A kind of shroud baffle disc strength test structure of rim positioning bolt connection
By designing a test wheel to simulate the engine's working state, the high cost and complexity of strength testing for the sealing gear disc of an aero-engine were solved, achieving efficient and low-cost strength testing.
Patent Information
- Authority / Receiving Office
- CN · China
- Patent Type
- Patents(China)
- Current Assignee / Owner
- AECC SHENYANG ENGINE RES INST
- Filing Date
- 2022-11-18
- Publication Date
- 2026-07-21
AI Technical Summary
Existing strength tests for sealing grates of aero-engines require multi-stage grates, resulting in complex test designs, high costs, and insufficient assessment. Furthermore, the grates cannot be reused after the test.
A test wheel is used instead of other engine components connected to the test wheel. The structural dimensions and materials of the test wheel are designed to simulate the engine's working state, and rotation and heating tests are conducted. Inexpensive materials and simple processes are used to reduce test costs.
It reduces the number of test pieces, simplifies assembly and inspection, lowers testing costs, and effectively simulates engine operating conditions, thus improving testing efficiency.
Smart Images
Figure CN115655922B_ABST
Abstract
Description
Technical Field
[0001] This application belongs to the field of aero-engine technology, and specifically relates to a strength test structure for a sealing toothed disc with a disc rim positioning bolt connection. Background Technology
[0002] High-pressure compressors and high-pressure turbines of aero engines are often sealed with sealing gratings. They have two main functions: first, to seal the gas in the flow channel and reduce engine performance loss; and second, to regulate the pressure in each cavity of the grating so that the axial force of the engine is within a suitable range.
[0003] Common aero-engine sealing grate structure such as Figure 1 As shown, when the sealing grate disc has axial positioning at its edge, and the sealing grate disc is bolted to other components, such as... Figure 1 As shown in Figures b and c, in addition to centrifugal loads, temperature loads, and aerodynamic pressure loads within the disk cavity, the sealing grate also experiences axial bending stress caused by the initial assembly of the disk rim and bolt connections. To ensure adequate assessment during the sealing grate strength test, it is essential to simulate the axial bending stress caused by the initial assembly.
[0004] In existing technologies, strength tests on sealing grate discs typically employ rotors containing multi-stage discs. However, this method requires the inclusion of other engine disc components connected to the sealing grate disc, resulting in a large number of test components and complex design, assembly, and loading / adjustment processes. This leads to lengthy assembly, disassembly, and inspection processes before, during, and after the test, consuming significant manpower and resources. Furthermore, the discs must be scrapped after the strength test, resulting in high testing costs. Without the inclusion of other engine disc components connected to the sealing grate disc, the test cannot achieve its intended purpose of thorough evaluation. Summary of the Invention
[0005] The purpose of this application is to provide a strength test structure for a sealing toothed disc with a flange positioning bolt connection, in order to solve or mitigate at least one of the problems in the prior art.
[0006] The technical solution of this application is: a strength test structure for a sealing toothed disc with a positioning bolt connection at the disc rim, comprising:
[0007] Assessment Roulette;
[0008] The roulette wheel for the test takers;
[0009] The test wheel and the auxiliary test wheel are connected by connecting bolts and nuts. A sleeve is provided between the test wheel and the auxiliary test wheel. The auxiliary test wheel is connected to the drive device via a drive shaft. The test wheel, connecting bolts, and sleeve are actual engine components. The structural dimensions of the auxiliary test wheel are configured to simulate the fit between the engine and the test wheel under engine operating conditions.
[0010] A heating device and a test protection device are installed on the outside of the test wheel. The strength test of the sealing grate disc is carried out in a rotating and heated environment. The drive device controls the transfer drive shaft to drive the test wheel and the test wheel to rotate. The heating device forms a temperature field to heat the test wheel and the test wheel. The test protection device prevents the test wheel and the test wheel from breaking and flying out.
[0011] Furthermore, the structural dimension configuration process of the test wheel includes:
[0012] The material of the test wheel is determined according to the type of strength test for the sealed toothed disc;
[0013] Based on the assembly relationship between the test wheel and the adjacent test wheel, determine the key assembly dimensions of the test wheel in its initial state.
[0014] Based on the deformation of the test wheel disc under engine operating conditions, determine the key deformation dimensions related to the deformation of the test wheel disc to ensure that the support stiffness of the test wheel disc under test conditions is consistent with the support stiffness of the test wheel disc under actual engine conditions.
[0015] Based on the fact that the maximum stress of the test wheel is located in the center region of the wheel under rotation, the key stress dimensions that affect the strength of the test wheel are determined so that the strength of the test wheel does not fail during the test.
