Magnetic levitation centrifugal compressor

Abstract

This application discloses a magnetically levitated centrifugal compressor, relating to the field of compressor technology. The magnetically levitated centrifugal compressor includes a drive assembly, an impeller, and an axial force balancing component. The drive assembly includes a drive shaft and a motor, with the drive shaft connected to the output end of the motor. The impeller is sleeved on the drive shaft. The axial force balancing component is located between the impeller and the motor, and has a main body, multiple first comb teeth, and multiple second comb teeth. The main body has a connecting hole and is sleeved on the drive shaft through the connecting hole. The wall of the connecting hole is spaced apart from the drive shaft, and the main body is spaced apart from the impeller. The multiple first comb teeth are spaced apart on the main body and positioned between the main body and the impeller. The multiple second comb teeth are spaced apart along the axial direction of the drive shaft, connected to the wall of the connecting hole, and all protrude from the wall of the connecting hole, and are spaced apart from the drive shaft. The magnetically levitated centrifugal compressor of this application can optimize the axial force balancing method of the impeller.

Description

Technical Field

[0001] This utility model relates to the field of compressor technology, and more specifically, to a magnetic levitation centrifugal compressor. Background Technology

[0002] The core feature of magnetic levitation centrifugal compressors is the use of magnetic bearings to achieve contactless rotor levitation, thereby significantly reducing mechanical losses and vibration noise. During operation, uneven gas pressure on both sides of the impeller generates axial thrust, a problem particularly prominent in high-speed centrifugal compressors. Traditional axial force balancing mainly relies on three methods: direct load bearing, counter-thrust generated by a balancing piston (or balancing disc), and drawing high-pressure gas to the low-pressure area through external pipelines. All these methods have limitations: thrust bearings increase friction, violating the frictionless principle of magnetic levitation; balancing pistons require additional axial space, making the structure bulky; and external balancing pipelines are not only costly but also pose risks due to leaks or blockages. Utility Model Content

[0003] In view of this, the purpose of this application is to overcome the shortcomings of the prior art and provide a magnetic levitation centrifugal compressor that can optimize the axial force balance of the impeller.

[0004] To achieve the above objectives, the technical solution adopted in this application is as follows: This application provides a magnetically levitated centrifugal compressor, comprising: a drive assembly including a drive shaft and a motor, the drive shaft being connected to the output end of the motor; an impeller sleeved on the drive shaft; and an axial force balancing component located between the impeller and the motor, the axial force balancing component having a main body, a plurality of first comb teeth, and a plurality of second comb teeth; the main body having a connecting hole and being sleeved on the drive shaft through the connecting hole, the wall of the connecting hole being spaced apart from the drive shaft, and the main body being spaced apart from the impeller; the plurality of first comb teeth being spaced apart on the main body, positioned between the main body and the impeller; and the plurality of second comb teeth being spaced apart along the axial direction of the drive shaft, connected to the wall of the connecting hole, and all protruding from the wall of the connecting hole, and all spaced apart from the drive shaft.

[0005] In an optional embodiment, the impeller has a wheel body portion sleeved on the drive shaft, the main body portion and the wheel body portion are spaced apart, a plurality of first comb teeth portions are disposed between the main body portion and the wheel body portion, and a plurality of second comb teeth portions are disposed between the wheel body portion and the drive shaft.

[0006] In an optional embodiment, a plurality of first comb teeth are radially spaced on the main body along the drive shaft, and the impeller also has a plurality of third comb teeth, which are radially spaced on the side of the wheel body near the main body along the drive shaft, and the plurality of third comb teeth are staggered with the plurality of first comb teeth.

[0007] In an optional implementation, the tooth pitch between any two adjacent first comb teeth is greater than the tooth width of any third comb tooth; and the tooth pitch between any two adjacent third comb teeth is greater than the tooth width of any first comb tooth.

[0008] In an optional embodiment, each of the first comb teeth is arranged parallel to the axial direction along the drive shaft.

[0009] In an optional embodiment, each of the first comb teeth is inclined relative to the axial direction of the drive shaft, and each of the third comb teeth is inclined relative to the axial direction of the drive shaft, and the inclination direction of the third comb teeth is the same as that of the first comb teeth.

