Integrated elastic support radial performance calculation method, device, equipment and medium

Abstract

This invention relates to the field of engine rotor elastic support technology, and discloses a method, device, equipment, and medium for calculating the radial performance of an integrated elastic support. For the special structure of an integrated elastic support with measurable axial force, this invention establishes a three-segment mechanical model including elastic bar one, elastic ring, and elastic bar two. By calculating the moment of inertia of each section about its own centroidal principal axis, the total deflection of the free end under radial load is obtained using the superposition method, and the radial stiffness is then determined. Simultaneously, based on the bending moment distribution, the fatigue stress at each connection end on elastic bar one and elastic bar two is calculated. This provides a dedicated analytical calculation method for radial stiffness and fatigue stress for this novel elastic support structure, filling the gap in existing technology which is only applicable to single-segment elastic bars, enabling designers to quickly and efficiently obtain the radial stiffness and stress level of the elastic support.

Description

Technical Field

[0001] This invention relates to the field of engine rotor elastic support technology, specifically to an integrated elastic support radial performance calculation method, device, equipment, and medium. Background Technology

[0002] Rotor axial force is a crucial performance indicator for aero-engines. If the axial force does not meet design requirements, the bearings will operate under overload or light-load slippage conditions for extended periods, severely impacting the engine's lifespan and reliability. Obtaining the magnitude of the rotor axial force is essential for evaluating the rationality of the engine's aerodynamic design, the normality of bearing loads, the appropriateness of bearing selection, and for improving the air system design. Before the engine's maiden flight, a pressure balance test must be completed to ensure that the bearings do not slip and are not damaged, thus preserving the performance of the rolling bearings. Therefore, obtaining the magnitude of the rotor axial force is of paramount importance to engine design.

[0003] The elastic support is a key elastic element in the rotor support system of an aero-engine. Installed between the bearing outer ring and the casing, it elastically transmits the axial and radial loads applied by the rotor via the bearing to the casing. The rotor's axial force is transmitted through this path, providing a basis for measurement at the elastic support. Currently, elastic supports are classified into two types: separate and integrated. In a separate elastic support, the bearing outer ring and the elastic support are independent parts, allowing for the measurement of rotor axial force by installing a force-measuring ring between them. However, in an integrated elastic support (i.e., a bearing outer ring integrated elastic support), the bearing outer ring and the elastic support body are designed as a single unit, meaning they are linked. Unlike a separate elastic support, a force-measuring ring cannot be installed between the bearing outer ring and the elastic support, making axial force measurement in a bearing outer ring integrated elastic support challenging.

[0004] Integrated spring supports are characterized by their compact structure, light weight, stable force transmission, and fewer vibration failures. Compared with split spring supports, bearing outer ring integrated spring supports have unique advantages in rotor vibration reduction, impact resistance, and instability prevention, which has led to their gradual and widespread use in engine rotor supports.

[0005] Currently, for integrated spring supports, due to the lack of a dedicated force measuring unit and the inability to install a force measuring ring, strain gauges can only be directly attached to the spring clip when measuring rotor axial force. However, the deformation of the spring clip under axial force is extremely small, resulting in a weak strain gauge output signal. The measurement sensitivity and signal-to-noise ratio of this method are insufficient to meet the requirements of high-precision axial force measurement. More importantly, whether it is a split-type or integrated spring support, its design only focuses on radial support stiffness and fatigue life. Axial deformation under axial force is not a design constraint, and axial stiffness and axial strength have never been considered in the design.

[0006] To address the challenge of axial force measurement in integrated spring supports, integrating an axial force measuring unit into the spring support body to form an integrated spring support capable of measuring axial force has become a feasible solution. This scheme connects two intersecting spring bars through the axial force measuring unit, aiming to convert the axial force into the deformation of the axial force measuring unit for measurement.