[0016] By performing deformation calculations on the combination of the test wheel and the test wheel, the key deformation dimensions of the test wheel are controlled to ensure that the axial deformation of the test wheel's edge deformation extraction point is consistent with the engine's operating state. By performing stress calculations on the combination of the test wheel and the test wheel, the key stress dimensions of the test wheel are controlled to ensure that the stress of the test wheel is within the range required by the engine's strength specifications, thereby obtaining the structural dimensions of the test wheel that meet the requirements.
[0017] Furthermore, if the sealing grate strength test is a compressor rotor strength test, the test wheel is made of stainless steel; if the sealing grate strength test is a turbine rotor strength test, the test wheel is made of high-temperature alloy.
[0018] Furthermore, the key assembly dimensions of the test wheel include: the distance P1 from the outermost mating point of the test wheel and the test wheel to the engine axis, the width P2 of the mating surface of the test wheel rim, the axial distance P3 between the mating surface of the rim and the bolt mating surface, and the width P4 of the bolt mating surface of the test wheel.
[0019] Furthermore, the key assembly dimensions of the test wheel satisfy the following relationship:
[0020] P1 = L1, P2 > L2, P4 > L3
[0021] In the formula, L1 is the distance from the outermost mating point of the test wheel and the auxiliary test wheel to the engine axis;
[0022] L2 is the width of the mating surface of the rim of the test wheel;
[0023] L3 is the width of the bolt mating surface of the test wheel.
[0024] Furthermore, the key dimensions for deformation of the test wheel include: the width of the support portion P5 and the radial length of the support portion P6.
[0025] Furthermore, the key stress dimensions of the test wheel include: the wheel center radius dimension P9, the wheel hub width dimension P7, and the wheel hub height dimension P8.
[0026] Furthermore, the extraction point of the disk edge deformation is the outer endpoint of the mating surface of the test disk and the assessment disk.
[0027] The sealing toothed disc strength test structure with flange positioning bolt connection proposed in this application can greatly reduce the number of auxiliary test parts by designing auxiliary test parts to replace several engine parts connected to the test disc. This greatly facilitates the assembly, disassembly and inspection work before, during and after the test, and improves work efficiency. The auxiliary test disc can be made of cheaper materials and can be processed with simpler technology, which greatly reduces the test cost. Attached Figure Description
[0028] To more clearly illustrate the technical solutions provided in this application, the accompanying drawings will be briefly described below. Obviously, the drawings described below are merely some embodiments of this application.
[0029] Figure 1 These are schematic diagrams of three typical aero-engine sealing grating structures.
[0030] Figure 2 This is a schematic diagram of the wheel disc strength test structure using actual engine components.
[0031] Figure 3 This is a schematic diagram of the test specimen structure for the test wheel using a test wheel in this application.
[0032] Figure 4 This is a schematic diagram of the experimental structure in this application.
[0033] Figure 5 This is a schematic diagram of the key dimensions of the test combination key and the test wheel in this application. Detailed Implementation
[0034] To make the objectives, technical solutions, and advantages of this application clearer, the technical solutions in the embodiments of this application will be described in more detail below with reference to the accompanying drawings.
[0035] To ensure the safety and reliability of the sealing grate disc (hereinafter referred to as the disc) under engine operating conditions, a strength test under the rotating state of the disc must be carried out during the engine design process to fully verify and assess the disc's strength.
[0036] like Figure 2 The diagram shows a schematic of a wheel strength test using real engine components. In the wheel test structure 10, the test wheel 11 and multiple real wheel discs 12a-12c are positioned by a stop. Sleeves 14a-14c are used between the wheel discs for distance limiting. Bolts 13 pass through the front mounting edge 16 and the rear mounting edge 17, and cooperate with nuts 15 to complete the assembly of the test wheel 11. In this assembly assembly, there are complex assembly relationships between the various real wheel discs 12a-12c. During operation, each wheel disc deforms and affects each other. When conducting a wheel rotation strength test, using multiple real wheel discs and assembling the test pieces according to engine assembly requirements can simulate the boundary conditions of the wheel. However, this test structure uses a large number of real engine components, especially multiple wheel discs. After the wheel strength test is completed, these real engine components cannot be reused for engine or other tests, resulting in excessively high test costs.
[0037] To address the aforementioned issues, this application proposes that when conducting strength tests on aircraft engine disks, the disk to be tested should be a real engine disk, while the disks that have an assembly relationship with the test disk should be replaced by specially designed auxiliary disks. The auxiliary disks should be designed with lower material prices and simpler processing technology to reduce test costs.
[0038] To ensure that the strength test conditions of the test wheel are consistent with those of the engine, and to fully verify and test the test wheel, the redesigned test wheel and the test wheel should be assembled in the same way as the engine. The deformation of the test wheel at the mating parts should be the same as the deformation of the engine under operating conditions, so as to accurately simulate the boundary conditions of the test wheel.