[0010] In an optional embodiment, the impeller further includes a protrusion disposed on the side of the wheel body portion near the main body portion and protruding from the wheel body portion along the axial direction of the drive shaft. The protrusion and the drive shaft are radially spaced apart. The axial force balancer is at least partially disposed between the protrusion and the drive shaft, and a plurality of first comb teeth portions are located between the protrusion and the main body portion.

[0011] In an optional embodiment, a plurality of first comb teeth are spaced apart along the axial direction of the drive shaft, and each first comb tooth is angled to the axial direction of the drive shaft, and each first comb tooth is spaced apart from the protrusion.

[0012] In an optional embodiment, the impeller further has a plurality of fourth comb teeth, which are spaced apart on the protrusion along the axial direction of the drive shaft and are all spaced apart from the main body. The plurality of fourth comb teeth are staggered with the plurality of first comb teeth.

[0013] In an optional implementation, the tooth pitch between any two adjacent first comb teeth is greater than the tooth width of any fourth comb tooth; and the tooth pitch between any two adjacent fourth comb teeth is greater than the tooth width of any first comb tooth.

[0014] The magnetically levitated centrifugal compressor of this application has the following advantages: In the magnetic levitation centrifugal compressor of this application, since the drive shaft is connected to the output end of the motor and the impeller is mounted on the drive shaft, the impeller can be driven to rotate by the motor. During the rotation of the impeller, the side of the impeller closest to the motor is subjected to high-pressure airflow, causing the impeller to displace away from the motor under the action of axial force. Since the axial force balancing component is disposed between the impeller and the motor, and the main body of the axial force balancing component is spaced apart from both the drive shaft and the impeller, an airflow channel can be defined between the axial force balancing component and the impeller by the main body, so that the high-pressure airflow can flow from the outlet end of the impeller towards the motor through the airflow channel. Because multiple first comb teeth are disposed between the main body and the impeller, when the high-pressure airflow flows in the airflow channel between the impeller and the main body, the high-pressure airflow will flow through the multiple first comb teeth. When the high-pressure airflow flows through the multiple first comb teeth, the multiple first comb teeth will create resistance to the flow of the high-pressure airflow, thereby reducing the flow velocity of the high-pressure airflow and thus reducing the pressure of the high-pressure airflow. At the same time, because multiple second comb teeth are spaced apart along the axial direction of the drive shaft between the drive shaft and the main body, when the high-pressure airflow flows in the airflow channel between the drive shaft and the main body, the multiple second comb teeth will create resistance to the flow of the high-pressure airflow, thereby further reducing the flow velocity of the high-pressure airflow and thus further reducing the pressure of the high-pressure airflow. In this way, the high-pressure airflow on the side of the impeller closer to the motor can be depressurized by the axial force balancing component, thereby reducing the pressure difference on both sides of the impeller along the axial direction of the drive shaft, thereby balancing the axial force of the impeller, without increasing the friction between the impeller and the drive shaft, reducing the possibility of rubbing between the impeller and the drive shaft. Meanwhile, the cooperation of multiple first comb teeth and multiple second comb teeth can form a labyrinth sealing tooth structure to improve the sealing effect on the medium and reduce media leakage. Therefore, the magnetic levitation centrifugal compressor of this application can achieve axial force balance without additional complex balancing devices, and can also reduce the possibility of friction between the impeller and the drive shaft, and reduce media leakage. Attached Figure Description

[0015] To more clearly illustrate the technical solutions of the embodiments of this application, the accompanying drawings used in the embodiments will be briefly introduced below. It should be understood that the following drawings only show some embodiments of this application and should not be regarded as a limitation of the scope. For those skilled in the art, other related drawings can be obtained based on these drawings without creative effort.

[0016] Figure 1 A three-dimensional structural schematic diagram of a magnetically levitated centrifugal compressor according to an embodiment of this application is shown; Figure 2 A cross-sectional structural schematic diagram of a magnetically levitated centrifugal compressor according to an embodiment of this application is shown; Figure 3 It shows Figure 2 Enlarged structural diagram at point A; Figure 4 It shows Figure 2 Enlarged structural diagram at point B; Figure 5 A cross-sectional structural schematic diagram of a magnetically levitated centrifugal compressor according to another embodiment of this application is shown; Figure 6 It shows Figure 5 Enlarged structural diagram at point C; Figure 7 A cross-sectional structural schematic diagram of a magnetically levitated centrifugal compressor according to yet another embodiment of this application is shown; Figure 8 It shows Figure 7 Enlarged structural diagram at point D; Figure 9 A cross-sectional structural schematic diagram of a magnetically levitated centrifugal compressor according to another embodiment of this application is shown; Figure 10 It shows Figure 9 A magnified structural diagram at point E in the middle.

