A device for testing magnetic seal assemblies

Abstract

The application discloses a device for testing magnetic sealing assembly, which comprises a shell provided with a hollow cavity, leakage detection openings arranged at two ends of the hollow cavity respectively, a main shaft arranged in the hollow cavity and driven to rotate by a driving assembly, a first assembly position arranged on the circumferential surface of one end of the main shaft, a sliding oil rotor coaxial with the main shaft and detachably connected to the other end of the main shaft, a second assembly position arranged on the circumferential surface of the sliding oil rotor, two magnetic sealing assemblies respectively arranged in the leakage detection openings at two ends of the hollow cavity, one of the two magnetic sealing assemblies arranged in the first assembly position and the other arranged in the second assembly position, the two magnetic sealing assemblies axially limited by limiting members, the outer sides of the two magnetic sealing assemblies respectively sealed with the inner wall of the hollow cavity, and the inner sides of the two magnetic sealing assemblies respectively sealed with the circumferential surface of the first assembly position and the circumferential surface of the second assembly position, so that the hollow cavity cooperates to form a sealing cavity to be tested, a medium opening communicated with the sealing cavity to be tested arranged on the shell, and the medium opening and the leakage detection opening connected with a leakage detection sensing unit to obtain leakage parameters. The application relates to the technical field of magnetic sealing devices.

Description

Technical Field

[0001] This invention relates to the field of magnetic seal leakage detection technology, and more specifically to an apparatus for testing magnetic seal components. Background Technology

[0002] Magnetic seals, as a key fundamental component of rotating shaft systems, are widely used in aero-engines, rocket turbopumps, long-endurance UAV propulsion systems, petrochemical pumps, and high-precision transmission equipment. Their function is to achieve media sealing, maintain stable system boundary pressure, and prevent the intrusion of external contaminants. Given that these devices generally operate under conditions requiring high speed, high load, and high reliability, magnetic seals have become a crucial factor determining the safety, stability, and engineering application level of the system.

[0003] As the application scale of magnetic seals continues to expand, higher requirements are placed on testing methods for product development, batch production verification, and service reliability assessment.

[0004] However, existing magnetic seal testing methods have the following shortcomings: First, the testing items are scattered. Existing methods mostly focus on single parameter verification. They can usually only perform static leakage checks or only test components with fixed size and structure. It is difficult to achieve a comprehensive evaluation of leakage rate, pressure decay capacity and O-ring traction friction torque under rotation at the same time. Second, the fit of the working conditions is low. Most of the existing testing tools use regular cylindrical cavities or simplified planar cavities, ignoring the curved transitions, local volume changes and complex flow areas in the inner cavity of the engine shaft end, resulting in a deviation between the ground testing state and the actual service state. Third, the clamping efficiency and repeatability are insufficient. Traditional testing fixtures have a large number of parts, long assembly chains, and a high degree of dependence on special tools. In the process of batch testing, differences in manual assembly can easily cause inconsistencies in positioning, affecting the repeatability and reliability of the test results. Fourth, there is a lack of quantitative detection methods for the rotational friction torque of O-rings. Currently, there is no specific verification method for the traction friction torque of the O-ring at the coupling end under rotational conditions, making it difficult to accurately determine the rationality of the relationship between the O-ring compression ratio, frictional resistance, and structural matching. Summary of the Invention

[0005] The purpose of this invention is to solve the technical problems of existing magnetic seal testing devices, such as scattered testing items, low working condition fit, insufficient clamping efficiency, poor testing repeatability, and lack of quantitative testing methods for O-ring rotational friction torque.

[0006] To achieve the above objectives, the present invention adopts the following technical solution: An apparatus for testing magnetic seal components, comprising: The shell has a hollow cavity, and leak detection ports are respectively provided at both ends of the hollow cavity; The main shaft passes through the hollow cavity and is driven to rotate by the drive assembly; The main shaft has a first assembly position on one end of its circumferential surface and a coaxial lubricating rotor detachably connected to the other end. The lubricating rotor has a second assembly position on its circumferential surface. The magnetic sealing assembly can be inserted into the leak detection ports at both ends of the hollow cavity, with one fitting at the first assembly position and the other fitting at the second assembly position. The two magnetic sealing components are axially limited by the limiting members, and the outer side forms a sealing pair with the inner wall of the hollow cavity and the inner side forms a sealing pair with the first assembly position peripheral surface and the second assembly position peripheral surface, so that the hollow cavity fits to form the tested sealing cavity. The housing is also provided with a medium port that communicates with the sealed cavity being tested; The medium port and leak detection port are used to connect to the leak detection sensing unit to obtain leak parameters.

[0007] Preferably, the hollow cavity is an irregular curved surface cavity, and the inner wall of the irregular curved surface cavity has a curved transition, a step and a groove structure.

[0008] Preferably, the circumferential surface portion of the lubricating oil rotor located within the hollow cavity is provided with an oil slinger groove, one end of which has an axial opening, and the other end extends radially and has a radial opening.

[0009] Preferably, the hollow cavity is further provided with an oil return groove, an oil return port is provided on the inner side of the oil return groove, the oil return port is close to the radial opening of the oil slinger groove, and the outer side of the oil return groove extends radially outward.