[0039] like Figure 3The diagram shows a new engine disc strength test structure provided in this application. The test disc 21, connecting bolts 23, and sleeve 24 are actual engine components, while the auxiliary test disc 22, nut 25, washer 26, and adapter drive shaft 27 are redesigned auxiliary test components. Nut 25 and washer 26 are designed according to the mating dimensions of the actual engine components, and adapter drive shaft 27 is designed according to the mating dimensions of auxiliary test disc 22 and the test apparatus. Since the deformation of the test disc 21 under working conditions is affected by initial assembly, centrifugal load, and temperature load, deformation occurs at the edge of the auxiliary test disc 22 and the bolt connection points. Therefore, it is necessary to determine the structural dimensions of the auxiliary test disc 22 to achieve this mating relationship.
[0040] like Figure 4 The diagram shows the overall scheme for the engine disc strength test provided in this application. The adapter drive shaft 27 is connected to the test disc 22 via a connector. The test disc 22 is connected to the test disc 21 via connecting bolts 23. A heating device 29 and a test protection device 28 are installed on the outside of the test disc 21. The disc strength test is conducted under rotation and heating conditions. The adapter drive shaft 27 drives the test disc 22 and the test disc 21 to rotate. The heating device 29 heats the test disc 22 and the test disc 21. The test protection device 28 prevents the test disc and the test disc from breaking and flying out.
[0041] For the 22-wheel roulette wheel, the following two requirements must be met:
[0042] a) It can accurately simulate the interaction between the engine and the test wheel 21 under the working conditions;
[0043] b) The strength meets the test requirements, and the test wheel 22 should not be damaged during the test.
[0044] To meet the above two requirements, the structure and dimensions of the test wheel 22 are designed, and the steps are as follows:
[0045] 1) Overall structural design
[0046] The material of the test disc 22 is selected according to the type of component being tested for strength. If the sealing grate is a compressor rotor component, stainless steel, which has a relatively low price and relatively good performance, can be selected for the test disc 22 because its operating temperature is relatively low. If the sealing grate is a turbine rotor component, high-temperature alloy material can be selected for the test disc 22 because its operating temperature is relatively high.
[0047] The overall topology of the test wheel 22 is planned to ensure that the test wheel 22 does not interfere with or affect the assembly of the adjacent test wheel 21. The final structure of the test wheel 22 is as follows: Figure 5 As shown.
[0048] 2) Determine the critical dimensions of the initial assembly.
[0049] Based on the assembly relationship between the engine test wheel 21 and the adjacent test wheel 22, the key assembly dimensions are determined.
[0050] like Figure 5 As shown, the two discs are assembled on the disc rim mating surface 32 and the bolt mating surface 33, respectively. The dimensions related to the disc rim mating surface are determined as follows:
[0051] P1 = L1, P2 > L2, P4 > L3 and P3
[0052] Wherein, P1 is the distance from the outermost mating point of the test wheel 22 and the assessment wheel 21 to the engine axis 31;
[0053] L1 is the distance from the outermost mating point of the test wheel 21 and the test wheel 22 to the engine axis 31;
[0054] P2 is the width of the mating surface of the rim of the test roulette wheel 21;
[0055] L2 is the width of the mating surface of the rim of the test roulette wheel 22;
[0056] P3 is the axial distance between the mating surface 32 of the disc rim and the mating surface 33 of the bolt;
[0057] P4 is the width of the bolt mating surface of the test wheel 22;
[0058] L3 is the width of the bolt mating surface of the test wheel 21;
[0059] 3) Determine the key dimensions for deformation under working conditions.
[0060] The dimensions related to the deformation of the test wheel 22 are determined based on the deformation of the wheel rim under engine operating conditions, ensuring that the support stiffness of the test wheel 22 under test conditions is consistent with the support stiffness of the wheel rim under actual engine conditions.
[0061] The dimensions that primarily affect the flange support stiffness are the distance between the connecting bolt 23 and the flange, such as... Figure 5 As shown, a contraction portion 36 extends from the bolt mating surface of the test wheel 22 to the rim mating surface. The equal segment between the contraction portion 36 and the rim mating surface forms a support portion 35. The key dimensions of this deformation are the width P5 and the radial length P6 of the support portion 35.
[0062] 4) Determine the critical dimensions for working condition strength (stress).
[0063] The test wheel 22 should have sufficient strength to ensure that it does not break during the test. Based on the stress distribution characteristics of the wheel under rotation, the maximum stress is located in the center region of the wheel. Therefore, the key dimensions affecting the strength of the test wheel 22 are mainly located in the center region. The key dimensions affecting the strength of the test wheel 22 are determined to be the center radius P9, the hub width P7, and the hub height P8.