[0017] Explanation of key component symbols: 100 - Drive assembly; 110 - Drive shaft; 120 - Motor; 200-Impeller; 210-Impeller body; 220-Third comb tooth section; 230-Protrusion; 240-Fourth comb tooth section; 250-Front cover plate; 260-Rear cover plate; 270-Impeller inlet; 280-Impeller outlet; 300 - Axial force balancer; 310 - Main body; 311 - Connecting hole; 320 - First comb tooth section; 330 - Second comb tooth section; 400 - First airflow chamber; 500 - Second airflow chamber; 600 - Third airflow chamber; 700-Diffuser. Detailed Implementation

[0018] The embodiments of this application are described in detail below. Examples of these embodiments are shown in the accompanying drawings, wherein the same or similar reference numerals denote the same or similar elements or elements having the same or similar functions throughout. The embodiments described below with reference to the accompanying drawings are exemplary and are only used to explain this application, and should not be construed as limiting this application.

[0019] In the description of this application, 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., indicating the orientation or positional relationship based on the orientation or positional relationship shown in the accompanying drawings, are only for the convenience of describing this application and simplifying the description, and do not indicate or imply that the device or element referred to must have a specific orientation, or be constructed and operated in a specific orientation, and therefore should not be construed as a limitation of this application.

[0020] Furthermore, the terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this application, "multiple" means two or more, unless otherwise explicitly specified.

[0021] In this application, unless otherwise expressly specified and limited, the terms "installation," "connection," "linking," and "fixing," etc., should be interpreted broadly. For example, they can refer to a fixed connection, a detachable connection, or an integral part; they can refer to a mechanical connection or an electrical connection; they can refer to a direct connection or an indirect connection through an intermediate medium; they can refer to the internal communication of two components or the interaction between two components. Those skilled in the art can understand the specific meaning of the above terms in this application according to the specific circumstances.

[0022] In this application, unless otherwise expressly specified and limited, "above" or "below" the second feature can mean that the first feature is in direct contact with the second feature, or that the first feature is in indirect contact with the second feature through an intermediate medium. Furthermore, "above," "on top of," and "over" the second feature can mean that the first feature is directly above or diagonally above the second feature, or simply that the first feature is at a higher horizontal level than the second feature. "Below," "below," and "under" the second feature can mean that the first feature is directly below or diagonally below the second feature, or simply that the first feature is at a lower horizontal level than the second feature.

[0023] Reference Figures 1 to 4 As shown, the magnetic levitation centrifugal compressor involved in the embodiments of this application includes: a drive assembly 100, an impeller 200, and an axial force balancing component 300.

[0024] Specifically, the drive assembly 100 includes a drive shaft 110 and a motor 120, with the output end of the drive shaft 110 connected to the motor 120; an impeller 200 is sleeved on the drive shaft 110; an axial force balancing component 300 is located between the impeller 200 and the motor 120, and the axial force balancing component 300 has a main body 310, a plurality of first comb teeth 320, and a plurality of second comb teeth 330; the main body 310 is provided with a connecting hole 311 and is sleeved on the drive shaft 110 through the connecting hole 311, the hole wall of the connecting hole 311 is spaced apart from the drive shaft 110, and the main body 310 is spaced apart from the impeller 200; the plurality of first comb teeth 320 are spaced apart on the main body 310 and are positioned between the main body 310 and the impeller 200; the plurality of second comb teeth 330 are spaced apart on the hole wall of the connecting hole 311 along the axial direction of the drive shaft 110 and all protrude from the hole wall of the connecting hole 311, and are all spaced apart from the drive shaft 110.

