A method, apparatus, device, and medium for use testing an engine seal ring

Abstract

The application discloses a use test method, device, equipment and medium of an engine sealing ring. The use test method of the engine sealing ring performs transient heat conduction analysis on a sealing structure, obtains a transient temperature field of the sealing structure under a cycle working condition, performs springback analysis on a sealing ring, a flange and a fastener of the sealing structure in combination with the transient temperature field, determines axial deformation data generated by the sealing ring in a use process, and on the basis of the sealing ring and a rigid surface of the sealing structure, in combination with the axial deformation data and the transient temperature field, describes ratchet damage behavior of the sealing ring under the cycle working condition by using a nonlinear follow-up hardening model and a saturated isotropic hardening model, obtains equivalent plastic strain rates of the sealing ring under each cycle period, and determines the maximum cycle number of the sealing ring under the cycle working condition of the engine due to ratchet damage accumulation and fracture by using the equivalent plastic strain rates, so that analysis on a ratchet strain accumulation process of the sealing ring under the cycle working condition of the engine is realized.

Description

Technical Field

[0001] This invention relates to the field of simulation testing technology, and in particular to a method, apparatus, equipment and medium for testing the use of engine sealing rings. Background Technology

[0002] Engine combustion passages are characterized by high temperature, high pressure, and large diameter, and are typically connected using metal sealing flanges. During engine operation, the flanges undergo some separation deformation under high temperature and high load. The sealing element needs sufficient compensation capacity to compensate for this deformation and separation to ensure that the flange leakage rate remains within the required range during engine operation. Engines have strict weight limitations; increasing axial load to achieve a reliable static seal would significantly increase the weight of the flange and fasteners. Therefore, thin-walled or cantilevered sealing structures are used, allowing the sealing ring to undergo overall elastic and localized plastic deformation during compression, and utilizing the resilience of the flexible structure to compensate for flange deformation and separation under operating loads.

[0003] The metal sealing structure of the gas passage usually uses nickel-based high-temperature alloy as the matrix. During repeated use, the root of the sealing cantilever will undergo cyclic plastic deformation. Furthermore, due to the asymmetry of the working load, local plastic strain will accumulate in the direction of average stress, resulting in ratchet damage effect.

[0004] However, in the existing technology, in the simulation calculation of the reusability of sealing structures, there is no effective numerical method to quantify the impact of ratchet damage accumulation on sealing performance degradation under cyclic force-thermal load. Summary of the Invention

[0005] The purpose of this invention is to provide a testing method, apparatus, equipment, and medium for engine sealing rings, in order to quantify the impact of ratchet damage accumulation on sealing performance degradation under cyclic force-thermal load.

[0006] To achieve the above objectives, the present invention provides the following technical solution:

[0007] A testing method for an engine sealing ring includes: performing transient thermal conduction analysis on the engine's sealing structure based on engine operating parameters to obtain the transient temperature field of the sealing structure under cyclic operating conditions; performing a first compression-rebound analysis on the sealing ring, flange, and fasteners of the sealing structure based on the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions; performing a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field and the axial deformation data to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions; wherein, during the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions; and determining the maximum number of cycles at which the sealing ring fractures due to ratchet damage accumulation under the engine cyclic operating conditions based on the ductility limit of the sealing ring and the equivalent plastic strain rate for each cycle.

[0008] In one optional embodiment of this application, the engine's cyclic operating conditions include: providing pre-tightening force to the sealing ring and flange through fasteners, and multiple cyclic operating conditions consisting of the temperature fields during the application of gas pressure, the loading of the engine start-up and operation process, the unloading of gas pressure, and the loading of the engine shutdown and recovery process; the step of performing transient heat conduction analysis on the engine's sealing structure based on the engine's operating parameters to obtain the transient temperature field of the sealing structure under the cyclic operating conditions includes: obtaining transient heat conduction analysis models of the sealing ring, flange, and fasteners in the sealing structure; combining the engine's operating ambient temperature, convective heat transfer boundary, radiative boundary, and contact heat conduction data between various parts of the sealing structure, performing a heating transient heat conduction analysis on the transient heat conduction analysis model to determine the temperature field during the engine start-up and operation process; combining the temperature field during the engine start-up and operation process, convective heat transfer boundary, radiative boundary, and contact heat conduction data between various parts of the sealing structure, performing a cooling transient heat conduction analysis on the transient heat conduction analysis model to determine the temperature field during the engine shutdown and recovery process.

[0009] In one optional embodiment of this application, the step of performing a first compression-rebound analysis on the sealing ring, flange, and fasteners of the sealing structure based on the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions includes: obtaining a three-dimensional symmetrical compression-rebound analysis model of the sealing ring, flange, and fasteners in the sealing structure by combining the contact characteristics and material properties of the sealing ring, flange, and fasteners in the sealing structure; and performing compression-rebound analysis on the three-dimensional symmetrical compression-rebound analysis model based on the engine cyclic operating conditions and the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions.

[0010] In one optional embodiment of this application, the step of performing a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field of the sealing structure and the axial deformation data to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions includes: obtaining a two-dimensional axisymmetric cyclic compression-rebound analysis model of the sealing ring and rigid surface in the sealing structure; in the two-dimensional axisymmetric cyclic compression-rebound analysis model, using a nonlinear kinematic hardening model and a saturated isotropic hardening model to describe the sealing ring, and combining the transient temperature field and the axial deformation data to simulate the mechanical behavior of the sealing ring under the engine cyclic operating conditions, thereby generating the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions.

[0011] In one optional embodiment of this application, the ductility limit of the sealing ring is determined by the following formula: Wherein, D represents the ductility limit of the sealing ring; This indicates the area shrinkage rate of the sealing ring material.