[0010] Preferably, the main shaft is a stepped shaft, which includes a first assembly section, a connecting section and a threaded section in sequence along the axial direction, and the diameters of the first assembly section, the connecting section and the threaded section decrease in sequence. The hollow cavity is provided with a bearing block, and the main shaft is rotatably supported in the hollow cavity through the bearing block; The lubricating oil rotor is provided with a bushing, and the lubricating oil rotor is screwed into the external thread of the threaded section through the internal thread, and the bushing is sleeved on the connecting section.

[0011] Preferably, the first assembly section is provided with a first annular groove; The magnetic sealing assembly located at the first assembly position has a rotating ring sleeved in the first ring groove. A first sealing ring is provided between the inner circumference of the rotating ring and the wall of the first ring groove. The rotating ring has an inwardly extending limiting flange that abuts against the bottom end face of the first ring groove. A second sealing ring is provided between the outer periphery of the stationary ring of the magnetic sealing assembly and the inner wall of the hollow cavity; The hollow cavity is also provided with a first retaining ring, which abuts against the end face of the stationary ring near the corresponding leak detection port.

[0012] Preferably, the end of the lubricating rotor near the second assembly position is provided with a second annular groove; The magnetic sealing assembly located in the second assembly position has a rotating ring sleeved in the second annular groove. A third sealing ring is provided between the inner circumference of the rotating ring and the wall of the second annular groove. The rotating ring has an inwardly extending limiting flange that abuts against the bottom end face of the second annular groove. A fourth sealing ring is provided between the outer periphery of the stationary ring of the magnetic sealing assembly and the inner wall of the hollow cavity; The hollow cavity is also provided with a second retaining spring, which abuts against the end face of the stationary ring near the corresponding leak detection port.

[0013] Preferably, a fifth sealing ring is provided between the inner circumference of the bushing and the outer circumference of the connecting section, and between the inner circumference of the lubricating rotor and the outer circumference of the threaded section.

[0014] Preferably, the drive assembly includes a drive motor and a torque detection unit, and the output shaft of the drive motor is connected to the extended end of the main shaft via a coupling.

[0015] The beneficial effects of this invention are: (1) Traditional regular cylindrical cavities or simplified cavities usually ignore the curved transitions, local volume changes and potential leakage boundaries in the inner cavity of the engine shaft end, resulting in inconsistencies between the ground inspection state and the actual service state. This invention employs a non-circular curved cavity adapted to the internal cavity of an actual engine shaft end. This allows for the accurate replication of key spatial boundaries, pressure boundaries, and media distribution conditions after the magnetic seal assembly is installed. This ensures that test results such as leakage rate and pressure attenuation rate more accurately reflect the actual sealing capability of the seal in a complex internal cavity environment, reducing misjudgments caused by oversimplification of the test boundaries. Simultaneously, by effectively controlling the ineffective volume within the cavity, the ineffective volume compression rate meets practical application requirements, thereby improving test sensitivity and data reliability.

[0016] (2) The special oil-throwing grooves on the irregularly shaped lubricating rotor have the functions of guiding oil, throwing oil, and changing the local medium distribution state in actual operation. Their geometry and spatial position directly affect the sealing boundary conditions around the rotor. This invention, by retaining or mimicking the shape of the oil slinger groove, allows the leak detection process to closely approximate the media distribution characteristics and local pressure conditions during actual operation. The detection process not only reflects the sealing status of the rotor's outer contour but also the influence of the oil slinger groove area on the media flow path, local oil accumulation space, and pressure boundary conditions. Compared to traditional leak detection methods that use regular replacement structures, this invention can more realistically expose sealing weaknesses in potentially leak-sensitive areas such as the edges of the oil slinger groove and curved transition zones, thereby improving leak detection accuracy and engineering application value.

[0017] (3) Traditional sealing testing devices have many parts, complex installation procedures, and a high degree of dependence on special tools. In batch testing, differences in manual assembly can easily lead to inconsistent positioning, affecting the repeatability and reliability of the test results. This invention integrates the installation, positioning, and locking functions of the spindle and lubricating rotor into a single assembly relationship. Quick clamping and stable locking are achieved through threaded engagement, eliminating the need for additional clamping or auxiliary positioning components. This structure significantly simplifies the clamping process, shortens test preparation time, reduces operational complexity and reliance on manual experience, and minimizes test fluctuations caused by assembly errors and clamping deviations. It ensures that the magnetic seal assembly is under consistent installation boundary conditions during each test, thereby improving test repeatability and reliability. It is suitable for rapid leak detection and quality consistency evaluation of large-volume magnetic seal products. Furthermore, this invention adopts a modular design approach. When the shaft diameter, sealing groove size, or structural parameters of the magnetic seal assembly under test change, only the corresponding specifications of the spindle, lubricating rotor, or adapting bushing need to be replaced, without significant reconstruction of the base, bearing block, cavity, or other basic structures, thus possessing excellent versatility and expandability.