[0025] It should be noted that, referring to Figure 2 , Figure 5 , Figure 7 as well as Figure 9 As shown, in the magnetic levitation centrifugal compressor, the front cover plate 250 of the impeller 200 is positioned away from the motor 120 along the axial direction of the drive shaft 110 relative to the rear cover plate 260 of the impeller 200, and the impeller inlet 270 is positioned away from the motor 120 along the axial direction of the drive shaft 110 relative to the impeller outlet 280. When the motor 120 drives the impeller 200 to rotate, the gas-liquid medium enters from the impeller inlet 270 and accelerates towards the impeller outlet 280 along the flow channel inside the impeller 200 under the action of centrifugal force, resulting in a gradual increase in medium pressure. This process will cause an asymmetrical pressure distribution in the areas of the front cover plate 250 and the rear cover plate 260, specifically, the pressure on the front cover plate 250 is significantly lower than that on the rear cover plate 260, thus forming a significant pressure difference between the two. This pressure difference will generate an axial thrust on the impeller 200 along the drive shaft 110, causing the impeller 200 to move away from the motor 120 along the axial direction of the drive shaft 110. To reduce this axial thrust, the pressure can be adjusted to reduce the pressure on the rear cover plate 260, thereby effectively controlling the pressure difference between the front cover plate 250 and the rear cover plate 260, and thus reducing the axial thrust on the impeller 200.

[0026] In the magnetic levitation centrifugal compressor of this application, since the drive shaft 110 is connected to the output end of the motor 120, and the impeller 200 is sleeved on the drive shaft 110, the motor 120 can drive the impeller 200 to rotate. During the rotation of the impeller 200, the side of the impeller 200 near the motor 120 is subjected to high-pressure airflow, causing the impeller 200 to displace away from the motor 120 under the action of axial force. Since the axial force balancing member 300 is disposed between the impeller 200 and the motor 120, and the main body 310 of the axial force balancing member 300 is spaced apart from both the drive shaft 110 and the impeller 200, an airflow channel can be defined between the axial force balancing member 300 and the impeller 200 by the main body 310, so that the high-pressure airflow can flow from the outlet end of the impeller 200 towards the motor 120 through the airflow channel. Since multiple first comb teeth 320 are disposed between the main body 310 and the impeller 200, when the high-pressure airflow flows in the airflow channel between the impeller 200 and the main body 310, the high-pressure airflow will flow through the multiple first comb teeth 320. When the high-pressure airflow flows through the multiple first comb teeth 320, the multiple first comb teeth 320 will create resistance to the flow of the high-pressure airflow, thereby reducing the flow velocity of the high-pressure airflow and thus reducing the pressure of the high-pressure airflow. At the same time, since multiple second comb teeth 330 are spaced apart along the axial direction of the drive shaft 110 between the drive shaft 110 and the main body 310, when the high-pressure airflow is driven... When the airflow flows within the airflow channel between shaft 110 and main body 310, the multiple second comb teeth 330 create resistance to the flow of high-pressure airflow, thereby further reducing the flow velocity and pressure of the high-pressure airflow. In this way, the axial force balancing member 300 can depressurize the high-pressure airflow on the side of impeller 200 closest to motor 120, reducing the pressure difference between the two sides of impeller 200 along the axial direction of drive shaft 110. This balances the axial force of impeller 200 without increasing the friction between impeller 200 and drive shaft 110, reducing the possibility of friction between impeller 200 and drive shaft 110. Simultaneously, the cooperation of the multiple first comb teeth 320 and multiple second comb teeth 330 forms a labyrinth seal tooth structure, improving the sealing effect on the medium and reducing leakage. Therefore, the magnetic levitation centrifugal compressor of this application can achieve axial force balance without the need for additional complex balancing devices, and can also reduce the possibility of friction between the impeller 200 and the drive shaft 110, and reduce media leakage.

[0027] When balancing the axial force of the impeller 200, there is no need to achieve balance through an additional complex balancing device, and the friction between the impeller and the drive shaft 110 is not increased. Therefore, the magnetic levitation centrifugal compressor of this application has a better balancing method for balancing the axial force of the impeller 200.

[0028] Specifically, in this embodiment, the tooth height of the first comb tooth portion 320, the tooth width of the first comb tooth portion 320, the tooth pitch between the plurality of first comb tooth portions 320, and the number of the plurality of first comb tooth portions 320 can be adjusted according to the actual pressure adjustment requirements; similarly, the tooth height of the second comb tooth portion 330, the tooth width of the second comb tooth portion 330, the tooth pitch between the plurality of second comb tooth portions 330, and the number of the plurality of second comb tooth portions 330 can be adjusted according to the actual pressure adjustment requirements.