[0012] In one optional embodiment of this application, determining the maximum number of cycles in which the sealing ring will fracture due to ratchet damage accumulation under engine cyclic conditions, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle, includes: determining the stable equivalent plastic strain rate of the sealing ring based on the equivalent plastic strain rate of adjacent cycles under engine cyclic conditions; and determining the maximum number of cycles based on the ductility limit and the stable equivalent plastic strain rate.

[0013] In one optional embodiment of this application, the maximum number of cycles is determined by the following formula: ;in, The maximum number of cycles is indicated by ; D represents the ductility limit of the sealing ring; This represents the stable equivalent plastic strain rate; D0 represents the life safety factor; D0 represents the plastic strain accumulated in the number of cycles before the sealing ring reaches a stable equivalent plastic strain rate.

[0014] Compared with existing technologies, the engine sealing ring testing method provided by this invention performs transient heat conduction analysis on the engine's sealing structure to obtain the transient temperature field of the sealing structure under cyclic operating conditions. Combined with the transient temperature field, springback analysis is performed on the sealing ring, flange, and fasteners of the sealing structure to determine the axial deformation data generated by the sealing ring during use. Simultaneously, based on the sealing ring and rigid surface of the sealing structure, and combining the axial deformation data and transient temperature field, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage behavior of the sealing ring under cyclic operating conditions. The equivalent plastic strain rate of the sealing ring in each cycle is obtained, and the maximum number of cycles required for the sealing ring to fracture due to ratchet damage accumulation under engine cyclic operating conditions is determined using the equivalent plastic strain rate. This achieves a quantitative analysis of the ratchet strain accumulation process of the sealing ring under engine cyclic operating conditions.

[0015] The present invention also provides a testing device for the use of engine sealing rings, comprising:

[0016] The temperature field determination unit is used to perform transient heat conduction analysis on the engine's sealing structure based on the engine's operating parameters, and to obtain the transient temperature field of the sealing structure under cyclic operating conditions.

[0017] The axial deformation data determination unit is used to perform a first compression and springback analysis on the sealing ring, flange, and fasteners of the sealing structure based on the transient temperature field of the sealing structure, and to determine the axial deformation data under the engine cyclic operating conditions.

[0018] The equivalent plastic strain determination unit is used to perform a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field and axial deformation data of the sealing structure, and to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions; wherein, in the process of the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions.

[0019] The maximum cycle count determination unit is used to determine the maximum number of cycles in which the sealing ring will break due to ratchet damage accumulation under engine cyclic conditions, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle.

[0020] Compared with the prior art, the beneficial effects of the engine sealing ring usage testing device provided by the present invention are the same as those of the engine sealing ring usage testing method described in the above technical solution, and will not be repeated here.

[0021] The present invention also provides an electronic device, comprising: a processor; a memory for storing executable instructions of the processor; the processor being configured to execute a method for testing the use of an engine sealing ring by running the instructions in the memory.

[0022] Compared with the prior art, the beneficial effects of the electronic device provided by the present invention are the same as those of the engine sealing ring testing method described in the above technical solution, and will not be repeated here.

[0023] The present invention also provides a computer storage medium storing instructions that, when executed, implement the above-described test method for the use of engine sealing rings.

[0024] Compared with the prior art, the beneficial effects of the computer storage medium provided by the present invention are the same as those of the engine sealing ring testing method described in the above technical solution, and will not be repeated here. Attached Figure Description

[0025] The accompanying drawings, which are included to provide a further understanding of the invention and form part of this invention, illustrate exemplary embodiments of the invention and are used to explain the invention, but do not constitute an undue limitation of the invention. In the drawings:

[0026] Figure 1 A flowchart illustrating the testing method for the use of an engine sealing ring provided in this application embodiment.

[0027] Figure 2 A structural diagram of the engine sealing ring testing device provided in this application embodiment.

[0028] Figure 3 This is a schematic diagram of an electronic device structure provided in an embodiment of this application. Detailed Implementation

[0029] To facilitate a clear description of the technical solutions in the embodiments of the present invention, the terms "first" and "second" are used to distinguish identical or similar items with essentially the same function and effect. For example, the first threshold and the second threshold are merely used to distinguish different thresholds and do not limit their order. Those skilled in the art will understand that the terms "first" and "second" do not limit the quantity or execution order, and that the terms "first" and "second" are not necessarily different.

[0030] It should be noted that in this invention, the terms "exemplary" or "for example" are used to indicate examples, illustrations, or descriptions. Any embodiment or design described as "exemplary" or "for example" in this invention should not be construed as being more preferred or advantageous than other embodiments or designs. Specifically, the use of terms such as "exemplary" or "for example" is intended to present the relevant concepts in a concrete manner.

[0031] In this invention, "at least one" refers to one or more, and "more than one" refers to two or more. "And / or" describes the relationship between related objects, indicating that three relationships can exist. For example, A and / or B can represent: A alone, A and B simultaneously, or B alone, where A and B can be singular or plural. The character " / " generally indicates that the preceding and following related objects are in an "or" relationship. "At least one of the following" or similar expressions refer to any combination of these items, including any combination of single or plural items. For example, at least one of a, b, or c can represent: a, b, c, a combination of a and b, a combination of a and c, a combination of b and c, or a, b, and c, where a, b, and c can be single or multiple.

[0032] This application provides a method, apparatus, equipment, and medium for testing the use of engine sealing rings, which will be described in detail in the following embodiments.

[0033] This application first provides a testing method for the use of engine sealing rings. Please refer to [link / reference]. Figure 1 , Figure 1 A flowchart illustrating the testing method for the use of an engine sealing ring provided in this application embodiment.