[0018] (4) Existing testing devices can usually only test a single set of magnetic sealing components one by one. The testing process requires repeated steps such as clamping, seal establishment, pressure stabilization and data acquisition. The waiting time for a single component is long and the overall testing cycle is low. Moreover, when different components are tested in batches, they are easily affected by differences in clamping status, environmental conditions and manual operation, which is not conducive to consistency evaluation and horizontal comparison. This invention utilizes a dual-station parallel testing structure to enable two sets of magnetic sealing assemblies to simultaneously complete clamping, seal establishment, pressure loading, leakage rate detection, and pressure decay detection under identical or controllable testing conditions. This not only reduces the time spent on repetitive waiting and multiple preparations for individual components but also allows for the acquisition of testing data for both sets of assemblies within the same testing cycle. This facilitates simultaneous comparative analysis of samples from the same batch, with different structural designs, or before and after optimization. Simultaneously, this device retains the independent testing function for each magnetic sealing assembly, allowing for flexible switching between single-station and dual-station testing modes as needed. Therefore, this invention improves testing efficiency, consistency, and data comparability, making it suitable for rapid screening of large batches of magnetic sealing assemblies, quality consistency evaluation, and performance comparison verification during the R&D phase.

[0019] (5) Existing magnetic seal testing methods mostly focus on static or quasi-static leakage performance testing. There is a lack of specialized quantitative testing methods for the traction torque generated by the O-ring during rotation due to compression fit, contact friction and rotational action. It is difficult to accurately determine the rationality of the relationship between O-ring compression ratio, frictional resistance and structural matching. In this invention, the main shaft is connected to the motor via a coupling. The motor drives the main shaft and the magnetic seal rotating ring assembly to rotate, simulating the actual working state. During the testing process, the output torque of the motor, the actual operating torque of the system, and the transmission resistance torque under no-load or reference conditions are collected. After deducting the resistance of the transmission components such as the main shaft, coupling, and bearings, the traction friction torque of the O-ring at the coupling end on the rotating rotating ring assembly is calculated. Then, the friction power of the O-ring is calculated in combination with the rotational speed parameters, thereby realizing the quantitative evaluation of the rotational friction characteristics of the O-ring. If the O-ring compression ratio is too high, it will lead to increased traction torque, increased friction power, accelerated wear, and increased drive load; if the compression ratio is insufficient, the sealing stability will decrease and the risk of leakage will increase. This invention can identify the above problems in advance through torque detection results, thereby avoiding design deviations caused by relying solely on experience for selection or single leakage detection. It integrates leakage performance detection and friction torque detection on the same tooling platform, so that the detection device can not only determine whether the leakage index meets the requirements, but also further analyze whether the friction matching under rotation is reasonable. This makes up for the shortcomings of existing tooling in that it is difficult to evaluate sealing performance and O-ring rotational friction characteristics at the same time, and improves the completeness, pertinence, and engineering practicality of the performance verification of magnetic sealing components. Attached Figure Description

[0020] Figure 1 A schematic diagram of the structure of the present invention is shown.

[0021] Figure 2 yes Figure 1 A schematic diagram of the structure of some components in an explosive state.

[0022] Figure 3 yes Figure 2A schematic diagram of the structure of some components in an explosive state.

[0023] Figure 4 This is a schematic diagram of the main shaft structure of the present invention.

[0024] Figure 5 This is a schematic diagram of the lubricating oil rotor structure of the present invention.

[0025] Figure 6 This is a schematic diagram illustrating the leak detection process of the present invention.

[0026] Figure 7 This is a schematic diagram illustrating the implementation of the friction torque detection method of the present invention. The figure shows: 1. Base; 2. Housing; 2.1. Hollow cavity; 2.11. Leak detection port; 2.12. Bearing seat; 2.2. Medium port; 2.3. Oil return groove; 2.31. Oil return port; 3. Main shaft; 3.1. First assembly section; 3.11. First assembly position; 3.2. Connecting section; 3.3. Threaded section; 4. Lubricating rotor; 4.1. Second assembly position; 4.11. Second annular groove; 5. Magnetic sealing assembly; 5.1. Moving ring; 5.11. Limiting flange; 5.2. Stationary ring; 6. Oil slinger groove; 6.1. Axial opening; 6.2. Radial opening; 7. Bearing block; 8. Bushing; 8.1. First annular groove; 9. First sealing ring; 10. Second sealing ring; 11. Third sealing ring; 12. Fourth sealing ring; 13. Fifth sealing ring; 14. Snap ring. Detailed Implementation

[0027] The present invention will be further described below with reference to the accompanying drawings and specific embodiments.

[0028] Example 1, please refer to Figure 1-6 As shown, the present invention provides a device for testing magnetic sealing components, comprising: a base 1, a housing 2, a main shaft 3, a lubricating oil rotor 4, two sets of magnetic sealing components 5, and a drive component.

[0029] The base 1 is a plate-shaped or frame-type structure. The housing 2 is fixedly installed on the base 1. The housing 2 has a hollow cavity 2.1 inside. Leak detection ports 2.11 are respectively provided at both ends of the hollow cavity 2.1. The main shaft 3 passes through the hollow cavity 2.1 and is driven to rotate by the drive assembly.

[0030] The main spindle 3 has a first assembly position 3.11 on one end of its circumference, and a coaxial lubricating rotor 4 is detachably connected to the other end. The lubricating rotor 4 has a second assembly position 4.1 on its circumference.

