Pneumatic structure and air flotation motor system

Abstract

The utility model discloses a pneumatic structure and an air flotation motor system, and relates to the technical field of air flotation bearing high-speed motors, a working impeller of the pneumatic structure is assembled in a shaft hole of a sealing plate, the side, facing the sealing plate, of the working impeller is a blade back, and a sealing gap is formed between the blade back and the sealing surface of the sealing plate; the sealing surface is of a flat structure, and the distances between the sealing surface and the blade back are equal everywhere. A detection channel is formed between the blade back and the sealing surface, a detection inlet is formed between the tip of the blade back and the sealing surface, or a detection inlet is formed between the tip of the sealing surface and the blade back, and the detection inlet is communicated with the detection channel to form a sealing gap measuring structure. According to the pneumatic structure, a sealing gap measuring structure is formed, so that the sealing gap between the blade back and the sealing surface can be directly measured, the problems that the impeller needs to be disassembled and assembled for multiple times and the measuring precision is low in the prior art are solved, the measuring efficiency and precision are improved, and the cooling effect and the overall performance of an air flotation motor system are further improved.

Description

Technical Field

[0001] This application relates to the field of air bearing high-speed motor technology, and specifically designs a pneumatic structure and an air bearing motor system. Background Technology

[0002] In a high-speed motor system with an air bearing, the impeller is one of the core components, its main function being to compress and transfer gas through high-speed rotation. Because the thrust bearing in the air bearing generates a significant amount of heat during operation, it requires cooling gas. This cooling is typically achieved using cooling gas that leaks through the sealing gap between the impeller back and the sealing plate.

[0003] The size of the sealing gap directly affects the flow rate and pressure of the cooling gas, thus impacting the cooling effect of the air bearing. Currently, the method for measuring the sealing gap between the impeller blade back and the sealing plate typically involves shimming a lead wire between them, locking the working impeller, disassembling the working impeller, measuring the lead wire indentation, and indirectly calculating the sealing gap value between the blade back and the sealing plate. This method has shortcomings. First, shimming the lead wire requires multiple disassemblies and reassemblies of the working impeller, which is complex and time-consuming, increasing assembly and maintenance time costs. Second, the measurement accuracy of the lead wire indentation is limited, making it difficult to accurately reflect the actual gap between the blade back and the sealing plate. This may lead to inaccurate control of the cooling gas flow rate and pressure, thereby affecting the cooling effect of the air bearing and the overall performance of the motor system. Utility Model Content

[0004] The purpose of this application is to provide a pneumatic structure that forms a sealing gap measurement structure, enabling direct measurement of the sealing gap between the impeller back and the sealing surface. This solves the problems of repeated impeller disassembly and assembly and low measurement accuracy in existing technologies, improving measurement efficiency and accuracy, and thus enhancing the cooling effect and overall performance of the air-bearing motor system. Another purpose of this application is to provide an air-bearing motor system.

[0005] To achieve the above objectives, this application provides a pneumatic structure, comprising:

[0006] A sealing plate has a through shaft hole in the middle, and a sealing surface is formed on the first side of the sealing plate;

[0007] A working impeller is fitted into the shaft hole of the sealing plate. The side of the working impeller facing the sealing plate is the blade back, and there is a sealing gap between the blade back and the sealing surface.

[0008] The sealing surface is configured as a flat structure, and the distance between the sealing surface and the blade back is equal everywhere; a detection channel is formed between the blade back and the sealing surface, and a detection inlet is formed between the tip of the blade back and the sealing surface, or a detection inlet is formed between the tip of the sealing surface and the blade back, and the detection inlet is connected to the detection channel to form a sealing gap measurement structure.

[0009] In some embodiments, the radial dimension of the sealing plate is greater than the radial dimension of the working impeller, and the detection inlet is formed between the tip of the blade back and the sealing surface.

[0010] In some embodiments, the sealing surface forms a pilot area beyond the tip of the sealing surface extending beyond the back of the blade and within the tip of the sealing surface, the pilot area being in communication with the detection inlet.

[0011] In some embodiments, the sealing surface and the blade back are circular in shape, and the sealing gap measuring structure is a three-dimensional hollow ring.

[0012] In some embodiments, the pneumatic structure further includes a first volute, which is fitted to the sealing plate and has a helical channel leading to the radial position of the working impeller.