[0034] like Figure 1 As shown, the test method for the use of the engine sealing ring includes the following steps S101 to S104.

[0035] S101, Based on the engine's operating parameters, perform transient heat conduction analysis on the engine's sealing structure to obtain the transient temperature field of the sealing structure under cyclic operating conditions.

[0036] A sealing structure refers to a key component in an engine used to connect the combustion passages. It is designed to prevent leakage of fuel, oxidizer, or combustion products between fixed parts under extreme pressure, high temperature, and severe vibration conditions.

[0037] Typically, a sealing structure includes a sealing ring, a flange, and fasteners. The sealing ring forms a reliable seal between the flange contact surfaces, preventing the leakage of high-temperature, high-pressure combustion gases. During engine operation, the flange expands due to heat or deforms under stress; the sealing ring can compensate for this deformation through elastic deformation to maintain the sealing effect. The flange secures the sealing ring, ensuring a smooth sealing surface. Fasteners provide clamping force between the sealing ring and the flange.

[0038] Under high temperature and high pressure working loads, the cyclic operating conditions of the sealing structure of an engine are typically as follows: pre-tightening of equipment at room temperature → start-up and steady-state operation → shutdown and recovery → start-up and steady-state operation → shutdown and recovery… Among them, start-up and steady-state operation correspond to the pressurization and heating process of the engine, while shutdown and recovery correspond to the depressurization and cooling process of the engine.

[0039] Corresponding to the above-mentioned cyclic operating conditions, the simulated cyclic load history of the engine's operation process can be established as follows: providing preload to the sealing ring and flange through fasteners → applying gas pressure → loading the temperature field during engine start-up and operation → removing the gas pressure load → loading the temperature field during engine shutdown and recovery → applying gas pressure → loading the temperature field during engine start-up and operation → removing the gas pressure load → loading the temperature field during engine shutdown and recovery… That is, the cyclic operating conditions of the engine include: providing preload to the sealing ring and flange through fasteners, and multiple cyclic operating conditions consisting of applying gas pressure, loading the temperature field during engine start-up and operation, removing the gas pressure, and loading the temperature field during engine shutdown and recovery.

[0040] In one optional embodiment of this application, the loading time for the temperature field during the power-on and operation process is typically 500 seconds, and the loading time for the temperature field during the power-off and recovery process is 3 hours.

[0041] The purpose of S101 is to determine the temperature environment of the sealing structure during engine operation by performing transient heat conduction analysis on the sealing structure, so as to facilitate subsequent simulation testing of the sealing ring in conjunction with the temperature environment.

[0042] Specifically, S101 includes the following S1 to S3.

[0043] S1, obtain the transient heat conduction analysis model of the sealing ring, flange and fasteners in the sealing structure.

[0044] Transient heat conduction analysis model is a thermodynamic simulation method used in finite element analysis to study the temperature change over time. In the flange connection system of an engine, obtaining the transient heat conduction analysis model of the system can be understood as establishing a mathematical or numerical model that can reflect the temperature distribution of the sealing ring, flange and fasteners under engine cyclic conditions over time.

[0045] In practical applications, since the sealing structure and the load under engine cyclic conditions have periodicity and symmetry, a sector-shaped local model containing a stud in the fastener can be established as a transient heat conduction analysis model to perform transient heat conduction analysis.

[0046] S2, combining the engine's operating environment temperature, convective heat transfer boundary, radiative boundary, and contact heat conduction data between various parts of the sealing structure, perform transient heat conduction analysis on the transient heat conduction analysis model to determine the temperature field during engine start-up and operation.

[0047] During the transient heat conduction analysis, the initial temperature of the structure is determined to be the working environment temperature. A convective heat transfer boundary is set for the inner surface of the flange that is in direct contact with the oxygen-rich gas. Contact heat conduction is set between the various parts of the sealing structure. Convective heat transfer boundaries and radiation boundaries are set for the outer surface of the flange that is in direct contact with the air. Based on the transient heat conduction analysis model and combined with the above environmental information, transient heat conduction analysis is performed to determine the temperature field during engine start-up and operation.

[0048] S3. Combining the temperature field, convective heat transfer boundary, radiation boundary, and contact heat conduction data between various parts of the sealing structure during the engine start-up and operation process, a cooling transient heat conduction analysis is performed on the transient heat conduction analysis model to determine the temperature field during the engine shutdown and warm-up process.

[0049] During the cooling heat conduction analysis, the initial temperature of the structure is the temperature field at the moment of engine shutdown, specifically the temperature field corresponding to the last moment of engine startup and steady-state operation; the inner surface of the flange that is in direct contact with the oxygen-rich gas is provided with a convective heat transfer boundary; contact heat conduction is provided between the various parts of the sealing structure; and convective heat transfer boundary and radiation boundary are provided on the outer surface of the flange that is in direct contact with the air. Based on the transient conduction analysis model and combined with the above environmental information, transient heat conduction analysis is performed to determine the temperature field during engine shutdown and reheating.

[0050] S102, based on the transient temperature field of the sealing structure, perform a first compression and springback analysis on the sealing ring, flange, and fasteners of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions.

[0051] The first compression and springback analysis of the sealing ring, flange, and fasteners of the sealing structure refers to the analysis of the compression of the sealing ring, flange, and fasteners under the pressure of the gas during loading, start-up, and operation, as well as the springback of the sealing ring, flange, and fasteners during the release of the gas pressure and the temperature recovery process after loading and shutdown.

[0052] Since the engine operates continuously from startup to shutdown and temperature recovery, the first compression-springback analysis only requires one cycle of engine operation.

[0053] Specifically, S102 includes the following S4 and S5.