[0007] However, the addition of the axial force measuring unit inevitably affects the original radial stiffness and strength characteristics of the spring support. This is because an integrated spring support with measurable axial force requires not only good axial force measuring performance but also suitable radial stiffness and strength, which are often contradictory. Existing methods for evaluating the radial stiffness and strength of spring supports are only applicable to ordinary single-segment spring support structures. They are not applicable to the aforementioned integrated spring support with measurable axial force connected by an elastic ring (i.e., the axial force measuring unit) with two intersecting spring segments. Currently, there are no publicly reported methods for evaluating the radial stiffness and strength of this integrated spring support with measurable axial force. Therefore, it is necessary to specifically design the integrated spring support with measurable axial force and study its radial stiffness and strength characteristics. Summary of the Invention

[0008] This invention provides a method, apparatus, equipment, and medium for calculating the radial performance of an integrated elastic support, in order to solve the technical problem that the radial stiffness and fatigue stress calculation formulas of existing single-segment elastic supports are no longer applicable due to the special structure of the integrated elastic support with measurable axial force (including two interlaced elastic bars connected by an elastic ring), thus making it impossible to quickly and accurately evaluate the strength corresponding to its radial stiffness and fatigue stress, which affects its structural design and performance optimization.

[0009] In a first aspect, the present invention provides a method for calculating the radial performance of an integrated elastic support, comprising: simplifying the axially measurable integrated elastic support into a three-segment mechanical model, the three-segment mechanical model comprising a first elastic bar, an elastic ring, and a second elastic bar connected in sequence, the end of the first elastic bar away from the elastic ring being a fixed end, and the end of the second elastic bar away from the elastic ring being a free end, used to bear radial loads; calculating the moments of inertia of the cross sections of the first elastic bar, the elastic ring, and the second elastic bar about their own centroidal principal axes according to the cross-sectional geometry of the first elastic bar, the elastic ring, and the second elastic bar respectively; calculating the total deflection of the free end under radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each cross section about its own centroidal principal axes; determining the radial stiffness of the axially measurable integrated elastic support based on the radial load and the total deflection; and calculating the fatigue stress at each connecting end of the first elastic bar and the second elastic bar based on the bending moment distribution of the three-segment mechanical model under radial load, combined with the moments of inertia of the cross sections of the first elastic bar and the second elastic bar about their own centroidal principal axes.

[0010] This invention establishes a three-segment mechanical model for the special structure of an integrated elastic support with measurable axial force, comprising elastic clip one, elastic ring, and elastic clip two. By calculating the moment of inertia of each section about its own centroidal principal axis, the total deflection of the free end under radial load is obtained using the superposition method, and the radial stiffness is then determined. Simultaneously, based on the bending moment distribution, the fatigue stress at each connection end on elastic clip one and elastic clip two is calculated. This provides a dedicated analytical calculation method for radial stiffness and fatigue stress for this novel elastic support structure, filling the gap in existing technologies that are only applicable to single-segment elastic clip supports. This enables designers to quickly and efficiently obtain the radial stiffness and stress level of the elastic support, providing a theoretical basis for the structural design and performance optimization of the elastic support.

[0011] In one optional embodiment, the step of calculating the moments of inertia of the cross-sections of spring clip one, elastic ring, and spring clip two about their own centroidal principal axes, based on the cross-sectional geometry of spring clip one, elastic ring, and spring clip two, respectively, includes: calculating the moments of inertia of the cross-sections of spring clip one and spring clip two about their own centroidal principal axes, based on the cross-sectional shapes and geometric dimensions of spring clip one and spring clip two; and calculating the moment of inertia of the cross-section of elastic ring about its own centroidal principal axis, based on the annular cross-section of elastic ring and its inner and outer diameters.

[0012] The above implementation method calculates the moments of inertia of the cross sections of spring clip one, spring clip two, and elastic ring about their own centroidal principal axes separately. Different calculation methods are used for different structural components and different cross-sectional shapes: for spring clip one and spring clip two, their moments of inertia about their own centroidal principal axes are calculated based on their cross-sectional shapes and geometric dimensions; for the elastic ring, the calculation is based on the inner and outer diameters of its annular cross section. This categorized calculation method fully considers the cross-sectional characteristics of different components in the integrated axial force measurable spring support. It ensures the accuracy of the moment of inertia calculation of the spring clips about their own centroidal principal axes while also taking into account the special characteristics of the elastic ring as an annular cross section. This provides accurate input parameters for subsequent deflection calculation, stiffness determination, and fatigue stress analysis, thereby improving the accuracy and reliability of the entire spring support radial performance calculation method.