[0013] In some embodiments, the first volute has an extension section that contacts the sealing surface and is spaced apart from the working impeller. An air passage is formed between the extension section and the working impeller, and the air passage leads to the sealing gap between the blade back and the sealing surface.

[0014] In some embodiments, the pneumatic structure further includes a second volute, which is assembled to the first volute. The second volute is provided with an air intake channel leading to the axial position of the power impeller.

[0015] This application also provides an air-bearing motor system, including an air-bearing high-speed motor and the aforementioned pneumatic structure, wherein the pneumatic structure is assembled on the air-bearing high-speed motor.

[0016] In some embodiments, the air bearing high-speed motor includes a housing, a stator assembly, and a rotating shaft, wherein the rotating shaft is assembled inside the stator assembly;

[0017] The pneumatic structure includes a first volute, both the first volute and the sealing plate are disposed in the housing, and the power impeller is disposed on the rotating shaft.

[0018] In some embodiments, the air-float motor system further includes a second impeller, which is coaxially disposed at both ends of the rotating shaft with the power impeller.

[0019] Compared to the aforementioned background technology, the pneumatic structure provided in this application mainly includes a sealing plate and a working impeller. The sealing plate has a through shaft hole in the middle, and a sealing surface is formed on the first side of the sealing plate. The working impeller is assembled in the shaft hole of the sealing plate, and the side of the working impeller facing the sealing plate is the blade back. There is a sealing gap between the blade back and the sealing surface. The sealing surface is set as a flat structure, and the distance between the sealing surface and the blade back is equal everywhere. A detection channel is formed between the blade back and the sealing surface, and a detection inlet is formed between the tip of the blade back and the sealing surface, or between the tip of the sealing surface and the blade back. The detection inlet and the detection channel are connected to form a sealing gap measurement structure.

[0020] In air-bearing motor systems, the sealing gap between the impeller and the sealing surface is one of the key factors ensuring efficient system operation. Traditionally, measuring the sealing gap typically requires multiple impeller disassembly and reassembly, a method that is not only time-consuming and labor-intensive but also prone to inaccuracies due to the complexity of the measurement process. This inefficient and inaccurate measurement method directly impacts the cooling effect and overall performance of the air-bearing motor system.

[0021] To address this issue, this application provides an innovative pneumatic structure, primarily comprising a sealing plate and a working impeller. The sealing plate has a through-hole shaft in its center, and its first side forms a flat sealing surface. This flat structure ensures that the distance between the blade back and the sealing surface is equidistant, providing a basis for accurate measurement. The working impeller is mounted in the shaft hole of the sealing plate, with its blade back facing the sealing plate, and a sealing gap existing between the blade back and the sealing surface.

[0022] Furthermore, a detection channel is formed between the blade back and the sealing surface, and a detection inlet is formed between the tip of the blade back and the sealing surface, or between the tip of the sealing surface and the blade back, depending on which has a larger radial dimension, i.e., which has a more outward-pointing tip. The detection inlet and the detection channel are connected, together forming the sealing gap measurement structure. This design allows the sealing gap to be measured directly without repeated disassembly and reassembly of the impeller, greatly improving measurement efficiency.

[0023] In practical use, the sealing plate and the working impeller are first assembled together. Then, a measuring tool, such as a feeler gauge, is inserted along the sealing gap measuring structure to detect the sealing gap between the impeller back and the sealing surface. This direct measurement method not only simplifies the measurement process but also significantly improves measurement accuracy. The flat sealing surface and uniform sealing gap design make the measurement process more stable and reliable, thus avoiding errors caused by multiple disassemblies and complex operations in traditional methods.

[0024] This high-precision measurement method can more accurately reflect the actual distance between the blade back and the sealing surface, thus providing reliable data support for the optimized design and operation of the air-bearing motor system. This direct measurement structure design not only improves measurement efficiency and accuracy but also enhances the cooling effect and overall performance of the air-bearing motor system.

[0025] Based on the above structural and process descriptions, it can be seen that the pneumatic structure has at least the following beneficial effects: The pneumatic structure forms a sealing gap measurement structure, which enables the sealing gap between the blade back and the sealing surface to be directly measured, thereby solving the problems of multiple impeller disassembly and assembly and low measurement accuracy in the prior art, improving measurement efficiency and accuracy, and thus enhancing the cooling effect and overall performance of the air-bearing motor system. Attached Figure Description

[0026] To more clearly illustrate the technical solutions in the embodiments of this application or the prior art, the drawings used in the description of the embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are only embodiments of this application. For those skilled in the art, other drawings can be obtained based on the provided drawings without creative effort.