[0031] The magnetic sealing assembly 5 can be inserted from the leak detection ports 2.11 at both ends of the housing 2. One of them is fitted into the first assembly position 3.11 of the spindle 3, and the other is fitted into the second assembly position 4.1 of the lubricating rotor 4 to form a dual-station parallel detection structure.

[0032] The two magnetic sealing components 5 are axially limited by the limiting members, and the outer side forms a sealing pair with the inner wall of the hollow cavity 2.1 of the housing 2, and the inner side forms a sealing pair with the circumferential surface of the first assembly position 3.11 and the circumferential surface of the second assembly position 4.1, so that the hollow cavity 2.1 fits to form the sealed cavity to be tested.

[0033] The housing 2 is also provided with a medium port 2.2 communicating with the sealed cavity being tested. There are multiple medium ports 2.2, which may include an inlet for the medium to enter, an outlet for the medium to exit, and a connection port for installing a pressure gauge. In some embodiments, the leak detection sensing unit can be a pressure gauge, and the detection section of the pressure gauge is used to install at the connection port; Specifically: the leak detection medium (which can be gas, oil, etc.) is introduced into the inlet, and the outlet is sealed. If there is a medium leakage path in the magnetic sealing assembly 5 (mainly leakage between the sealing pair between the opposite end faces of the dynamic ring 5.1 and the stationary ring 5.2); After the medium has entered, if the pressure gauge reading is stable, it means that the two magnetic sealing components 5 are working properly. If the pressure gauge reading continues to change, usually decreasing, it indicates a leak. This allows for a quick assessment of the sealing performance of the two magnetic sealing components 5.

[0034] In some embodiments, the leak detection sensing unit can be a flow meter, etc. In use, an end cap can be installed on the leak detection port, and the flow meter can be installed on the end cap. If the flow meter has a reading, it means that medium is passing through, indicating a seal leak. The two flow meters can more quickly determine which side of the seal is leaking, achieving the verification effect more quickly and verifying whether the sealing performance of the magnetic sealing assembly 5 meets the standard, in order to obtain more accurate leakage parameters.

[0035] This embodiment utilizes a dual-station parallel testing structure to enable two sets of magnetic sealing assemblies 5 to simultaneously complete clamping, seal establishment, pressure loading, and leakage detection under the same or controllable testing conditions. This not only reduces the time spent on repeated waiting and preparation for individual components but also allows for the acquisition of testing data for both sets of components within the same testing cycle. This facilitates simultaneous comparative analysis of samples from the same batch of products, different structural schemes, or before and after optimization, thereby improving testing efficiency, consistency, and data comparability. It is particularly suitable for rapid screening, quality consistency evaluation, and performance comparison verification during the R&D phase of large-scale magnetic sealing assemblies 5.

[0036] Example 2, please refer to Figure 6 As shown, this embodiment further defines the hollow cavity 2.1 of the shell 2 based on embodiment 1.

[0037] Hollow cavity 2.1 is an irregular curved surface cavity. The inner wall of the irregular curved surface cavity has curved transition, step and groove structure. The inner wall of the irregular curved surface cavity is modeled after the curved surface contour of the actual engine shaft end cavity. The internal structure has key spatial boundaries, pressure boundaries and medium distribution conditions that simulate the actual engine shaft end cavity.

[0038] like Figure 1 and Figure 2 As shown, the shell 2 has an overall external outline that is approximately rectangular or octagonal, and the internal cavity has an irregular curved inner wall. Traditional regular cylindrical cavity, planar cavity or simplified cavity type testing tooling usually ignores the curved transition, local volume change, complex flow area and potential leakage boundary in the inner cavity of the engine shaft end, which can easily cause the ground test state to be inconsistent with the actual service state, thereby affecting the accuracy of leakage performance evaluation and engineering reference value.

[0039] This embodiment uses an irregularly shaped curved cavity to simulate and constrain the distribution space, pressure application area, and leakage path of the test medium, enabling the magnetic seal assembly 5 to complete leakage performance testing under internal cavity boundary conditions close to the actual installed state. The test results, such as leakage rate and pressure attenuation rate, can more realistically reflect the sealing capability of the magnetic seal in the complex internal cavity environment of the engine shaft end, reducing misjudgments caused by oversimplification of the test boundary. This structure is particularly suitable for ground simulation verification of magnetic seals at the shaft end of aero-engines, allowing for the early identification of weak sealing areas before overall assembly or testing, reducing testing costs and verification cycles.

[0040] Example 3, please refer to Figure 2-6 As shown, this embodiment further defines the lubricating oil rotor 4 and housing 2 based on embodiment 2.

[0041] The lubricating oil rotor 4 is provided with an oil slinger 6 on the circumferential surface of the hollow cavity 2.1. One end of the oil slinger 6 is provided with an axial opening 6.1, and the other end extends radially and is provided with a radial opening 6.2. During the rotation of the lubricating oil rotor 4 with the main shaft 3, oil enters through the axial opening 6.1 and is thrown out through the radial opening 6.2.