[0013] In an optional implementation, the method further includes: calculating the total rotation angle of the free end under radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis; and determining the bending moment at the free end without considering the actual angular constraint capacity of the free end based on the total rotation angle and the preset total rotation angle condition.

[0014] The above implementation method calculates the total rotation angle of the free end under radial load using the superposition method, and determines the bending moment without considering the actual angular constraint capacity of the free end based on this total rotation angle and a preset total rotation angle condition. This provides a key intermediate parameter for the mechanical analysis of the integrated elastic support with measurable axial force. The determination of this bending moment lays the foundation for subsequent calculations of the deflection of the free end under bending moment and provides a benchmark for subsequent correction calculations considering the actual angular constraint capacity.

[0015] In one optional implementation, the step of calculating the total rotation angle of the free end under radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis includes: calculating the first rotation angle of the free end under radial load only and the second rotation angle under bending moment only based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis; and superimposing the first rotation angle and the second rotation angle to obtain the total rotation angle of the free end under radial load.

[0016] The above implementation method decomposes the radial load into radial and bending moment components, calculates the first rotation angle of the free end under radial load only and the second rotation angle under bending moment only, and then superimposes the two to obtain the total rotation angle. This method decomposes the complex composite load into two simple single load conditions, making the rotation angle calculation process clearer and more standardized. It also provides accurate input for subsequent determination of bending moment based on the total rotation angle, ensuring the theoretical rigor and engineering feasibility of the entire calculation method.

[0017] In one optional implementation, the step of calculating the total deflection of the free end under radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis includes: calculating the first deflection of the free end under radial load only and the second deflection under bending moment only based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis; and superimposing the first deflection and the second deflection to obtain the total deflection of the free end under radial load.

[0018] The above implementation method decomposes the radial load into radial and bending moment components, calculates the first deflection of the free end under radial load only and the second deflection under bending moment only, and then superimposes the two to obtain the total deflection. This method transforms the complex deflection calculation under combined loads into a simple calculation of two single load conditions, ensuring the standardization of the calculation process and improving the accuracy of the calculation results. By considering the contributions of radial force and bending moment components to deflection separately, the influence of different load components on the deformation of the spring support can be clearly understood, providing accurate input for subsequent stiffness calculations, and laying a theoretical foundation for the performance analysis and optimization design of the spring support structure.

[0019] In one optional implementation, the step of determining the radial stiffness of the axially force-measurable integrated elastic support based on the radial load and total deflection includes: determining the basic radial stiffness of the axially force-measurable integrated elastic support without considering the actual angular constraint capacity at the free end, based on the ratio of radial load to total deflection; introducing a moment distribution coefficient to correct the basic radial stiffness, thereby obtaining the actual radial stiffness of the axially force-measurable integrated elastic support considering the actual angular constraint capacity at the free end, wherein the moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity at the free end without considering the actual angular constraint capacity at the free end.

[0020] The above implementation method first determines the foundation radial stiffness without considering the actual angular constraint capacity at the free end based on the ratio of radial load to total deflection. Then, a moment distribution coefficient is introduced to correct it, ultimately yielding the actual radial stiffness considering the actual angular constraint capacity at the free end. This step-by-step correction calculation method fully embodies the progressive analysis approach from ideal model to real working conditions. This method retains the simplicity of calculation under ideal boundary conditions while approximating real working conditions through correction coefficients, making the calculated radial stiffness more consistent with engineering reality. This provides more accurate input parameters for the structural design of the spring support and the dynamic analysis of the rotor system.