[0027] Figure 1 A schematic diagram of the aerodynamic structure provided in the embodiments of this application;

[0028] Figure 2 Another schematic diagram of the aerodynamic structure provided in the embodiments of this application;

[0029] Figure 3 This is a schematic diagram of an air flotation motor system provided in an embodiment of this application.

[0030] in:

[0031] Aerodynamic structure 100

[0032] Sealing plate 1, shaft hole 101, sealing surface 102

[0033] 2. Working impeller; 201. Blade back; 202. Detection channel; 203. Detection inlet; 204. Sealing gap measuring structure; 205. Pilot zone.

[0034] First volute 3, spiral channel 301, extension section 302, ventilation channel 303

[0035] Second volute 4, air intake passage 401

[0036] 200 high-speed motor with air bearing

[0037] Casing 5

[0038] Stator assembly 6

[0039] 7. Rotating shaft

[0040] Second impeller 8,

[0041] Air flotation motor system 1000. Detailed Implementation

[0042] The technical solutions of the embodiments of this application will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of this application, and not all embodiments. Based on the embodiments of this application, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of this application.

[0043] To enable those skilled in the art to better understand the present application, the present application will be further described in detail below with reference to the accompanying drawings and specific embodiments.

[0044] Please refer to Figure 1 , Figure 1 This is a schematic diagram of the aerodynamic structure provided in an embodiment of this application.

[0045] In a first specific embodiment, the pneumatic structure 100 provided in this application mainly includes a sealing plate 1 and a working impeller 2. The sealing plate 1 has a through shaft hole 101 in the middle, and a sealing surface 102 is formed on the first side of the sealing plate 1. The working impeller 2 is assembled into the shaft hole 101 of the sealing plate 1. The side of the working impeller 2 facing the sealing plate 1 is a blade back 201, and there is a sealing gap between the blade back 201 and the sealing surface 102. The sealing surface 102 is set as a flat structure, and the distance between the sealing surface 102 and the blade back 201 is equal everywhere. A detection channel 202 is formed between the blade back 201 and the sealing surface 102, and a detection inlet 203 is formed between the tip of the blade back 201 and the sealing surface 102, or a detection inlet 203 is formed between the tip of the sealing surface 102 and the blade back 201. The detection inlet 203 and the detection channel 202 are connected to form a sealing gap measuring structure 204.

[0046] In the air-float motor system 1000, the sealing gap between the impeller and the sealing surface is one of the key factors ensuring the efficient operation of the system. In traditional technology, measuring the sealing gap usually requires multiple disassemblies and reassemblies of the impeller. This method is not only time-consuming and labor-intensive, but also often suffers from difficulty in guaranteeing measurement accuracy due to the complexity of the measurement process. This inefficient and inaccurate measurement method directly affects the cooling effect and overall performance of the air-float motor system 1000.

[0047] To address this issue, this application provides an innovative pneumatic structure 100, which mainly includes a sealing plate 1 and a power impeller 2. The sealing plate 1 has a through shaft hole 101 in its center, and a flat sealing surface 102 is formed on its first side. This flat structure ensures that the distance between the blade back 201 and the sealing surface 102 is equal everywhere, providing a basis for accurate measurement. The power impeller 2 is mounted in the shaft hole 101 of the sealing plate 1, with its blade back 201 facing the sealing plate 1, and a sealing gap between the blade back 201 and the sealing surface 102.

[0048] Furthermore, a detection channel 202 is formed between the blade back 201 and the sealing surface 102, and a detection inlet 203 is formed between the tip of the blade back 201 and the sealing surface 102, or between the tip of the sealing surface 102 and the blade back 201, depending on which has a larger radial dimension, i.e., which has a more outward-pointing tip. The detection inlet 203 communicates with the detection channel 202, together forming the sealing gap measurement structure 204. This design allows the sealing gap to be measured directly without repeated disassembly and reassembly of the impeller, greatly improving measurement efficiency.