[0042] like Figure 5 As shown, the structure of the oil slinger 6 is modeled after the oil slinger 6 of the actual engine shaft-end lubricating rotor 4, which can reproduce the oil guiding, oil slinging, and local medium distribution state during actual operation. Since the special oil slinger 6 on the irregularly shaped lubricating rotor 4 has the functions of guiding oil, slinging oil, and changing the local medium distribution state during actual operation, its geometry and spatial position will directly affect the sealing boundary conditions around the rotor.

[0043] This embodiment retains or replicates the shape of the special oil-throwing groove 6, allowing the leak detection process to more closely resemble the media distribution characteristics and local pressure conditions during actual operation, thereby improving the ability of the test results to reflect actual operating conditions. Compared with traditional leak detection methods that use regular replacement structures or simplify sealing boundaries, this embodiment can make the leak detection state closer to the actual service conditions of the irregular-shaped lubricating oil rotor 4, improving the representativeness of the test conditions and the consistency between the leak detection results and the actual use conditions. Especially for potentially leak-sensitive areas such as the edges of the oil-throwing groove 6, curved transition areas, and local convex-concave connection areas, this embodiment can more realistically expose weak sealing points, reducing misjudgments and leaks caused by structural simplification, thereby improving the accuracy, repeatability, and engineering application value of leak detection.

[0044] In addition, the hollow cavity 2.1 is also provided with an oil return groove 2.3, and an oil return port 2.31 is provided on the inner side of the oil return groove 2.3. The oil return port 2.31 is close to the radial opening 6.2 of the oil slinger 6. The outer side of the oil return groove 2.3 extends radially outward and leads to the outside of the shell 2. The oil return groove 2.3 is designed to collect the detection medium thrown out from the oil slinger 6 and discharge it outward through the oil return port 2.31. It is then received and thrown out by the oil slinger 6, so that the detection medium is concentrated in the vicinity of the oil slinger 6. The structure allows the detection medium to be recycled between the two structures, while maintaining the stability of the detection environment.

[0045] Example 4, please refer to Figure 2-6 As shown, this embodiment further defines the main shaft 3, the lubricating rotor 4, and the bearing block 7 based on embodiment one.

[0046] The main shaft 3 is a stepped shaft, consisting of a first assembly section 3.1, a connecting section 3.2, and a threaded section 3.3 arranged axially from front to back, with the diameters of the first assembly section 3.1, connecting section 3.2, and threaded section 3.3 decreasing sequentially. The sections of the main shaft 3 are connected by shoulders. The protruding end of the main shaft 3 (i.e., the front end of the first assembly section 3.1) extends beyond the housing 2 and is used to connect to the drive assembly via a coupling. The first assembly section 3.1, located at the very front (left) of the main shaft 3, has the largest outer diameter and is used to install the stationary ring 5.2 of the magnetic seal assembly 5. The connecting section 3.2, located behind the first assembly section 3.1, has a smaller diameter than the first assembly section 3.1 and is used to fit the bushing 8 and mate with the inner hole of the bearing block 7. The threaded section 3.3, located behind the connecting section 3.2, has the smallest diameter and external threads on its outer circumference, used to connect to the lubricating rotor 4.

[0047] The bearing block 7 can be a rolling bearing or a sliding bearing structure. Its outer ring is installed with the bearing seat 2.12 on the inner wall of the hollow cavity 2.1 of the housing 2 through an interference fit or a clearance fit. Its inner ring is fitted with the journal of the connecting section 3.2 of the spindle 3 to ensure the coaxiality and stability of the spindle 3 during rotation.

[0048] During assembly, a bushing 8 is first fitted onto the front of the connecting section 3.2. The threaded section 3.3 is inserted through the front of the inner hole of the bearing block 7 until the connecting section 3.2 is located within the inner hole of the bearing block 7, allowing the main shaft 3 to be rotatably supported by the bearing block 7. The lubricating rotor 4 has a sleeve-shaped structure with internal threads. These internal threads engage with the external threads of the threaded section 3.3 of the main shaft 3, and the bushing 8 locks the bearing in place. This achieves axial positioning of the bearing block 7 and a quick-locking series connection between the main shaft 3 and the lubricating rotor 4, enabling a detachable coaxial connection.

[0049] The installation, positioning, and locking functions of the spindle 3 and the lubricating rotor 4 are integrated into a single assembly. Operators only need to complete the thread engagement to establish a stable testing assembly state, which significantly simplifies the clamping process, shortens the test preparation time, reduces operational complexity and reliance on manual experience, and reduces test fluctuations caused by assembly errors and clamping deviations. This ensures that the magnetic seal assembly 5 is under consistent installation boundary conditions during each test, thereby improving test repeatability and reliability. It is suitable for rapid leakage detection and quality consistency evaluation of large-volume magnetic seal products. In addition, the detachable structure facilitates the replacement of suitable spindle 3 and lubricating rotor 4 to meet the testing needs of different types of magnetic seal assembly 5.

[0050] In this application, a radially inwardly protruding bearing seat 2.12 is provided inside the hollow cavity 2.1. The bearing seat 2.12 has multiple through holes extending from front to back, and multiple radially through grooves are provided between it and the oil return groove 2.3 for the passage of the detection medium. The bearing seat 2.12 and the oil return groove 2.3 have multiple structures with different diameters and contours to create more complex spatial boundaries, pressure boundaries, and medium distribution conditions.