[0054] S4. Combining the contact characteristics and material properties of the sealing ring, flange, and fasteners in the sealing structure, a three-dimensional symmetrical compression and springback analysis model of the sealing ring, flange, and fasteners in the sealing structure is obtained.

[0055] The three-dimensional symmetric compression and springback analysis model is a three-dimensional finite element model. That is, it is a three-dimensional model that can reflect the actual behavior of the structure by considering the geometric features and stress conditions in three spatial directions (X, Y, Z) during the modeling process.

[0056] Similar to the transient heat conduction analysis model, the three-dimensional symmetric compression-springback analysis model can also be a sector-shaped local model containing a stud in the fasteners, due to the circumferential symmetry of the sealing ring, flange, and fasteners in the engine. Furthermore, to ensure consistency of environmental data, the finite element mesh of the three-dimensional symmetric compression-springback analysis model is the same as that of the transient heat conduction analysis model.

[0057] In practical applications, establishing a three-dimensional symmetric compression-springback analysis model requires defining the material properties of the sealing ring, flange, and fasteners. In this embodiment, the sealing ring is described by both a nonlinear kinematic hardening model and a saturated isotropic hardening model; the flange and fasteners are described by a linear kinematic hardening model.

[0058] Meanwhile, to reflect the connection relationship between the sealing ring, flange, and fasteners, as well as their behavioral characteristics during engine operation, contact pairs are set between the sealing ring and the flange sealing ring groove, between the mating surfaces of the upper and lower flanges, between the bolts and bolt hole walls of the fasteners, between the bolts and gaskets, and between the gaskets and the upper flange. In the contact pair between the sealing ring and the flange sealing ring groove, the sealing ring is the secondary contact surface, and the flange sealing ring groove is the primary contact pair. The slip equation between the sealing ring and the flange sealing ring groove adopts a finite slip equation; the discretization method is selected as node-to-face. In the remaining contact pairs, the slip equation adopts a finite slip equation, and the discretization method is selected as face-to-face.

[0059] To reflect the mechanical behavior of the flange in the actual piping system of the engine, the flange boundary should be set according to the stiffness of the flange in the actual piping system. At the same time, when the three-dimensional symmetric compression and springback analysis model is a sector-shaped local model, a periodic symmetric boundary is applied.

[0060] S5. Based on the engine cycle conditions and the transient temperature field of the sealing structure, perform compression and springback analysis on the three-dimensional symmetrical compression and springback analysis model to determine the axial deformation data under the engine cycle conditions.

[0061] Axial deformation data refers to the amount of axial deformation of the sealing ring under engine cyclic conditions.

[0062] During the first compression and rebound analysis, the load history corresponding to the following five analysis steps is mainly analyzed: providing preload to the sealing ring and flange through fasteners → applying gas pressure → loading the temperature field during startup and operation → removing the gas pressure load → loading the temperature field during shutdown and recovery.

[0063] In the analysis step of the temperature field during the loading start-up and operation process, the temperature field during the engine start-up and operation process determined by S2 is used. In the analysis step of the temperature field during the loading shutdown and recovery process, the temperature field during the engine shutdown and recovery process determined by S3 is used.

[0064] S103, based on the transient temperature field of the sealing structure and the axial deformation data, a second compression-rebound analysis is performed on the sealing ring and rigid surface of the sealing structure to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions; wherein, in the process of the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions.

[0065] The second compression-rebound analysis of the sealing ring and rigid surface of the sealing structure refers to simulating the mechanical motion of the sealing ring under engine cyclic conditions by combining the contact relationship between the sealing ring and the rigid surface, using a nonlinear kinematic hardening model and a saturated isotropic hardening model to describe the sealing ring, and then obtaining the ratchet damage data.

[0066] In practical applications, the danger point of seal ring breakage is generally located at the cantilever position of the secondary seal. Therefore, the equivalent plastic strain rate corresponds to the equivalent plastic strain rate at the cantilever position of the secondary seal.

[0067] Specifically, S103 includes the following S6 to S7.

[0068] S6, obtain the two-dimensional axisymmetric cyclic compression and springback analysis model of the sealing ring and rigid surface in the sealing structure.

[0069] The two-dimensional axisymmetric cyclic compression and springback analysis model can be understood as a simplified model used to study the interaction between the sealing ring and the rigid surface in a sealing structure. In practical applications, the two-dimensional axisymmetric cyclic compression and springback analysis model is usually a two-dimensional model in the radial and axial directions in the polar coordinate system. In the embodiments of this application, since the shape and material properties of the sealing ring do not change at each axial interface, the model refers to the model of one axial section of the sealing ring.

[0070] In this model, compression refers to the process in which the sealing ring is compressed and deformed during the application of gas pressure and the loading of the temperature field during startup and operation. Springback refers to the process in which the pressure on the sealing ring decreases and the sealing ring attempts to return to its original shape during the process of removing the gas pressure load, loading the temperature field during shutdown and reheating.

[0071] In practical applications, a contact pair is set between the sealing ring and the rigid surface in the two-dimensional axisymmetric cyclic compression and springback analysis model. The rigid surface is set as the main contact surface, and the sealing lip and the sealing ring limiting surface are set as the secondary contact surfaces. The slip equation between the two is a finite slip equation, and the discretization method is a node-to-face discretization method.

[0072] S7. In the two-dimensional axisymmetric cyclic compression and springback analysis model, the sealing ring is described by a nonlinear kinematic hardening model and a saturated isotropic hardening model. Combined with the transient temperature field and the axial deformation data, the mechanical behavior of the sealing ring under engine cyclic conditions is simulated, and the equivalent plastic strain rate of each cycle under engine cyclic conditions is generated.