[0029] Reference Figure 2 as well as Figure 5 As shown, in some embodiments, the impeller 200 has a wheel body portion 210, which is sleeved on the drive shaft 110. The main body portion 310 and the wheel body portion 210 are spaced apart. A plurality of first comb teeth 320 are disposed between the main body portion 310 and the wheel body portion 210, and a plurality of second comb teeth 330 are disposed between the wheel body portion 210 and the drive shaft 110.

[0030] In this embodiment, the gas-liquid medium flows from the impeller inlet 270 to the impeller outlet 280 within the wheel body portion 210. Since multiple first comb teeth 320 are disposed between the main body portion 310 and the wheel body portion 210, the high-pressure airflow can be depressurized by the disturbance and resistance of the multiple first comb teeth 320. Since multiple second comb teeth 330 are disposed between the wheel body portion 210 and the drive shaft 110, the gas flow can be depressurized again by the disturbance and resistance, thereby reducing the airflow pressure in the rear cover plate 260 region, thereby reducing the pressure difference between the front cover plate 250 and the rear cover plate 260, and achieving the balance of the axial force on the impeller 200.

[0031] Reference Figure 3 as well as Figure 6 As shown, in some embodiments, a plurality of first comb teeth 320 are radially spaced on the main body 310 along the drive shaft 110, and the impeller 200 also has a plurality of third comb teeth 220, which are radially spaced on the side of the wheel body 210 near the main body 310 along the drive shaft 110, and the plurality of third comb teeth 220 are staggered with the plurality of first comb teeth 320.

[0032] In this embodiment, since multiple first comb teeth 320 are arranged radially at intervals on the main body 310 along the drive shaft 110, when the airflow flows out from the impeller outlet 280, it will flow through multiple first comb teeth 320 in sequence, so as to reduce the airflow pressure through the disturbance and resistance of multiple first comb teeth 320. However, when the impeller 200 shifts away from the motor 120 under the action of axial force, the distance between the wheel body 210 and the multiple first comb teeth 320 gradually increases. This weakens the disturbance and resistance effect of the multiple first comb teeth 320 on the airflow. Since the multiple third comb teeth 220 are arranged radially at intervals along the drive shaft 110 and are staggered with the multiple first comb teeth 320, even if the distance between the wheel body 210 and the multiple first comb teeth 320 gradually increases, an "S-shaped" flow channel can be formed between the multiple third comb teeth 220 and the multiple first comb teeth 320 to reduce the airflow velocity through the "S-shaped" flow channel, thereby ensuring the pressure reduction of the airflow.

[0033] Specifically, in this embodiment, referring to Figure 3 , Figure 4 as well as Figure 6 As shown, the impeller outlet 280 is connected to the airflow channel. Multiple first comb teeth 320 and multiple second comb teeth 330 divide the airflow channel into a first airflow chamber 400, a second airflow chamber 500, and a third airflow chamber 600. The first airflow chamber 400 is located between the impeller outlet 280 and the multiple first comb teeth 320, the second airflow chamber 500 is located between the multiple first comb teeth 320 and the multiple second comb teeth 330, and the third airflow chamber 600 is located between the multiple second comb teeth 330 and the motor 120. When the gas-liquid medium flows through the impeller outlet 280, the airflow will flow sequentially through the first airflow chamber 400, the multiple first comb teeth 320, the second airflow chamber 500, the multiple second comb teeth 330, and the third airflow chamber 600. During the gas flow process, due to the disturbance and resistance of the gas flow by the multiple first comb teeth 320, the air pressure in the second airflow chamber 500 is lower than the air pressure in the first airflow chamber 400. Similarly, due to the disturbance and resistance of the gas flow by the multiple second comb teeth 330, the air pressure in the third airflow chamber 600 is lower than the air pressure in the second airflow chamber 500, thereby achieving air pressure reduction in the rear cover plate 260 area.

[0034] Specifically, refer to Figure 3 as well as Figure 6 As shown, in some embodiments, the tooth pitch value between any two adjacent first comb teeth 320 is greater than the tooth width value of any third comb teeth 220; the tooth pitch value between any two adjacent third comb teeth 220 is greater than the tooth width value of any first comb teeth 320.