[0051] Example 5, please refer to Figure 6 As shown, this embodiment further limits the limiting structure of the magnetic sealing component 5 based on embodiment four.

[0052] The first mating part of the first assembly section 3.1 is provided with a first annular groove 8.1, which is opened axially backward from the front end face of the first mating part. The magnetic sealing assembly 5 located at the first assembly position 3.11 has a moving ring 5.1 fitted inside the first annular groove 8.1. A first sealing ring 9 (O-ring) is provided between the inner circumference of the moving ring 5.1 and the wall surface of the first annular groove 8.1 to achieve radial sealing between the moving ring 5.1 and the main shaft 3. The moving ring 5.1 has an inwardly extending limiting flange 5.11, which is located in front of the first sealing ring 9 and can abut against the bottom end face of the first annular groove 8.1 to form an axial limiting fit and prevent the moving ring 5.1 from moving backward under axial force. A second sealing ring 10 (O-ring) is provided between the outer circumference of the stationary ring 5.2 of the magnetic sealing assembly 5 and the inner wall of the hollow cavity 2.1 to achieve radial sealing between the stationary ring 5.2 and the housing 2.

[0053] A second annular groove 4.11 is provided at the tail end (rear end) of the lubricating rotor 4 near the second assembly position 4.1. The second annular groove 4.11 is opened axially forward from the rear end face of the lubricating rotor 4. The magnetic sealing assembly 5 located at the second assembly position 4.1 has a moving ring 5.1 fitted inside the second annular groove 4.11. A third sealing ring 11 (O-ring) is provided between the inner circumference of the moving ring 5.1 and the wall of the second annular groove 4.11 to achieve radial sealing between the moving ring 5.1 and the lubricating rotor 4. The moving ring 5.1 has an inwardly extending limiting flange 5.11, which is located behind the third sealing ring 11 and can abut against the bottom end face of the second annular groove 4.11 to form an axial limiting fit. A fourth sealing ring 12 (O-ring) is provided between the outer circumference of the stationary ring 5.2 of the magnetic sealing assembly 5 and the inner wall of the hollow cavity 2.1.

[0054] The hollow cavity 2.1 is also provided with a retaining ring 14, which abuts against the end face of the stationary ring 5.2 near the leak detection port 2.11 to axially limit the stationary ring 5.2 and prevent it from moving towards the leak detection port 2.11 under the detection pressure.

[0055] This embodiment achieves radial sealing and axial limiting of the magnetic sealing assembly 5 through the cooperative structure of the annular groove, sealing ring and retaining spring 14. The clamping and positioning are accurate and the detection boundary is stable, which can significantly improve the detection repeatability and result consistency.

[0056] Example 6, please refer to Figure 6 As shown, this embodiment further limits the sealing between the main shaft 3 and the lubricating rotor 4, based on embodiment five.

[0057] A fifth sealing ring 13 (O-ring) is provided between the inner circumference of the bushing 8 and the outer circumference of the connecting section 3.2 to prevent the detection medium from leaking from the gap between the bushing 8 and the connecting section 3.2; a fifth sealing ring 13 (O-ring) is also provided between the inner circumference of the lubricating rotor 4 and the outer circumference of the threaded section 3.3 to prevent the detection medium from leaking from the threaded gap between the lubricating rotor 4 and the threaded section 3.3.

[0058] This embodiment ensures the boundary integrity of the tested sealing cavity by setting the fifth sealing ring 13, avoids leakage in non-tested areas from interfering with the test results, and enables the leakage detection data to truly reflect the sealing performance of the magnetic sealing component 5 itself, rather than false signals caused by leakage in the fitting gap, thereby improving the accuracy and reliability of the test data.

[0059] Example 7, please refer to Figure 7 As shown, this embodiment further defines the driving component based on embodiment one.

[0060] It also includes a drive assembly, which includes a drive motor and a torque detection unit. The output shaft of the drive motor is connected to the extended end of the main shaft 3 via a coupling.

[0061] The torque detection unit can be a torque and speed sensor, etc., used to collect the system operating torque during the rotation of the spindle 3 in real time; or the motor output torque can be obtained by converting the torque feedback signal or motor current signal of the servo motor driver.

[0062] Before testing, without O-rings installed, without O-rings compressed, or under other no-load / reference conditions, spindle 3 is run at the same speed to collect the reference resistance torque generated by the spindle 3, coupling, bearings and other transmission components.

[0063] During formal testing, after the magnetic sealing assembly 5 and the O-ring are installed in the actual assembly and compression state, the system operating torque is collected. The reference resistance torque is then subtracted from the system operating torque to obtain the traction friction torque generated by the O-ring at the coupling end on the rotating moving ring 5.1 assembly.

[0064] The torque detection unit is used to collect the output torque of the motor. After deducting the resistance of the transmission components such as the main shaft 3, coupling, and bearing block 7, the traction friction torque generated by the O-ring on the rotating ring 5.1 assembly can be calculated.

[0065] By combining the rotational speed parameters, the frictional power of the O-ring can also be calculated, thereby evaluating the O-ring's compression ratio, frictional characteristics, and model matching.