[0049] In practical use, the sealing plate 1 and the working impeller 2 are first assembled together. Then, a measuring tool, such as a feeler gauge, is inserted along the sealing gap measuring structure 204 to detect the sealing gap between the impeller back 201 and the sealing surface 102. This direct measurement method not only simplifies the measurement process but also significantly improves measurement accuracy. The flat sealing surface 102 and the uniform sealing gap design make the measurement process more stable and reliable, thus avoiding errors caused by multiple disassemblies and complex operations in traditional methods.

[0050] This high-precision measurement method can more accurately reflect the actual distance between the blade back 201 and the sealing surface 102, thus providing reliable data support for the optimized design and operation of the air-bearing motor system 1000. This direct measurement structural design not only improves measurement efficiency and accuracy but also enhances the cooling effect and overall performance of the air-bearing motor system 1000.

[0051] Based on the above structural and process descriptions, it can be seen that the pneumatic structure 100 has at least the following beneficial effects: The pneumatic structure 100 forms a sealing gap measuring structure 204, which enables the sealing gap between the blade back 201 and the sealing surface 102 to be directly measured, thereby solving the problems of multiple impeller disassembly and assembly and low measurement accuracy in the prior art, improving measurement efficiency and accuracy, and thus enhancing the cooling effect and overall performance of the air-bearing motor system 1000.

[0052] In some embodiments, the radial dimension of the sealing plate 1 is larger than the radial dimension of the working impeller 2, and the detection inlet 203 is formed between the tip of the blade back 201 and the sealing surface 102.

[0053] In this embodiment, this design allows the detection inlet 203 to be formed between the tip of the blade back 201 and the sealing surface 102. This structural layout is chosen based on the relative dimensional relationship between the blade back 201 and the sealing surface 102; specifically, it is based on the condition that the radial dimension of the sealing plate 1 is larger than the radial dimension of the working impeller 2. In this case, the projection of the working impeller 2 onto the sealing plate 1 lies entirely within the contour of the sealing plate 1, meaning that the tip of the sealing surface 102 is located at a more distant radial position, thus providing space for the formation of the detection inlet 203.

[0054] This design choice offers several advantages. First, by increasing the structural dimensions of the sealing plate 1, the assembly process is simplified. In actual assembly, the larger sealing plate 1 provides more stable support and positioning, facilitating the precise installation of the power impeller 2. Second, this dimensional relationship helps improve the sealing effect when the subsequent pneumatic structure 100 is assembled with the air bearing high-speed motor 200. The larger sealing plate 1 provides a wider contact area, thereby enhancing sealing performance and reducing the risk of gas leakage. Furthermore, this design improves assembly convenience, as the larger sealing plate 1 provides more operating space for assembly tools and personnel, reducing assembly difficulty and time costs.

[0055] In some embodiments, a pilot region 205 is formed on the sealing surface 102 beyond the tip of the blade back 201 and within the tip of the sealing surface 102, and the pilot region 205 is in communication with the detection inlet 203.

[0056] In this embodiment, the pilot area 205 is located on the sealing surface 102 beyond the tip of the blade back 201, but also within the tip of the sealing surface 102. This design allows the pilot area 205 to communicate with the detection inlet 203, providing additional convenience for the insertion of measuring tools.

[0057] The pilot zone 205 can be understood as a guiding and supporting extension surface. When a measuring tool such as a feeler gauge is inserted into the detection inlet 203 of the sealing gap measuring structure 204, the pilot zone 205 provides an initial placement position for the feeler gauge. By placing the feeler gauge in the pilot zone 205, the operator can push the feeler gauge along this extension surface, allowing it to enter the sealing gap measuring structure 204 more smoothly. This design not only improves the ease of access for measuring tools to the sealing gap but also enhances the accuracy of the measurement.

[0058] Guided by the pilot zone 205, the feeler gauge can enter the detection channel 202 more stably, reducing measurement errors caused by improper operation. Furthermore, the presence of the pilot zone 205 provides additional support for the measuring tool, reducing the risk of the feeler gauge shifting or being damaged during measurement. This design optimizes the measurement process, making the measurement of sealing gaps more efficient and reliable.

[0059] It should be noted that the pilot area 205 belongs to the sealing surface 102, and therefore is also a flat surface.

[0060] In some embodiments, the sealing surface 102 and the blade back 201 are circular in shape, and the sealing gap measuring structure 204 is a three-dimensional hollow ring.

[0061] In this embodiment, the design of this structure provides great convenience and flexibility for measuring the sealing gap.