[0035] In this embodiment, since the tooth pitch between any two adjacent first comb teeth 320 is greater than the tooth width of any third comb teeth 220, any two adjacent first comb teeth 320 and the third comb teeth 220 located between them can be spaced apart. Similarly, since the tooth pitch between any two adjacent third comb teeth 220 is greater than the tooth width of any first comb teeth 320, any two adjacent third comb teeth 220 and the first comb teeth 320 located between them can be spaced apart, thereby ensuring that an "S-shaped" flow channel is formed between the plurality of third comb teeth 220 and the plurality of first comb teeth 320, so that the airflow in the first airflow cavity 400 can flow into the second airflow cavity 500 through the plurality of first comb teeth 320 and the plurality of third comb teeth 220.

[0036] Reference Figure 3 As shown, in some embodiments, each first comb tooth 320 is arranged parallel to the axial direction along the drive shaft 110.

[0037] In the embodiment, since each first comb tooth 320 is arranged parallel to the axial direction along the drive shaft 110, when the airflow flows between the multiple first comb teeth 320 and the multiple third comb teeth 220, the flow path of the airflow can be extended, thereby further reducing the flow velocity of the airflow and improving the pressure reduction effect on the airflow.

[0038] Reference Figure 6 As shown, in some embodiments, each first comb tooth 320 is inclined relative to the axial direction of the drive shaft 110, and each third comb tooth 220 is inclined relative to the axial direction of the drive shaft 110, and the inclination direction of the third comb tooth 220 is the same as that of the first comb tooth 320.

[0039] In this embodiment, since each first comb tooth 320 and each third comb tooth 220 are inclined relative to the axial direction of the drive shaft 110, and the inclination direction of the third comb tooth 220 is the same as that of the first comb tooth 320, when the impeller 200 is deflected away from the motor 120 under the action of axial force, the probability of the first comb tooth 320 and the third comb tooth 220 disengaging can be reduced, so as to ensure the structural stability of the "S-shaped" flow channel between the multiple third comb tooth 220 and the multiple first comb tooth 320.

[0040] Reference Figure 8 as well as Figure 10As shown, in some embodiments, the impeller 200 further includes a protrusion 230, which is disposed on the side of the wheel body portion 210 near the main body portion 310 and protrudes from the wheel body portion 210 along the axial direction of the drive shaft 110. The protrusion 230 and the drive shaft 110 are radially spaced apart. The axial force balancer 300 is at least partially disposed between the protrusion 230 and the drive shaft 110, and a plurality of first comb teeth 320 are located between the protrusion 230 and the main body portion 310.

[0041] In this embodiment, since the protrusion 230 protrudes from the wheel body 210 along the axial direction of the drive shaft 110, and the axial force balancer 300 is at least partially disposed between the protrusion 230 and the drive shaft 110, when the airflow passes between the axial force balancer 300 and the protrusion 230, the airflow direction changes from the radial direction of the drive shaft 110 to the axial direction of the drive shaft 110, thereby further increasing the disturbance to the airflow by changing the airflow direction. Furthermore, since the plurality of first comb teeth 320 are located between the protrusion 230 and the main body 310, when the airflow passes between the axial force balancer 300 and the protrusion 230, the airflow pressure can be reduced by the disturbance and resistance of the plurality of first comb teeth 320. Furthermore, when the multiple first comb teeth 320 are located between the protrusion 230 and the main body 310, even if the impeller 200 moves axially under the action of axial force, the distance between the axial force balancer 300 and the protrusion 230 will not change, thereby ensuring that the multiple first comb teeth 320 do not disturb or resist the airflow.

[0042] Continue to refer to Figure 8 In some embodiments, a plurality of first comb teeth 320 are spaced apart along the axial direction of the drive shaft 110, and each first comb tooth 320 is angled to the axial direction of the drive shaft 110, and each first comb tooth 320 is spaced apart from the protrusion 230.

[0043] In this embodiment, since the multiple first comb teeth 320 are spaced apart along the axial direction of the drive shaft 110, even if the impeller 200 moves axially under the action of axial force, at least some of the first comb teeth 320 can be located between the protrusion 230 and the main body 310 to ensure that the multiple first comb teeth 320 have a disturbance and resistance effect on the airflow. Since each first comb tooth 320 is set at an angle to the axial direction of the drive shaft 110 and each first comb tooth 320 is spaced apart from the protrusion 230, the airflow can be ensured to flow between the main body 310 and the protrusion 230. At the same time, when the airflow flows between the main body 310 and the protrusion 230, the airflow flows in the "S-shaped" flow channel formed between the multiple first comb teeth 320 to disturb and resist the airflow, thereby achieving the depressurization of the airflow.