[0066] This embodiment integrates magnetic seal leakage performance testing and O-ring traction friction torque testing on the same tooling platform, enabling the testing device to not only determine whether the magnetic seal meets the leakage index, but also to further analyze whether its friction matching under rotation is reasonable.

[0067] Through the above testing methods, this embodiment can evaluate the frictional resistance and energy loss of O-rings under actual assembly compression conditions, providing data basis for O-ring compression ratio verification, cross-sectional size selection, material hardness matching, and model optimization.

[0068] If the O-ring compression ratio is too high, it may lead to increased traction torque, increased friction power, accelerated wear, and increased drive load; if the compression ratio is insufficient, it may cause a decrease in sealing stability and an increased risk of leakage.

[0069] This embodiment can identify the above problems in advance through torque detection results, thereby avoiding design deviations caused by relying solely on experience-based selection or single leak detection.

[0070] This structure overcomes the shortcomings of existing testing fixtures that make it difficult to simultaneously evaluate sealing performance and O-ring rotational friction characteristics, thereby improving the completeness, relevance, and engineering practicality of the performance verification of the magnetic sealing assembly 5.

[0071] In some embodiments, the device performs detection according to the following steps: Step 1: Insert the main shaft 3 into the hollow cavity 2.1 through the leak detection port 2.11 at one end of the housing 2, so that the main shaft 3 is rotatably supported in the hollow cavity 2.1 by the bearing block 7; fit the bushing 8 onto the connecting section 3.2 of the main shaft 3; screw the lubricating rotor 4 into the threaded end (rear end) of the main shaft 3, and through the engagement of the internal and external threads, make the lubricating rotor 4 coaxially connected with the main shaft 3, and tighten it until the front end face of the lubricating rotor 4 abuts against the bearing block 7, thereby achieving axial positioning of the bearing block 7; insert the magnetic sealing assembly 5 of the first assembly position 3.11 into the leak detection port 2.11 at the front end of the housing 2, so that the moving ring 5.1 is embedded in the first ring groove 8.1, and the outer circumference of the stationary ring 5.2 is in contact with the hollow cavity. 2.1 The inner wall is fitted, and the first retaining ring 14 is installed to limit the stationary ring 5.2; the magnetic sealing assembly 5 of the second assembly position 4.1 is inserted into the leak detection port 2.11 at the rear end of the housing 2, so that the moving ring 5.1 is embedded in the second ring groove 4.11, and the outer circumference of the stationary ring 5.2 fits with the inner wall of the hollow cavity 2.1, and the second retaining ring 14 is installed to limit the stationary ring 5.2; each sealing ring (first sealing ring 9, second sealing ring 10, third sealing ring 11, fourth sealing ring 12, fifth sealing ring 13) is installed; the housing 2 is fixedly installed on the base 1; the drive assembly is connected to the protruding end of the main shaft 3 through a coupling; the leak detection port 2.11 is connected to the leak detection sensing unit to complete the assembly. If dual-station detection is used, the installation of two sets of magnetic sealing assemblies 5 is completed simultaneously.

[0072] Step 2: Inject the test medium into the tested sealing cavity (first sealing cavity and / or second sealing cavity) through the air inlet until the pressure inside the tested sealing cavity reaches the specified pressure. The pressure change is monitored in real time by the leakage detection sensing unit to obtain the leakage rate and / or pressure decay rate. During the test, the irregular curved surface cavity simulates the key spatial boundaries, pressure boundaries, and medium distribution conditions of the actual engine shaft end cavity. The oil slinger 6 area of ​​the irregular lubricating oil rotor 4 reproduces the local medium flow path and oil accumulation space under actual working conditions, thus enabling the leakage detection results to more realistically reflect the sealing performance of the magnetic sealing assembly 5 under actual installed conditions.

[0073] Step 3: Start the drive motor to rotate the main shaft 3 and the lubricating rotor 4 via the coupling, simulating the rotational state of the magnetic seal assembly 5 in actual operation. The torque signal of the rotating ring 5.1 assembly is detected by the torque detection unit. After subtracting the resistance torque of the transmission components, the traction friction torque generated by the O-ring at the coupling end on the rotating ring 5.1 assembly is obtained. If a speed detection unit is configured, the O-ring friction power is calculated based on the speed parameters, thereby achieving a quantitative evaluation of the O-ring's rotational friction characteristics.

[0074] Step 4: Based on the leakage rate and / or pressure attenuation rate, as well as the traction friction torque, a comprehensive evaluation is performed on the leakage performance of the magnetic sealing assembly 5 and the traction friction performance of the O-ring at the coupling end. If the O-ring compression ratio is too high, it will lead to increased traction torque, increased friction power, accelerated wear, and increased drive load; if the compression ratio is insufficient, the sealing stability will decrease, and the risk of leakage will increase. The detection device of this invention can identify these problems in advance, thereby providing data for O-ring compression ratio verification, cross-sectional size selection, material hardness matching, and model optimization.

[0075] The above are merely preferred embodiments of the present invention. The scope of protection of the present invention is not limited to the above embodiments. All technical solutions falling within the scope of the present invention's concept are within the scope of protection of the present invention. It should be noted that for those skilled in the art, any improvements and modifications made without departing from the principle of the present invention should also be considered within the scope of protection of the present invention.