[0064] 5) Validity analysis of the test-taking roulette wheel
[0065] Based on the key dimensions determined in the above steps, an effectiveness analysis is performed on the test wheel 22. The effectiveness of the test wheel 22 is reflected in meeting the following requirements:
[0066] 1) Perform deformation calculations on the test components and adjust key dimensions P5 and P6 to make the axial deformation of the test wheel 22 edge deformation extraction point 34 (the top edge of the mating surface between the test wheel 22 and the test wheel 21) consistent with the engine working state.
[0067] 2) Perform stress calculations on the test components and adjust key dimensions P7, P8 and P9 to ensure that the stress of the test wheel 22 is within the range required by the engine strength specifications;
[0068] When the above two requirements are met, the design of the quiz roulette 22 is complete.
[0069] The sealing toothed disc strength test structure with flange positioning bolt connection proposed in this application greatly reduces the number of auxiliary test pieces by designing auxiliary test pieces to replace several engine components connected to the test disc. This provides great convenience for assembly, disassembly, and inspection before, during, and after the test, and improves work efficiency. Furthermore, the auxiliary test disc can be made of cheaper materials and can be processed using simpler techniques, significantly reducing test costs. This structure and method have been applied in engineering with excellent results and have been verified by engineering.
[0070] The above description is merely a specific embodiment of this application, but the scope of protection of this application is not limited thereto. Any variations or substitutions that can be easily conceived by those skilled in the art within the technical scope disclosed in this application should be included within the scope of protection of this application. Therefore, the scope of protection of this application should be determined by the scope of the claims.
Claims
1. A strength test structure for a sealing toothed disc with a positioning bolt connection at the disc rim, characterized in that, include: Assessment Roulette; The roulette wheel for the test takers; The test wheel and the auxiliary test wheel are connected by connecting bolts and nuts. A sleeve is provided between the test wheel and the auxiliary test wheel. The auxiliary test wheel is connected to the drive device via a drive shaft. The test wheel, connecting bolts, and sleeve are actual engine components. The structural dimensions of the auxiliary test wheel are configured to simulate the fit between the engine and the test wheel under engine operating conditions. A heating device and a test protection device are installed on the outside of the test wheel. The strength test of the sealing grate disc is carried out in a rotating and heated environment. The drive device controls the transfer drive shaft to drive the test wheel and the test wheel to rotate. The heating device forms a temperature field to heat the test wheel and the test wheel. The test protection device prevents the test wheel and the test wheel from breaking and flying out. The structural dimension configuration process of the accompanying test wheel includes: The material of the test wheel is determined according to the type of strength test for the sealed toothed disc; Based on the assembly relationship between the test wheel and the adjacent test wheel, the key assembly dimensions of the test wheel in its initial state are determined. These key assembly dimensions include: the distance P1 from the outermost mating point of the test wheel and the test wheel to the engine axis; the width P2 of the mating surface of the test wheel's rim; the axial distance P3 between the mating surface of the rim and the bolt mating surface; and the width P4 of the bolt mating surface of the test wheel. These dimensions satisfy the following relationships: P1 = L1, P2 > L2, P4 > L3, where L1 is the distance from the outermost mating point of the test wheel and the test wheel to the engine axis, L2 is the width of the mating surface of the test wheel's rim, and L3 is the width of the bolt mating surface of the test wheel. Based on the deformation of the disc rim under engine operating conditions, the key deformation dimensions related to the deformation of the test disc rim are determined. The key deformation dimensions include: the width of the support part P5 and the radial length of the support part P6, so as to ensure that the support stiffness of the test disc rim under test conditions is consistent with the support stiffness of the disc rim under actual engine conditions. Based on the fact that the maximum stress of the test wheel is located in the center region under rotation, the key stress dimensions affecting the strength of the test wheel are determined. The key stress dimensions include: the center radius dimension P9, the hub width dimension P7, and the hub height dimension P8, so that the strength of the test wheel does not break down during the test. By performing deformation calculations on the combination of the test wheel and the test wheel, the key deformation dimensions of the test wheel are controlled to ensure that the axial deformation of the test wheel's edge deformation extraction point is consistent with the engine's operating state. By performing stress calculations on the combination of the test wheel and the test wheel, the key stress dimensions of the test wheel are controlled to ensure that the stress of the test wheel is within the range required by the engine's strength specifications, thereby obtaining the structural dimensions of the test wheel that meet the requirements.
2. The strength test structure for the sealing toothed disc with rim positioning bolt connection as described in claim 1, characterized in that, If the sealing grate strength test is a compressor rotor strength test, the test wheel is made of stainless steel; if the sealing grate strength test is a turbine rotor strength test, the test wheel is made of high-temperature alloy.
3. The strength test structure for the sealing toothed disc with rim positioning bolt connection as described in claim 1, characterized in that, The extraction point for the deformation of the disk rim is the outer endpoint of the mating surface of the test disk and the assessment disk rim.