[0021] In one optional implementation, the step of calculating the fatigue stress at each connection end of spring clips one and two based on the bending moment distribution under radial load using a three-segment mechanical model, combined with the moments of inertia of the cross sections of spring clip one and spring clip two about their own centroidal principal axes, includes: determining the first bending moment at each connection end of spring clip one and spring clip two without considering the actual angular constraint capacity at the free end, based on the bending moment distribution under radial load using a three-segment mechanical model; and calculating the actual angular constraint capacity at the free end without considering the first bending moment and the moments of inertia of the cross sections of spring clips one and two about their own centroidal principal axes. The basic fatigue stress at each connection end of spring clip 1 and spring clip 2 is calculated. A moment distribution coefficient is introduced to correct the first moment, resulting in a second moment at each connection end of spring clip 1 and spring clip 2 when considering the actual angular constraint capacity of the free end. Based on the second moment and the moments of inertia of the sections of spring clip 1 and spring clip 2 about their own centroidal principal axes, the actual fatigue stress at each connection end of spring clip 1 and spring clip 2 when considering the actual angular constraint capacity of the free end is calculated. The moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity of the free end when the actual angular constraint capacity of the free end is not considered.

[0022] The above implementation method first determines the first bending moment based on the bending moment distribution without considering the actual angular constraint capacity of the free end and calculates the foundation fatigue stress. Then, it introduces a bending moment distribution coefficient to correct the first bending moment to obtain the second bending moment and calculates the actual fatigue stress. This step-by-step correction calculation method completely realizes the fatigue stress analysis from ideal boundary conditions to actual working conditions. This method can not only obtain the foundation stress level at each connection end of spring clip one and spring clip two without considering angular constraints, but more importantly, it corrects the bending moment by introducing a bending moment distribution coefficient, thereby obtaining the actual fatigue stress that is closer to the actual engineering situation. Through the step-by-step correction calculation method, this method can simultaneously obtain the foundation fatigue stress without considering the actual angular constraint capacity of the free end and the actual fatigue stress considering the actual angular constraint capacity of the free end. This allows designers to fully grasp the stress level of the spring clip under ideal boundary conditions and actual working conditions, providing multi-dimensional reference for the structural design, strength verification, and fatigue life assessment of the spring clip.

[0023] Secondly, the present invention provides an integrated elastic support radial performance calculation device, comprising: a mechanical model construction module for simplifying the axial force measurable integrated elastic support into a three-segment mechanical model, the three-segment mechanical model comprising a first elastic bar, an elastic ring, and a second elastic bar connected in sequence, the end of the first elastic bar away from the elastic ring being a fixed end, and the end of the second elastic bar away from the elastic ring being a free end, used to bear radial loads; and a moment of inertia calculation module for calculating the moment of inertia of the cross-sections of the first elastic bar, the elastic ring, and the second elastic bar according to their cross-sectional geometry. The system includes: a moment of inertia of its own centroidal principal axis; a deflection calculation module, used to calculate the total deflection of the free end under radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis; a radial stiffness determination module, used to determine the radial stiffness of the axial force measurable integrated elastic support based on the radial load and the total deflection; and a fatigue stress determination module, used to calculate the fatigue stress at each connection end of elastic clip one and elastic clip two based on the bending moment distribution under radial load of the three-segment mechanical model and the moments of inertia of the sections of elastic clip one and elastic clip two about their own centroidal principal axes.

[0024] Thirdly, the present invention provides an electronic device, comprising: a memory and a processor, wherein the memory and the processor are communicatively connected to each other, the memory stores computer instructions, and the processor executes the computer instructions to perform the integrated elastic support radial performance calculation method of the first aspect or any corresponding embodiment described above.

[0025] Fourthly, the present invention provides a computer-readable storage medium storing computer instructions for causing a computer to execute the integrated elastic support radial performance calculation method of the first aspect or any corresponding embodiment described above. Attached Figure Description

[0026] To more clearly illustrate the specific embodiments of the present invention or the technical solutions in the prior art, the drawings used in the description of the specific embodiments or the prior art will be briefly introduced below. Obviously, the drawings described below are some embodiments of the present invention. For those skilled in the art, other drawings can be obtained from these drawings without creative effort.