Claims

1. An apparatus for testing magnetic sealing components, characterized in that, include: The shell (2) is provided with a hollow cavity (2.1), and leak detection ports (2.11) are respectively provided at both ends of the hollow cavity (2.1); The main shaft (3) is inserted into the hollow cavity (2.1) and is driven to rotate by the drive assembly; The main shaft (3) has a first assembly position (3.11) on one end of its circumferential surface and a coaxial lubricating rotor (4) detachably connected to the other end. The lubricating rotor (4) has a second assembly position (4.1) on its circumferential surface. The magnetic sealing assembly (5) can be inserted from the leak detection ports (2.11) at both ends of the hollow cavity (2.1), with one of them fitted in the first assembly position (3.11) and the other fitted in the second assembly position (4.1). The two magnetic sealing components (5) are axially limited by the limiting member, and the outer side forms a sealing pair with the inner wall of the hollow cavity (2.1), the inner side forms a sealing pair with the circumferential surface of the first assembly position (3.11) and the circumferential surface of the second assembly position (4.1), so that the hollow cavity (2.1) cooperates to form the sealed cavity to be tested; The housing (2) is also provided with a medium port (2.2) that communicates with the sealed cavity under test. The medium port (2.2) and leak detection port (2.11) can be used to connect a leak detection sensing unit to obtain leak parameters.

2. The apparatus for testing magnetic sealing components according to claim 1, characterized in that, The hollow cavity (2.1) is an irregular curved surface cavity, and the inner wall of the irregular curved surface cavity has a curved transition, a step and a groove structure.

3. The apparatus for testing magnetic sealing components according to claim 1, characterized in that, The lubricating rotor (4) has an oil slinger (6) on its circumferential surface within the hollow cavity (2.1). One end of the oil slinger (6) has an axial opening (6.1), and the other end extends radially and has a radial opening (6.2).

4. The apparatus for testing magnetic sealing components according to claim 3, characterized in that, The hollow cavity (2.1) is also provided with an oil return groove (2.3), and an oil return port (2.31) is provided on the inner side of the oil return groove (2.3). The oil return port (2.31) is close to the radial opening (6.2) of the oil slinger (6), and the outer side of the oil return groove (2.3) extends radially outward.

5. The apparatus for testing magnetic sealing components according to claim 1, characterized in that, The main shaft (3) is a stepped shaft, which includes a first assembly section (3.1), a connecting section (3.2) and a threaded section (3.3) from front to back, and the diameters of the first assembly section (3.1), the connecting section (3.2) and the threaded section (3.3) decrease sequentially. The hollow cavity (2.1) is provided with a bearing block (7). A bushing (8) is fitted at the front end of the connecting section (3.2). The threaded section (3.3) extends from the front of the inner hole of the bearing block (7) to the connecting section (3.2) located within the inner hole of the bearing block (7). The lubricating rotor (4) engages with the external thread of the threaded section (3.3) through its internal thread, and locks the bearing with the bushing (8).

6. The apparatus for testing magnetic sealing components according to claim 5, characterized in that, The bushing (8) is provided with a first annular groove (8.1) extending from front to back. The magnetic sealing assembly (5) located at the first assembly position (3.11) has a moving ring (5.1) sleeved in the first ring groove (8.1). A first sealing ring (9) is provided between the inner circumference of the moving ring (5.1) and the wall of the first ring groove (8.1). The moving ring (5.1) has an inwardly extending limiting flange (5.11) in front of the first sealing ring (9). A second sealing ring (10) is provided between the outer periphery of the stationary ring (5.2) of the magnetic sealing assembly (5) and the inner wall of the hollow cavity (2.1).

7. The apparatus for testing magnetic sealing components according to claim 6, characterized in that, The lubricating rotor (4) has a second annular groove (4.11) that is opened from back to front at the end near the second assembly position (4.1). The magnetic sealing assembly (5) located in the second assembly position (4.1) has a moving ring (5.1) sleeved in the second ring groove (4.11). A third sealing ring (11) is provided between the inner circumference of the moving ring (5.1) and the wall of the second ring groove (4.11). The moving ring (5.1) has an inwardly extending limiting flange (5.11) behind the third sealing ring (11). A fourth sealing ring (12) is provided between the outer periphery of the stationary ring (5.2) of the magnetic sealing assembly (5) and the inner wall of the hollow cavity (2.1).

8. The apparatus for testing magnetic sealing components according to claim 7, characterized in that, The hollow cavity (2.1) is also provided with a retaining ring (14), which abuts against the end face of the stationary ring (5.2) on the side near the corresponding leak detection port (2.11).

9. The apparatus for testing magnetic sealing components according to claim 5, characterized in that, A fifth sealing ring (13) is provided between the inner circumference of the bushing (8) and the outer circumference of the connecting section (3.2), and between the inner circumference of the lubricating rotor (4) and the outer circumference of the threaded section (3.3).

10. The apparatus for testing magnetic sealing components according to claim 1, characterized in that, The drive assembly includes a drive motor and a torque detection unit, and the output shaft of the drive motor is connected to the extended end of the main shaft (3) via a coupling.

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