[0073] In the process of performance analysis, similar to S102 above, the nonlinear kinematic hardening model and the saturated isotropic hardening model are used to describe the sealing ring. At the same time, a fixed constraint is applied to the lower rigid surface, and the axial deformation data of the engine cyclic condition obtained in S102 is applied to the upper rigid surface. Furthermore, the transient temperature field obtained in S101 is combined to simulate the mechanical behavior of the engine cyclic condition, and the equivalent plastic strain of each cycle under the engine cyclic condition is generated.

[0074] The nonlinear kinematic hardening model can be expressed by the following formulas (1) and (2):

[0075] (1);

[0076] (2);

[0077] The nonlinear kinematic hardening model describes the movement of the yield surface. The back stress evolution equation of this model includes a linear hardening term and a dynamic recovery term. Due to the dynamic recovery term... The existence of this allows the model to simulate the non-closed ratchet behavior in the cyclic stress-strain response of materials.

[0078] in, Represents the back stress tensor, which is given by the i-th term. Superimposed composition, through different back stresses It reflects the nonlinear behavior of materials at different stages of plastic deformation; Let i be the rate of change of the i-th back stress; and These are the material constants in the kinematic hardening model; This is the initial kinematic hardening modulus; The decay rate of the kinematic hardening model with increasing plastic deformation is described; Represents the inelastic strain rate tensor; This represents the cumulative plastic strain rate.

[0079] The isotropic hardening model describes the process of the yield surface expanding equally in all directions in stress space. In the saturated isotropic hardening model, the strengthening or weakening effect of the yield surface has a saturation value, which is expressed by the following formula (3):

[0080] (3);

[0081] in, It represents the flow stress, reflecting the change in the radius of the yield surface of the sealing ring material during the deformation process; 'b' represents the resistance to saturated isotropic deformation; 'b' represents a material parameter used to describe isotropic flow stress. The evolution rate; p represents the cumulative plastic strain.

[0082] The embodiments of this application employ a nonlinear kinematic hardening model and an isotropic hardening model, which can simulate the plastic behavior of the sealing ring under engine cyclic conditions by considering the ratchet damage accumulation under engine cyclic conditions.

[0083] S104, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle, determine the maximum number of cycles in which the sealing ring will break due to ratchet damage accumulation under engine cyclic conditions.

[0084] In practical applications, the ductility limit of the sealing ring can be determined by the following formula (4):

[0085] (4);

[0086] Wherein, D represents the ductility limit of the sealing ring; The area reduction rate of the sealing ring material can be calculated by measuring the cross-sectional radius at the fracture point of a standard specimen.

[0087] In this embodiment, the ductility limit of the sealing ring is used as a criterion for sealing ring failure. It is assumed to be the equivalent plastic strain limit value at the critical point of the sealing ring structure. When the equivalent plastic strain at the critical point reaches the ductility limit D, the sealing ring is considered to be in a structural failure state.

[0088] Specifically, S104 above includes:

[0089] The stable equivalent plastic strain rate of the sealing ring is determined based on the equivalent plastic strain rate of adjacent cycles under engine cyclic conditions; the maximum number of cycles is determined based on the ductility limit and the stable equivalent plastic strain rate.

[0090] In practical applications, the equivalent plastic strain of the sealing ring will accumulate rapidly in the initial stage of cyclic operation, at which time the equivalent plastic strain rate is relatively large. Subsequently, as the number of cycles increases, the equivalent plastic strain rate gradually decreases, and the accumulation rate of equivalent plastic strain (or ratchet damage accumulation) slows down compared to the initial stage, eventually entering the cyclic stability stage, where the equivalent plastic strain rate remains basically unchanged.

[0091] Furthermore, in order to determine the stable equivalent plastic strain rate, the following formula (5) can be used:

[0092] (5);

[0093] in, This represents the maximum equivalent plastic strain rate in the Nth cycle. Represents equivalent plastic strain; It represents the maximum equivalent plastic strain rate in the (N-1)th cycle.

[0094] If the equivalent plastic strain rate of multiple consecutive cycles satisfies the above formula (5), it is considered that the plastic strain accumulation at the dangerous point of the sealing ring enters the cyclic stable state during these multiple consecutive cycles, and the equivalent plastic strain rate at this time can be determined as the stable equivalent plastic strain rate.

[0095] Once the equivalent plastic strain rate and the ductility limit are obtained, the maximum number of cycles of the sealing ring structure can be determined.

[0096] Specifically, the maximum number of cycles can be determined by the following formula (6).

[0097] (6);

[0098] in, The maximum number of cycles is indicated by ; D represents the ductility limit of the sealing ring; This represents the stable equivalent plastic strain rate; D0 represents the life safety factor; D0 represents the plastic strain accumulated in the number of cycles before the sealing ring reaches a stable equivalent plastic strain rate.

[0099] In summary, the engine sealing ring testing method provided in this application performs transient heat conduction analysis on the engine's sealing structure to obtain the transient temperature field of the sealing structure under cyclic operating conditions. Combined with the transient temperature field, springback analysis is performed on the sealing ring, flange, and fasteners of the sealing structure to determine the axial deformation data generated by the sealing ring during use. Furthermore, based on the sealing ring and rigid surface of the sealing structure, and combining the axial deformation data and transient temperature field, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage behavior of the sealing ring under cyclic operating conditions. The equivalent plastic strain rate of the sealing ring in each cycle is obtained, and the maximum number of cycles required for the sealing ring to fracture due to ratchet damage accumulation under engine cyclic operating conditions is determined using the equivalent plastic strain rate. This achieves a quantitative analysis of the ratchet strain accumulation process of the sealing ring under engine cyclic operating conditions.

[0100] This application also provides a testing device for the use of engine sealing rings. Please refer to [link / reference]. Figure 2 , Figure 2 A structural diagram of the engine sealing ring testing device provided in this application embodiment.