[0062] Specifically, when using a feeler gauge to measure the sealing gap, the feeler gauge can be inserted into the detection channel 202 through the detection inlet 203. Since the sealing gap measuring structure 204 is a three-dimensional hollow ring, the feeler gauge can enter from any point on the outer circumference of the three-dimensional hollow ring, and the entry direction is not limited to radial; it can also be at a certain angle to the radial direction. This design makes the measurement operation more flexible, allowing operators to choose the most convenient insertion angle and position according to the actual situation, thereby improving measurement efficiency.

[0063] Once the feeler gauge enters the hollow ring, its thickness can be detected, which corresponds to the sealing gap. This design not only simplifies the measurement process but also improves accuracy and reliability. Due to the structural characteristics of the hollow ring, the feeler gauge can be used for measurements at multiple locations, ensuring comprehensive and consistent measurement results.

[0064] Please refer to Figure 2 , Figure 2 This is another schematic diagram of the aerodynamic structure provided in an embodiment of this application.

[0065] In some embodiments, the pneumatic structure 100 further includes a first volute 3, which is assembled on the sealing plate 1. The first volute 3 is provided with a spiral channel 301, which leads to the radial position of the working impeller 2.

[0066] In this embodiment, the pneumatic structure 100 further expands its function and structural design by introducing a first volute 3. The first volute 3 is assembled with the sealing plate 1. This combination not only enhances the overall stability of the pneumatic structure 100, but also provides an optimized path for gas flow.

[0067] The first volute 3 has a spiral channel 301 inside. This design not only improves the efficiency of gas flow, but also optimizes the distribution of gas around the working impeller 2, thereby improving the overall performance of the aerodynamic structure 100.

[0068] In some embodiments, the first volute 3 is provided with an extension section 302, which contacts the sealing surface 102 and is spaced apart from the working impeller 2. An air passage 303 is formed between the extension section 302 and the working impeller 2, and the air passage 303 leads to the sealing gap between the blade back 201 and the sealing surface 102.

[0069] In this embodiment, this design creates a ventilation channel 303 between the extension section 302 and the working impeller 2. This ventilation channel 303 leads directly to the sealing gap between the blade back 201 and the sealing surface 102, allowing the airflow to flow as expected to achieve a cooling effect.

[0070] It is important to note that when testing the sealing gap, the assembly of the sealing plate 1 and the working impeller 2 is usually completed first, but the assembly of the first volute 3 is not performed at this time. In this state, the sealing gap measuring structure 204 can be considered exposed, facilitating direct measurement using measuring tools such as feeler gauges. This design not only simplifies the measurement process but also improves the accuracy and efficiency of the measurement.

[0071] After the sealing gap measurement is completed, the first volute 3 is assembled. At this point, although the extension 302 may partially obstruct the sealing gap measurement structure 204, this obstruction does not affect the measurement results since the sealing gap measurement has already been completed. Simultaneously, due to the presence of the ventilation channel 303, airflow can smoothly enter the space between the blade back 201 and the sealing surface 102, thereby achieving a cooling effect on the sealing gap. This design not only optimizes the functionality of the aerodynamic structure 100 but also improves the overall performance and reliability of the system.

[0072] Please refer to Figure 3 , Figure 3 This is a schematic diagram of an air flotation motor system provided in an embodiment of this application.

[0073] In some embodiments, the pneumatic structure 100 further includes a second volute 4, which is assembled to the first volute 3. The second volute 4 is provided with an air intake channel 401, which leads to the axial position of the power impeller 2.

[0074] In this embodiment, the pneumatic structure 100 further expands its function and structural design by introducing a second volute 4. The second volute 4 is assembled to the first volute 3, together forming a complete volute structure. This modular design not only improves assembly flexibility but also facilitates subsequent maintenance and replacement.

[0075] The second volute 4 is equipped with an air intake channel 401, the design of which is one of the key innovations of the aerodynamic structure 100. The air intake channel 401 leads to the axial position of the power impeller 2, providing an optimized path for gas to enter the power impeller 2. This design not only improves the efficiency of gas flow but also optimizes the distribution of gas around the power impeller 2, thereby improving the overall performance of the aerodynamic structure 100.

[0076] With its modular design, the first volute 3 and the second volute 4 can be assembled and replaced independently. This design is particularly suitable for pneumatic systems requiring high precision and high efficiency, such as the air-bearing motor system 1000. In practical applications, this modular design not only simplifies the assembly process but also reduces maintenance costs and improves the reliability and maintainability of the system.