[0044] Specifically, refer to Figure 7 As shown, in this embodiment, the magnetic levitation centrifugal compressor further includes a diffuser 700, which is sleeved on the drive shaft 110 and located between the axial force balancer 300 and the motor 120. The impeller outlet 280 is connected to the airflow channel. A plurality of first comb teeth 320 and a plurality of second comb teeth 330 divide the airflow channel into a first airflow chamber 400, a second airflow chamber 500, and a third airflow chamber 600. The first airflow chamber 400 is located between the impeller outlet 280 and the plurality of first comb teeth. The first airflow chamber 500 is located between the multiple first comb teeth 320 and the multiple second comb teeth 330, and the third airflow chamber 600 is located between the multiple second comb teeth 330 and the motor 120. When the gas-liquid medium flows through the impeller outlet 280, the airflow will sequentially flow through the first airflow chamber 400, the multiple first comb teeth 320, the second airflow chamber 500, the multiple second comb teeth 330, and the third airflow chamber 600. During the gas flow, due to the disturbance and resistance of the gas flow by the multiple first comb teeth 320, the airflow pressure in the second airflow chamber 500 will be lower than the airflow pressure in the first airflow chamber 400. Similarly, due to the disturbance and resistance of the gas flow by the multiple second comb teeth 330, the airflow pressure in the third airflow chamber 600 will be lower than the airflow pressure in the second airflow chamber 500, thereby achieving airflow pressure reduction in the area of ​​the rear cover plate 260.

[0045] Reference Figure 10 As shown, in some embodiments, the impeller 200 also has a plurality of fourth comb teeth 240, which are spaced apart on the protrusion 230 along the axial direction of the drive shaft 110 and are all spaced apart from the main body 310. The plurality of fourth comb teeth 240 are staggered with the plurality of first comb teeth 320.

[0046] In this embodiment, since the multiple fourth comb teeth 240 and the multiple first comb teeth 320 are staggered, the structural stability of the impeller 200 can be improved by the mutual limiting effect of the multiple fourth comb teeth 240 and the multiple first comb teeth 320, further reducing the possibility of the impeller 200 moving axially along the drive shaft 110. At the same time, it can further increase the disturbance and resistance effect on the airflow, thereby improving the pressure reduction effect on the airflow.

[0047] Continue to refer to Figure 10 As shown, in some embodiments, the tooth pitch value between any two adjacent first comb teeth 320 is greater than the tooth width value of any fourth comb teeth 240; the tooth pitch value between any two adjacent fourth comb teeth 240 is greater than the tooth width value of any first comb teeth 320.

[0048] In this embodiment, since the tooth pitch between any two adjacent first comb teeth 320 is greater than the tooth width of any fourth comb tooth 240, any two adjacent first comb teeth 320 and the fourth comb tooth 240 located between them can be spaced apart. Similarly, since the tooth pitch between any two adjacent fourth comb teeth 240 is greater than the tooth width of any first comb tooth 320, any two adjacent fourth comb teeth 240 and the first comb tooth 320 located between them can be spaced apart, thereby ensuring that an "S-shaped" flow channel is formed between the plurality of fourth comb teeth 240 and the plurality of first comb teeth 320, so that the airflow in the first airflow cavity 400 can flow into the second airflow cavity 500 through the plurality of first comb teeth 320 and the plurality of fourth comb teeth 240.

[0049] Specifically, in the above embodiments, the first comb tooth portion 320, the second comb tooth portion 330, the third comb tooth portion 220, and the fourth comb tooth portion 240 can all play a sealing role. Since the axial force balancer 300 reduces the pressure difference between the front cover plate 250 and the rear cover plate 260, when the medium flows together with the airflow in the impeller 200, the medium may leak along the first airflow chamber 400, the second airflow chamber 500, and the third airflow chamber 600. At this time, the first comb tooth portion 320, the second comb tooth portion 330, the third comb tooth portion 220, and the fourth comb tooth portion 240 can all form a labyrinth sealing tooth structure to play a sealing role for the medium and reduce the leakage of the medium.