[0101] like Figure 2 The aforementioned testing device for the use of engine sealing rings includes:

[0102] Temperature field determination unit 201 is used to perform transient heat conduction analysis on the sealing structure of the engine based on the engine's operating parameters, and obtain the transient temperature field of the sealing structure under cyclic operating conditions.

[0103] The axial deformation data determination unit 202 is used to perform a first compression and springback analysis on the sealing ring, flange and fasteners of the sealing structure based on the transient temperature field of the sealing structure, and to determine the axial deformation data under the engine cyclic operating conditions.

[0104] The equivalent plastic strain determination unit 203 is used to perform a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field of the sealing structure and the axial deformation data, and to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions; wherein, in the process of the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions.

[0105] The maximum number of cycles determination unit 204 is used to determine the maximum number of cycles in which the sealing ring will break due to ratchet damage accumulation under engine cyclic conditions, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle.

[0106] In one optional embodiment of this application, the cyclic operating conditions of the engine include: providing pre-tightening force to the sealing ring and flange through fasteners, and multiple cyclic operating conditions consisting of applying gas pressure, loading the start-up and operating temperature field, unloading the gas pressure, and loading the shutdown and warm-up temperature field.

[0107] The step involves performing transient heat conduction analysis on the engine's sealing structure based on the engine's operating parameters to obtain the transient temperature field of the sealing structure under cyclic operating conditions. This includes: obtaining transient heat conduction analysis models of the sealing ring, flange, and fasteners in the sealing structure; combining the engine's operating ambient temperature, convective heat transfer boundaries, radiative heat transfer boundaries, and contact heat conduction data between various parts of the sealing structure to perform heating transient heat conduction analysis on the transient heat conduction analysis models to determine the temperature field during engine start-up and operation; and combining the temperature field during engine start-up and operation, convective heat transfer boundaries, radiative heat transfer boundaries, and contact heat conduction data between various parts of the sealing structure to perform cooling transient heat conduction analysis on the transient heat conduction analysis models to determine the temperature field during engine shutdown and recovery.

[0108] In one optional embodiment of this application, the step of performing a first compression-rebound analysis on the sealing ring, flange, and fasteners of the sealing structure based on the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions includes: obtaining a three-dimensional symmetrical compression-rebound analysis model of the sealing ring, flange, and fasteners in the sealing structure by combining the contact characteristics and material properties of the sealing ring, flange, and fasteners in the sealing structure; and performing compression-rebound analysis on the three-dimensional symmetrical compression-rebound analysis model based on the engine cyclic operating conditions and the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions.

[0109] In one optional embodiment of this application, the step of performing a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field of the sealing structure and the axial deformation data to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions includes: obtaining a two-dimensional axisymmetric cyclic compression-rebound analysis model of the sealing ring and rigid surface in the sealing structure; in the two-dimensional axisymmetric cyclic compression-rebound analysis model, using a nonlinear kinematic hardening model and a saturated isotropic hardening model to describe the sealing ring, and combining the transient temperature field and the axial deformation data to simulate the mechanical behavior of the sealing ring under the engine cyclic operating conditions, thereby generating the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions.

[0110] In one optional embodiment of this application, the ductility limit of the sealing ring is determined by the following formula: Wherein, D represents the ductility limit of the sealing ring; This indicates the area shrinkage rate of the sealing ring material.

[0111] In one optional embodiment of this application, determining the maximum number of cycles in which the sealing ring will fracture due to ratchet damage accumulation under engine cyclic conditions, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle, includes: determining the stable equivalent plastic strain rate of the sealing ring based on the equivalent plastic strain rate of adjacent cycles under engine cyclic conditions; and determining the maximum number of cycles based on the ductility limit and the stable equivalent plastic strain rate.

[0112] In one optional embodiment of this application, the maximum number of cycles is determined by the following formula: ;in, The maximum number of cycles is indicated by ; D represents the ductility limit of the sealing ring; This represents the stable equivalent plastic strain rate; D0 represents the life safety factor; D0 represents the plastic strain accumulated in the number of cycles before the sealing ring reaches a stable equivalent plastic strain rate.

[0113] The method embodiments provided in this example and the system embodiments of this application belong to the same application concept. For technical details not described in detail in this example, please refer to the specific processing content of the engine sealing ring usage test method provided in the above embodiments of this application, which will not be repeated here.

[0114] This application also provides an electronic device, such as... Figure 3 As shown, Figure 3 This is a schematic diagram of an electronic device structure provided in an embodiment of this application.

[0115] like Figure 3As shown, the electronic device includes: a processor 210; a memory 200 for storing executable instructions of the processor 210; the processor 210 is used to execute the engine sealing ring usage test method disclosed in any of the above embodiments by running the instructions in the memory 200.

[0116] The processor 210, memory 200, communication interface 220, input device 230, and output device 240 are interconnected via a bus. Among them:

[0117] A bus can include a pathway for transmitting information between various components of a computer system.

[0118] Processor 210 can be a general-purpose processor, such as a general-purpose central processing unit (CPU), a microprocessor, etc., or an application-specific integrated circuit (ASIC), or one or more integrated circuits used to control the execution of the program of the present invention. It can also be a digital signal processor (DSP), an application-specific integrated circuit (ASIC), an off-the-shelf programmable gate array (FPGA), or other programmable logic devices, discrete gate or transistor logic devices, or discrete hardware components.

[0119] Processor 210 may include a main processor, as well as a baseband chip, modem, etc.

[0120] The memory 200 stores a program that executes the technical solution of this invention, and may also store an operating system and other key business functions. Specifically, the program may include program code, which includes computer operation instructions. More specifically, the memory 200 may include read-only memory (ROM), other types of static storage devices capable of storing static information and instructions, random access memory (RAM), other types of dynamic storage devices capable of storing information and instructions, disk storage, flash memory, etc.