[0077] Please continue to refer to this. Figure 3 This application also provides an air-bearing motor system 1000, including an air-bearing high-speed motor 200 and the aforementioned pneumatic structure 100, wherein the pneumatic structure 100 is assembled on the air-bearing high-speed motor 200.

[0078] In this embodiment, by integrating the aforementioned pneumatic structure 100 into the air-bearing motor system 1000, not only are all the beneficial technical effects of the pneumatic structure 100 inherited, but the overall performance and application flexibility of the air-bearing motor system 1000 are further improved. The pneumatic structure 100, through optimizing the structure of the sealing plate 1 and the working impeller 2, enables direct measurement of the sealing gap, improving measurement efficiency and accuracy. This ensures more precise flow and pressure of the cooling gas, effectively enhancing the cooling effect of the air-bearing bearing and the stability of the system.

[0079] It should be noted that the air flotation motor system 1000 can be flexibly configured as a compressor or a blower according to actual needs; this embodiment is not limited to either. This versatility allows the system to adapt to a wider range of industrial applications, further enhancing its practicality and economy.

[0080] In some embodiments, the air bearing high-speed motor 200 includes a housing 5, a stator assembly 6 and a rotating shaft 7, with the rotating shaft 7 assembled inside the stator assembly 6; the pneumatic structure 100 includes a first volute 3, with the first volute 3 and the sealing plate 1 both disposed in the housing 5, and the power impeller 2 disposed in the rotating shaft 7.

[0081] In this embodiment, the air bearing high-speed motor 200 is the core power component of the air bearing motor system 1000, and its structural design fully considers its integration and coordinated operation with the pneumatic structure 100. Specifically, the air bearing high-speed motor 200 consists of a housing 5, a stator assembly 6, and a rotating shaft 7, wherein the rotating shaft 7 is assembled inside the stator assembly 6 and supported by air bearings to achieve high-speed and stable rotation. This design not only ensures the efficient operation of the motor but also provides a stable power source for the pneumatic structure 100.

[0082] The integrated design of the pneumatic structure 100 and the high-speed motor 200 with the air bearing is one of the key innovations of this embodiment. The pneumatic structure 100 includes a first volute 3, which, along with the sealing plate 1, is mounted on the housing 5, while the power impeller 2 is mounted on the rotating shaft 7. This mounting relationship ensures that the airflow generated by the power impeller 2 during high-speed rotation can smoothly pass through the sealing gap and flow to the air bearing, thereby achieving effective cooling of the air bearing. Specifically, the power impeller 2 compresses and accelerates the gas during rotation, and the generated airflow passes through the sealing gap between its blade back and the sealing plate 1. The precise design of this gap allows the airflow to flow evenly and stably to the air bearing, carrying away the heat generated during its operation and ensuring the stability and reliability of the air bearing in high-temperature environments.

[0083] The airflow generated by the power impeller 2 flows directly to the air bearing after passing through the sealed gap. This path design fully utilizes the functional characteristics of the pneumatic structure 100, achieving a highly efficient cooling effect. By precisely controlling the size of the sealed gap, the airflow rate and pressure can be ensured to achieve the optimal cooling effect, while avoiding insufficient or excessive cooling caused by uneven airflow. This design not only improves the cooling efficiency of the system but also extends the service life of the air bearing, enhancing the stability and reliability of the entire air-bearing motor system 1000.

[0084] In some embodiments, the air flotation motor system 1000 further includes a second impeller 8, which is coaxially disposed at both ends of the rotating shaft 7 with the power impeller 2.

[0085] In this embodiment, the air-float motor system 1000 further extends its structure in some embodiments by introducing a second impeller 8, which is coaxially mounted at both ends of the rotating shaft 7 with the working impeller 2. This design makes the system more flexible and adaptable in function, and can meet the needs of different application scenarios. Since the air-float motor system 1000 in this embodiment is not limited to a compressor or a blower, the specific functions of the working impeller 2 and the second impeller 8 are not limited, which makes it possible for the system to be widely used in a variety of industrial applications.