[0027] Figure 1 This is a schematic diagram of the first process of the integrated elastic support radial performance calculation method according to an embodiment of the present invention; Figure 2 This is a schematic diagram of the second process for calculating the radial performance of an integrated elastic support according to an embodiment of the present invention; Figure 3 Main view of the integrated elastic support with measurable axial force; Figure 4 A schematic diagram of a three-segment mechanical model of an integrated elastic support with measurable axial force; Figure 5 Rectangular cross-sectional views of integrated axial force measuring spring clip one and spring clip two; Figure 6 Trapezoidal cross-sectional views of integrated elastic clip 1 and elastic clip 2 with measurable axial force; Figure 7 A fan-shaped annular cross-sectional view of integrated elastic clip 1 and elastic clip 2 with measurable axial force; Figure 8 This is a schematic diagram illustrating the deformation of an integrated elastic support with measurable axial force under radial force, calculated using the superposition method based on a three-segment mechanical model. Figure 9 This is a schematic diagram illustrating the deformation of an integrated elastic support with measurable axial force under bending moment, calculated using the superposition method based on a three-segment mechanical model. Figure 10 An integrated elastic support internal force diagram with measurable axial force; Figure 11 This is a structural block diagram of the integrated elastic support radial performance calculation device according to an embodiment of the present invention; Figure 12 This is a schematic diagram of the hardware structure of an electronic device according to an embodiment of the present invention; Wherein, 1 represents spring bar one; 2 represents elastic ring; and 3 represents spring bar two. Detailed Implementation

[0028] To make the objectives, technical solutions, and advantages of the embodiments of the present invention clearer, the technical solutions of the embodiments of the present invention will be clearly and completely described below with reference to the accompanying drawings. Obviously, the described embodiments are only some embodiments of the present invention, not all embodiments. Based on the embodiments of the present invention, all other embodiments obtained by those skilled in the art without creative effort are within the scope of protection of the present invention.

[0029] It is understood that before using the technical solutions disclosed in the various embodiments of the present invention, users should be informed of the types, scope of use, and usage scenarios of the personal information involved in the present invention and their authorization should be obtained in accordance with relevant laws and regulations through appropriate means.

[0030] The terms "first" and "second" are used for descriptive purposes only and should not be construed as indicating or implying relative importance or implicitly specifying the number of technical features indicated. Thus, a feature defined as "first" or "second" may explicitly or implicitly include one or more of that feature. In the description of this invention, "a plurality of" means two or more, unless otherwise explicitly specified.

[0031] For ordinary spring supports, there are specific formulas for calculating their radial stiffness and fatigue stress. The formula for calculating the radial stiffness of an ordinary spring support is as follows: or The fatigue stress formula for a common elastic support is: or ,in, Number of pop-up bars The width of the pop-up bar. For the thickness of the elastic bar, The length of the elastic bar. For elastic modulus, This represents the displacement at the free end of the spring support. The above formula is not applicable to the radial stiffness and fatigue stress calculation of an integrated spring support with measurable axial force for two intersecting spring clips connected by elastic ring 2. Instead, it directly uses the two intersecting spring clips (with radial stiffnesses of...) and ) and elastic ring 2 (radial stiffness is Formula for calculating the series radial stiffness To calculate the radial stiffness of the integrated elastic support with measurable axial force. There is a considerable margin of error. There are currently no publicly available reports on precise analytical calculation formulas for the radial stiffness and fatigue stress of this integrated elastic support structure with measurable axial force.

[0032] Because existing elastic support structures are single-segment elastic supports, their radial stiffness and fatigue stress formulas are only derived for this single-segment elastic support. However, the radial stiffness and fatigue stress calculation method for the axially force-measurable integrated elastic support of this invention is for two interlocking elastic support segments (connected by an elastic ring 2). The aforementioned formulas for the radial stiffness and fatigue stress of a single-segment elastic support are no longer applicable. In other words, there are no analytical calculation formulas for the radial stiffness and fatigue stress of this axially force-measurable integrated elastic support structure. Analytical calculation methods can provide technical means for evaluating the radial stiffness and strength of the axially force-measurable integrated elastic support, and can also provide guidance for the subsequent structural parameter sensitivity analysis and optimization design of the axially force-measurable integrated elastic support. Therefore, it is not yet possible to use analytical calculation methods to evaluate the radial stiffness and strength of the axially force-measurable integrated elastic support, or to provide technical support and guidance for the subsequent structural parameter sensitivity analysis and optimization design. Based on this, the present invention provides an integrated elastic support radial performance calculation method, device, equipment and medium to solve the technical problem that the radial stiffness and fatigue stress calculation formulas of existing single-segment elastic supports are no longer applicable due to the special structure of the integrated elastic support with measurable axial force (including two interlaced elastic bars connected by an elastic ring 2), thus making it impossible to quickly and accurately evaluate the strength corresponding to its radial stiffness and fatigue stress, which affects its structural design and performance optimization.