[0121] Input device 230 may include a device for receiving user input data and information, such as a keyboard, mouse, camera, scanner, touch screen, etc.

[0122] Output device 240 may include devices that allow information to be output to a user, such as a display screen, printer, speaker, etc.

[0123] The communication interface 220 may include a device that uses any transceiver to communicate with other devices or communication networks, such as Ethernet, Radio Access Network (RAN), Wireless Local Area Network (WLAN), etc.

[0124] The processor 210 executes the program stored in the memory 200 and calls other devices, and can be used to implement each step of any of the engine sealing ring usage test methods provided in the above embodiments of this application.

[0125] In addition to the methods and devices described above, embodiments of this application may also be computer program products, which include computer program instructions that, when executed by a processor, cause the processor to perform the steps in the engine sealing ring usage test methods of various embodiments of this application.

[0126] The computer program product can be written in any combination of one or more programming languages ​​to perform the operations of the embodiments of this application. The programming languages ​​include object-oriented programming languages ​​such as Java and C++, as well as conventional procedural programming languages ​​such as C or similar languages. The program code can be executed entirely on the user's computing device, partially on the user's computing device, as a standalone software package, partially on the user's computing device and partially on a remote computing device, or entirely on a remote computing device or server.

[0127] Furthermore, embodiments of this application may also be storage media storing a computer program, which is executed by a processor in the steps of the engine sealing ring usage test method of various embodiments of this application.

[0128] For the foregoing method embodiments, in order to simplify the description, they are all described as a series of actions. However, those skilled in the art should understand that this application is not limited to the described order of actions, because according to this application, some steps can be performed in other orders or simultaneously. Furthermore, those skilled in the art should also understand that the embodiments described in the specification are all preferred embodiments, and the actions and modules involved are not necessarily essential to this application.

[0129] It should be noted that the various embodiments in this specification are described in a progressive manner, with each embodiment focusing on the differences from other embodiments. Similar or identical parts between embodiments can be referred to interchangeably. For apparatus embodiments, since they are basically similar to method embodiments, the description is relatively simple; relevant parts can be referred to the descriptions in the method embodiments.

[0130] The steps in the methods of the various embodiments of this application can be adjusted, merged, or deleted in order according to actual needs, and the technical features described in each embodiment can be replaced or combined.

[0131] The modules and sub-modules in the apparatus and terminal in the various embodiments of this application can be merged, divided, and deleted according to actual needs.

[0132] It should be understood that the disclosed terminals, devices, and methods can be implemented in other ways, given the several embodiments provided in this application. For example, the terminal embodiments described above are merely illustrative. For instance, the division of modules or sub-modules is only a logical functional division, and in actual implementation, there may be other division methods. For example, multiple sub-modules or modules may be combined or integrated into another module, or some features may be ignored or not executed. Furthermore, the coupling or direct coupling or communication connection shown or discussed may be indirect coupling or communication connection through some interfaces, devices, or modules, and may be electrical, mechanical, or other forms.

[0133] The modules or submodules described as separate components may or may not be physically separate. The components that constitute a module or submodule may or may not be physical modules or submodules; that is, they may be located in one place or distributed across multiple network modules or submodules. Some or all of the modules or submodules can be selected to achieve the purpose of this embodiment's solution, depending on actual needs.

[0134] Furthermore, the functional modules or sub-modules in the various embodiments of this application can be integrated into one processing module, or each module or sub-module can exist physically separately, or two or more modules or sub-modules can be integrated into one module. The integrated modules or sub-modules described above can be implemented in hardware or in the form of software functional modules or sub-modules.

[0135] Those skilled in the art will further recognize that the units and algorithm steps of the various examples described in conjunction with the embodiments disclosed herein can be implemented in electronic hardware, computer software, or a combination of both. To clearly illustrate the interchangeability of hardware and software, the components and steps of the various examples have been generally described in terms of functionality in the foregoing description. Whether these functions are implemented in hardware or software depends on the specific application and design constraints of the technical solution. Those skilled in the art can use different methods to implement the described functions for each specific application, but such implementation should not be considered beyond the scope of this application.

[0136] The steps of the methods or algorithms described in conjunction with the embodiments disclosed herein can be implemented directly by hardware, a software unit executed by a processor, or a combination of both. The software unit can be located in random access memory (RAM), main memory, read-only memory (ROM), electrically programmable ROM, electrically erasable programmable ROM, registers, hard disk, removable disk, CD-ROM, or any other form of storage medium known in the art.

[0137] Finally, it should be noted that in this document, relational terms such as "first" and "second" are used only to distinguish one entity or operation from another, and do not necessarily require or imply any such actual relationship or order between these entities or operations. Furthermore, the terms "comprising," "including," or any other variations thereof are intended to cover non-exclusive inclusion, such that a process, method, article, or apparatus that comprises a list of elements includes not only those elements but also other elements not expressly listed, or elements inherent to such a process, method, article, or apparatus. Without further limitations, an element defined by the phrase "comprising one..." does not exclude the presence of other identical elements in the process, method, article, or apparatus that includes said element.

[0138] The above description of the disclosed embodiments enables those skilled in the art to make or use this application. Various modifications to these embodiments will be readily apparent to those skilled in the art, and the general principles defined herein may be implemented in other embodiments without departing from the spirit or scope of this application. Therefore, this application is not to be limited to the embodiments shown herein, but is to be accorded the widest scope consistent with the principles and novel features disclosed herein.