[0086] The introduction of the second impeller 8 makes the air-float motor system 1000 more structurally symmetrical. This symmetry not only helps to balance the system's operation but also improves the overall efficiency of the system. In practical applications, the power impeller 2 and the second impeller 8 can each perform different tasks or work together to achieve specific functions. For example, one impeller can be used to compress gas, while the other impeller can be used to generate additional airflow for cooling or other auxiliary functions. This flexible configuration allows the system to be optimized and adjusted according to different needs, thereby achieving optimal performance in various industrial scenarios.

[0087] Because no specific functional limitations are imposed, the working impeller 2 and the second impeller 8 can be customized according to actual needs. This gives the air-float motor system 1000 extremely high versatility and adaptability, enabling it to easily cope with various complex industrial environments and diverse work tasks. Whether used as a compressor, blower, or other types of pneumatic equipment, the system can achieve efficient and stable operation by adjusting the impeller configuration and operating parameters. This high degree of flexibility and adaptability gives the air-float motor system 1000 a significant advantage in market competition, meeting the diverse needs of different users for pneumatic equipment.

[0088] In one specific embodiment, the air flotation motor system 1000 and its aerodynamic structure 100 are described below.

[0089] First, a sealing plate 1 is installed inside the housing 5. The sealing plate 1 has a through shaft hole 101 in its center, and a flat sealing surface 102 is formed on its first side. Next, a working impeller 2 is assembled into the shaft hole 101 of the sealing plate 1. The side of the working impeller 2 facing the sealing plate 1 is the blade back 201, forming a sealing gap between the blade back 201 and the sealing surface 102. Because the sealing surface 102 is a flat structure, the distance between the blade back 201 and the sealing surface 102 is equal everywhere, ensuring the uniformity of the sealing gap. A detection channel 202 is formed between the blade back 201 and the sealing surface 102, and a detection inlet 203 is formed between the tip of the blade back 201 and the sealing surface 102. The detection inlet 203 communicates with the detection channel 202, together forming the sealing gap measuring structure 204.

[0090] During assembly, the sealing gap between the impeller back 201 and the sealing surface 102 is directly measured using measuring tools such as feeler gauges through the detection inlet 203 and detection channel 202. This direct measurement method simplifies the measurement process, improves measurement accuracy, and avoids the measurement errors and increased time costs caused by repeated impeller disassembly and assembly in traditional methods. The flat sealing surface 102 and uniform sealing gap design make the measurement process more stable and reliable, providing reliable data support for the optimized design and operation of the air-float motor system 1000.

[0091] Furthermore, the first volute 3 is assembled onto the sealing plate 1. The first volute 3 is provided with a spiral channel 301, which leads to the radial position of the working impeller 2. The extension 302 of the first volute 3 contacts the sealing surface 102, and the extension 302 is spaced apart from the working impeller 2 to form a ventilation channel 303, which leads to the sealing gap between the impeller back 201 and the sealing surface 102. This design allows the airflow generated by the working impeller 2 during high-speed rotation to flow through the ventilation channel 303 to the sealing gap, achieving a cooling effect on the air bearing.

[0092] Furthermore, the aerodynamic structure 100 also includes a second volute 4, which is assembled to the first volute 3. The second volute 4 is provided with an air intake channel 401, which leads to the axial position of the power impeller 2. This split design not only improves assembly flexibility but also facilitates subsequent maintenance and replacement. The air intake channel 401 provides an optimized path for gas to enter the power impeller 2, improving gas flow efficiency and optimizing gas distribution around the power impeller 2, thereby improving the overall performance of the aerodynamic structure 100.

[0093] In the air-bearing motor system 1000, the air-bearing high-speed motor 200 includes a housing 5, a stator assembly 6, and a rotating shaft 7, with the rotating shaft 7 installed inside the stator assembly 6. The pneumatic structure 100 is installed within the air-bearing high-speed motor 200, with the first volute 3 and the sealing plate 1 both located in the housing 5, and the power impeller 2 located on the rotating shaft 7. This integrated design allows the air-bearing motor system 1000 to not only inherit all the beneficial technical effects of the pneumatic structure 100, but also further enhance the overall performance and application flexibility of the system.

