second outlet is connected to the throttling hole (3), and the refrigerant throttled through the throttling hole (3) enters the accommodating space through the cooling inlet (11); the end of the compressor housing (103) is provided with a closed cover, the closed cover is connected to the side of the magnetic bearing away from the hollow cavity, and the cooling inlet (11) and the outlet of the throttling hole (3) are both located in the cover space of the closed cover; the cover space is also provided with a sensor connected to the side of the magnetic shell away from the hollow cavity; an overflow channel (4) is formed between the mating surface of the connection area of ​​the sensor and the magnetic shell.

2. The magnetic levitation compressor according to claim 1, characterized in that: The cooling channel (1031) further comprises a medium inlet (1032) connected to a cooling medium supply component, and the compressor housing (103) is further provided with a return port (1033) for allowing the cooling medium to return.

3. The magnetic levitation compressor according to claim 2, characterized in that: The cooling outlet (12) of the magnetic suspension bearing is located close to the side of the hollow cavity and is in communication with the hollow cavity, and the cooling inlet (11) is located away from the side of the hollow cavity.

4. The magnetic levitation compressor according to claim 1, characterized in that: There are multiple cooling inlets (11) and / or cooling outlets (12), and the multiple cooling inlets (11) and / or cooling outlets (12) are arranged at intervals around the rotating shaft (101).

5. The magnetic levitation compressor according to claim 1, characterized in that: A protective bearing (5) is provided on the radial inner side of the magnetic conductive housing, and the outlet of the flow passage (4) is adapted to the position of the protective bearing (5).

6. The magnetic levitation compressor according to claim 2, characterized in that: The first bearing (21) is an axial-radial composite bearing, and the second bearing (22) is a radial bearing.

7. An air conditioner, characterized in that: The magnetic levitation compressor comprises the magnetic levitation compressor according to any one of claims 1 to 6.

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