[0033] According to an embodiment of the present invention, an embodiment of an integrated elastic support radial performance calculation method is provided. It should be noted that the steps shown in the flowchart in the accompanying drawings can be executed in a computer system such as a set of computer-executable instructions. Furthermore, although a logical order is shown in the flowchart, in some cases, the steps shown or described may be executed in a different order than that shown here.

[0034] This embodiment provides a method for calculating the radial performance of an integrated elastic support. Figure 1 This is a flowchart of the integrated elastic support radial performance calculation method according to an embodiment of the present invention, such as... Figure 1 As shown, the process includes the following steps: Step S101: The axial force measurable integrated spring support is simplified into a three-segment mechanical model. The three-segment mechanical model includes spring bar 1, elastic ring 2 and spring bar 3 connected in sequence. The end of spring bar 1 away from elastic ring 2 is the fixed end, and the end of spring bar 3 away from elastic ring 2 is the free end, which is used to bear radial load.

[0035] This step establishes a simplified analytical model for the special structure of the integrated spring support with measurable axial force. The spring support is characterized by two intersecting spring clips (spring clip 1 and spring clip 3) connected by an elastic ring 2. Therefore, it is simplified into three parts: spring clip 1, elastic ring 2, and spring clip 3 connected sequentially. In this embodiment, this is called a three-segment mechanical model. The "fixed end" refers to the end of spring clip 1 connected to the housing, which is considered a fixed support boundary condition with zero displacement and rotation angle in the mechanical analysis. The "free end" refers to the end of spring clip 3 bearing the radial load, used to simulate the radial force exerted by the bearing on the spring support. This mechanical model provides the boundary conditions and force analysis basis for subsequent calculations.

[0036] Step S102: Based on the cross-sectional geometry of spring clip 1, elastic ring 2, and spring clip 3, calculate the moments of inertia of the cross-sections of spring clip 1, elastic ring 2, and spring clip 3 about their own centroidal principal axes.

[0037] This step calculates the moment of inertia of each section about its own principal centroidal axis based on the cross-sectional geometry of elastic clip 1, elastic ring 2, and elastic clip 3. The "moment of inertia" is a geometric indicator that measures the section's resistance to bending deformation; its value depends on the shape and size of the section. The cross-sectional shapes of elastic clips 1 and 3 may be rectangular, trapezoidal, or fan-shaped, and their moments of inertia about their own principal centroidal axes need to be calculated based on their specific shapes and geometric dimensions. Elastic ring 2 is an annular section, and its moment of inertia about its own principal centroidal axis needs to be calculated based on its inner and outer diameters. This step provides crucial cross-sectional geometric parameters for subsequent calculations.

[0038] Step S103: Based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis, the total deflection of the free end under radial load is calculated using the superposition method.

[0039] This step, based on the aforementioned three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axes, uses the superposition method to calculate the total deflection of the free end under radial load. The "superposition method" is based on the superposition principle of linear elastic systems, decomposing the complex composite load into several individual load conditions, calculating them separately, and then linearly superimposing them. Specifically, the radial load is decomposed into radial and bending moment components. The first deflection of the free end under radial load alone and the second deflection under bending moment alone are calculated separately, and then the two are superimposed to obtain the total deflection. The bending moment in this step is the bending moment at the free end without considering the actual angular constraint capacity of the free end; it needs to be pre-determined by calculating the total rotation angle and combining it with preset total rotation angle conditions (such as zero rotation angle). This step provides crucial deformation input for the radial stiffness calculation in step S104.