[0050] In the description of this specification, the references to terms such as "one embodiment," "some embodiments," "example," "specific example," or "some examples," etc., refer to specific features, structures, materials, or characteristics described in connection with that embodiment or example, which are included in at least one embodiment or example of this application. In this specification, the illustrative expressions 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 one or more embodiments or examples. Moreover, without contradiction, those skilled in the art can combine and integrate the different embodiments or examples described in this specification, as well as the features of different embodiments or examples.

[0051] Although embodiments of this application have been shown and described above, it is understood that the above embodiments are exemplary and should not be construed as limiting this application. Those skilled in the art can make changes, modifications, substitutions and variations to the above embodiments within the scope of this application.

Claims

1. A magnetically levitated centrifugal compressor, characterized in that, include: A drive assembly includes a drive shaft and a motor, wherein the drive shaft is connected to the output end of the motor; The impeller is fitted onto the drive shaft; An axial force balancing component is located between the impeller and the motor. The axial force balancing component has a main body, a plurality of first comb teeth, and a plurality of second comb teeth. The main body is provided with a connecting hole and is sleeved on the drive shaft through the connecting hole. The wall of the connecting hole is spaced apart from the drive shaft, and the main body is spaced apart from the impeller. A plurality of first comb teeth are spaced apart on the main body and disposed between the main body and the impeller; Multiple second comb teeth are spaced apart on the wall of the connecting hole along the axial direction of the drive shaft, and each protrudes from the wall of the connecting hole and is spaced apart from the drive shaft.

2. The magnetic levitation centrifugal compressor according to claim 1, characterized in that, The impeller has a wheel body portion, which is sleeved on the drive shaft. The main body portion and the wheel body portion are spaced apart. A plurality of first comb teeth portions are disposed between the main body portion and the wheel body portion, and a plurality of second comb teeth portions are disposed between the wheel body portion and the drive shaft.

3. The magnetic levitation centrifugal compressor according to claim 2, characterized in that, A plurality of first comb teeth are radially spaced on the main body along the drive shaft. The impeller also has a plurality of third comb teeth, which are radially spaced on the side of the wheel body near the main body along the drive shaft. The plurality of third comb teeth are staggered with the plurality of first comb teeth.

4. The magnetic levitation centrifugal compressor according to claim 3, characterized in that, The tooth pitch between any two adjacent first comb teeth is greater than the tooth width of any third comb tooth. The tooth pitch between any two adjacent third comb teeth is greater than the tooth width of any first comb tooth.

5. The magnetic levitation centrifugal compressor according to claim 3, characterized in that, Each of the first comb teeth is arranged parallel to the axial direction along the drive shaft.

6. The magnetic levitation centrifugal compressor according to claim 3, characterized in that, Each of the first comb teeth is inclined relative to the axial direction of the drive shaft, and each of the third comb teeth is inclined relative to the axial direction of the drive shaft, and the inclination direction of the third comb teeth is the same as that of the first comb teeth.

7. The magnetically levitated centrifugal compressor according to claim 2, characterized in that, The impeller also includes a protrusion disposed on the side of the wheel body portion near the main body portion and protruding from the wheel body portion along the axial direction of the drive shaft. The protrusion and the drive shaft are radially spaced apart. The axial force balancing member is at least partially disposed between the protrusion and the drive shaft, and a plurality of first comb teeth portions are located between the protrusion and the main body portion.

8. The magnetic levitation centrifugal compressor according to claim 7, characterized in that, Multiple first comb teeth are spaced apart along the axial direction of the drive shaft, and each first comb tooth is angled to the axial direction of the drive shaft, and each first comb tooth is spaced apart from the protrusion.

9. The magnetic levitation centrifugal compressor according to claim 8, characterized in that, The impeller also has a plurality of fourth comb teeth, which are spaced apart on the protrusion along the axial direction of the drive shaft and are all spaced apart from the main body. The plurality of fourth comb teeth are staggered with the plurality of first comb teeth.

10. The magnetically levitated centrifugal compressor according to claim 9, characterized in that, The tooth pitch between any two adjacent first comb teeth is greater than the tooth width of any fourth comb tooth. The tooth pitch between any two adjacent fourth comb teeth is greater than the tooth width of any first comb tooth.

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