Claims

1. A testing method for the use of an engine sealing ring, characterized in that, include: Based on the engine's operating parameters, a transient heat conduction analysis is performed on the engine's sealing structure to obtain the transient temperature field of the sealing structure under cyclic operating conditions. Based on the transient temperature field of the sealing structure, a first compression and springback analysis is performed on the sealing ring, flange and fasteners of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions. Based on the transient temperature field of the sealing structure and the axial deformation data, a second compression-rebound analysis is performed on the sealing ring and rigid surface of the sealing structure to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions. In the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions. Based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle, determine the maximum number of cycles in which the sealing ring will break due to ratchet damage accumulation under engine cyclic conditions. The ductility limit of the sealing ring and the equivalent plastic strain rate for each cycle are used to determine the maximum number of cycles required for the sealing ring to fracture due to ratchet damage accumulation under engine cyclic conditions, including: The stable equivalent plastic strain rate of the sealing ring is determined based on the equivalent plastic strain rate of adjacent cycles under engine cyclic conditions. The maximum number of cycles is determined based on the ductility limit and the stable equivalent plastic strain rate. The maximum number of cycles is determined by the following formula: ； in, The maximum number of cycles is indicated by ; D represents the ductility limit of the sealing ring; This represents the stable equivalent plastic strain rate; D0 represents the life safety factor; D0 represents the plastic strain accumulated in the number of cycles before the sealing ring reaches a stable equivalent plastic strain rate.

2. The test method for the use of the engine sealing ring according to claim 1, characterized in that, The engine's cyclic operating conditions include: providing pre-tightening force to the sealing ring and flange through fasteners, and multiple cyclic operating conditions consisting of applying gas pressure, loading the start-up and operating temperature field, unloading the gas pressure, and loading the shutdown and temperature recovery process. The step of performing transient heat conduction analysis on the engine's sealing structure based on the engine's operating parameters to obtain the transient temperature field of the sealing structure under cyclic operating conditions includes: Obtain transient heat conduction analysis models for the sealing ring, flange, and fasteners in the sealing structure; Based on the engine's operating ambient temperature, convective heat transfer boundary, radiative boundary, and contact heat conduction data between various components of the sealing structure, a transient heat conduction analysis model is performed to determine the temperature field during engine start-up and operation. By combining the temperature field, convective heat transfer boundary, radiation boundary, and contact heat conduction data between various parts of the sealing structure during the engine start-up and operation process, a transient heat conduction analysis is performed on the transient heat conduction analysis model during cooling to determine the temperature field during the engine shutdown and warm-up process.

3. The test method for the use of the engine sealing ring according to claim 1, characterized in that, The step involves performing a first compression-rebound analysis on the sealing ring, flange, and fasteners of the sealing structure based on the transient temperature field of the sealing structure to determine the axial deformation data under the engine cyclic operating conditions, including: By combining the contact characteristics and material properties of the sealing ring, flange, and fasteners in the sealing structure, a three-dimensional symmetric compression-rebound analysis model of the sealing ring, flange, and fasteners in the sealing structure is obtained. Based on the engine cycle conditions and the transient temperature field of the sealing structure, compression and springback analysis is performed on the three-dimensional symmetrical compression and springback analysis model to determine the axial deformation data under the engine cycle conditions.

4. The test method for the use of the engine sealing ring according to claim 1, characterized in that, The step involves performing a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field and axial deformation data of the sealing structure, to determine the equivalent plastic strain rate for each cycle under the engine's cyclic operating conditions, including: A two-dimensional axisymmetric cyclic compression and springback analysis model of the sealing ring and rigid surface in the sealing structure is obtained; In the two-dimensional axisymmetric cyclic compression and springback analysis model, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the sealing ring. Combined with the transient temperature field and the axial deformation data, the mechanical behavior of the sealing ring under engine cyclic conditions is simulated, and the equivalent plastic strain rate of each cycle under engine cyclic conditions is generated.

5. The test method for the use of the engine sealing ring according to claim 1, characterized in that, The ductility limit of the sealing ring is determined by the following formula: ； Wherein, D represents the ductility limit of the sealing ring; This indicates the area shrinkage rate of the sealing ring material.

6. A testing device for the use of an engine sealing ring, applied to the testing method for the use of an engine sealing ring as described in any one of claims 1-5, characterized in that, include: The temperature field determination unit is used to perform transient heat conduction analysis on the engine's sealing structure based on the engine's operating parameters, and to obtain the transient temperature field of the sealing structure under cyclic operating conditions. The axial deformation data determination unit is used to perform a first compression and springback analysis on the sealing ring, flange and fasteners of the sealing structure based on the transient temperature field of the sealing structure, and to determine the axial deformation data under the engine cycle conditions. The equivalent plastic strain determination unit is used to perform a second compression-rebound analysis on the sealing ring and rigid surface of the sealing structure based on the transient temperature field and axial deformation data of the sealing structure, and to determine the equivalent plastic strain rate for each cycle under the engine cyclic operating conditions; wherein, in the process of the second compression-rebound analysis, a nonlinear kinematic hardening model and a saturated isotropic hardening model are used to describe the ratchet damage data of the sealing ring under the engine cyclic operating conditions; The maximum cycle count determination unit is used to determine the maximum number of cycles in which the sealing ring will break due to ratchet damage accumulation under engine cyclic conditions, based on the ductility limit of the sealing ring and the equivalent plastic strain rate of each cycle.

7. An electronic device, characterized in that, include: processor; Memory used to store the processor's executable instructions; The processor is configured to execute the engine sealing ring usage test method according to any one of claims 1 to 5 by running instructions in the memory.

8. A computer storage medium, characterized in that, The computer storage medium stores instructions that, when executed, cause the processor to perform the test method for the use of the engine sealing ring as described in any one of claims 1 to 5.

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