[0094] Furthermore, the air-float motor system 1000 also includes a second impeller 8, which is coaxially mounted at both ends of the rotating shaft 7 with the working impeller 2. This dual-impeller structure provides the system with greater functional flexibility and adaptability, meeting the needs of different application scenarios. Since there are no specific functional limitations, the working impeller 2 and the second impeller 8 can be customized according to actual needs, enabling the system to be widely used in various industrial applications. The introduction of the second impeller 8 makes the air-float motor system 1000 more structurally symmetrical. This symmetry not only helps to balance the system's operation but also improves the overall efficiency of the system. In practical applications, the working impeller 2 and the second impeller 8 can each perform different tasks or work together to achieve specific functions. For example, one impeller can be used to compress gas, while the other impeller can be used to generate additional airflow for cooling or other auxiliary functions. This flexible configuration allows the system to be optimized and adjusted according to different needs, thereby achieving optimal performance in various industrial scenarios.

[0095] As can be seen from the above detailed usage process, the pneumatic structure 100 and the air-float motor system 1000 of this application fully consider the requirements of measurement accuracy, cooling effect and multifunctionality in the design and use process. By optimizing the structure and assembly relationship of components such as the sealing plate 1, the working impeller 2, the first volute 3, and the second volute 4, efficient and stable operation is achieved, which provides strong support for the widespread use of the air-float motor system 1000 in a variety of industrial applications.

[0096] It should be noted that many of the components mentioned in this application are general standard parts or components known to those skilled in the art, and their structure and principle can be learned by those skilled in the art through technical manuals or through conventional experimental methods.

[0097] It should be noted that in this specification, relational terms such as first and second are used only to distinguish one entity from several other entities, and do not necessarily require or imply any such actual relationship or order between these entities.

[0098] The pneumatic structure and air-bearing motor system provided in this application have been described in detail above. Specific examples have been used to illustrate the principles and implementation methods of this application. The descriptions of the embodiments above are only for the purpose of helping to understand the method and core ideas of this application. It should be noted that those skilled in the art can make several improvements and modifications to this application without departing from the principles of this application, and these improvements and modifications also fall within the protection scope of the claims of this application.

Claims

1. A pneumatic structure, characterized by, include: A sealing plate has a through shaft hole in the middle, and a sealing surface is formed on the first side of the sealing plate; A working impeller is fitted into the shaft hole of the sealing plate. The side of the working impeller facing the sealing plate is the blade back, and there is a sealing gap between the blade back and the sealing surface. The sealing surface is configured as a flat structure, and the distance between the sealing surface and the blade back is equal everywhere; a detection channel is formed between the blade back and the sealing surface, and a detection inlet is formed between the tip of the blade back and the sealing surface, or a detection inlet is formed between the tip of the sealing surface and the blade back, and the detection inlet is connected to the detection channel to form a sealing gap measurement structure.

2. Aerodynamic structure according to claim 1, characterized in that, The radial dimension of the sealing plate is larger than the radial dimension of the working impeller, and the detection inlet is formed between the tip of the blade back and the sealing surface.

3. Aerodynamic structure according to claim 2, characterized in that, The sealing surface forms a pilot area beyond the tip of the blade back and within the tip of the sealing surface, and the pilot area is connected to the detection inlet.

4. The pneumatic structure of claim 1, wherein, The sealing surface and the blade back are circular in shape, and the sealing gap measuring structure is a three-dimensional hollow ring.

5. The aerodynamic structure of claim 1, wherein, It also includes a first volute, which is assembled to the sealing plate. The first volute is provided with a spiral channel leading to the radial position of the working impeller.

6. Aerodynamic structure according to claim 5, characterized in that, The first volute has an extension section that contacts the sealing surface and is spaced apart from the working impeller. An air passage is formed between the extension section and the working impeller, and the air passage leads to the sealing gap between the blade back and the sealing surface.

7. The aerodynamic structure of claim 5, wherein, It also includes a second volute, which is assembled on the first volute. The second volute is provided with an air intake channel leading to the axial position of the power impeller.

8. An air bearing motor system characterized by, It includes an air-bearing high-speed motor and a pneumatic structure as described in any one of claims 1 to 7, wherein the pneumatic structure is mounted on the air-bearing high-speed motor.

9. The air floatation motor system of claim 8, wherein, The air bearing high-speed motor includes a housing, a stator assembly, and a rotating shaft, with the rotating shaft assembled inside the stator assembly; The pneumatic structure includes a first volute, both the first volute and the sealing plate are disposed in the housing, and the power impeller is disposed on the rotating shaft.

10. The air floatation motor system of claim 9, wherein, It also includes a second impeller, which is coaxially disposed at both ends of the rotating shaft with the power impeller.

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