[0040] Step S104: Based on the radial load and total deflection, determine the radial stiffness of the integrated elastic support with measurable axial force.

[0041] In this step, "radial stiffness" is a mechanical index characterizing the ability of the projectile to resist radial deformation, defined as the ratio of the radial load to the resulting radial displacement (i.e., total deflection). After calculating the total deflection of the free end under radial load in step S103, dividing this total deflection by the applied radial load yields the radial stiffness of the projectile. This radial stiffness is a core parameter for evaluating the performance of the projectile and provides an important basis for subsequent rotor dynamics analysis and projectile structural optimization design.

[0042] Step S105: Based on the bending moment distribution of the three-segment mechanical model under radial load, and combined with the moments of inertia of the sections of elastic clip 1 and elastic clip 2 about their own centroidal principal axes, calculate the fatigue stress at each connection end of elastic clip 1 and elastic clip 2.

[0043] In this step, "bending moment distribution" refers to the distribution pattern of bending moments generated by each section inside the spring support along the axial direction under radial load. Through mechanical analysis, the bending moment values ​​at key locations such as the connection between spring clip 1 and the fixed end, the connection between spring clip 1 and elastic ring 2, and the connection between spring clip 2 and elastic ring 2 can be determined. "Fatigue stress" refers to the stress value at which the spring support gradually expands due to stress concentration and the cumulative damage from microcracks under alternating loads, eventually leading to fracture. Based on the bending moment distribution and the moments of inertia of the sections at each connection end about their own centroidal principal axes, the fatigue stress values ​​at each key location are calculated using stress formulas. This fatigue stress is a key parameter for evaluating the fatigue strength of the spring support and predicting its fatigue life.

[0044] The integrated elastic support radial performance calculation method provided in this embodiment establishes a three-segment mechanical model including elastic bar 1, elastic ring 2, and elastic bar 2 3 for the special structure of the integrated elastic support with measurable axial force. By calculating the moment of inertia of each section about its own centroidal principal axis, the total deflection of the free end under radial load is obtained by superposition method, and then the radial stiffness is determined. At the same time, the fatigue stress at each connection end on elastic bar 1 and elastic bar 2 3 is calculated based on the bending moment distribution. This provides a dedicated analytical calculation method for radial stiffness and fatigue stress for this novel elastic support structure, filling the gap in the calculation of existing technology which is only applicable to single-segment elastic bars. It enables designers to quickly and efficiently obtain the radial stiffness and stress level of the elastic support, providing a theoretical basis for the structural design and performance optimization of the elastic support.

[0045] This embodiment provides another method for calculating the radial performance of an integrated elastic support. Figure 2 This is a flowchart of the integrated elastic support radial performance calculation method according to an embodiment of the present invention, such as... Figure 2 As shown, the process includes the following steps: Step S201: The axial force measurable integrated spring support is simplified into a three-segment mechanical model. The three-segment mechanical model includes spring bar 1, elastic ring 2 and spring bar 3 connected in sequence. The end of spring bar 1 away from elastic ring 2 is the fixed end, and the end of spring bar 3 away from elastic ring 2 is the free end, which is used to bear radial load.

[0046] The method of this invention is based on an integrated elastic support with measurable axial force, which can also be simply referred to as an integrated elastic support with measurable axial force. Figure 3 As shown, it consists of a base, several spring bars 1 and 3, and a bearing outer ring. Spring bars 1 and 3 are connected by an elastic ring 2 and are staggered relative to the elastic ring 2.

[0047] like Figure 4 As shown, this is a three-segment mechanical model of an integrated elastic support with measurable axial force, including... part, Duan He part, Segment 1 is the elastic bar. The segment is an elastic ring 2. Segment 2 is spring clip 3. Specifically, the integrated spring support mechanical model with measurable axial force can be simplified to spring clip 1. Point-fixed support, spring bar 23 Radial force is applied at the point (end of the spring bearing). and bending moment The loads, and the lengths of spring clip 1, elastic ring 2, and spring clip 3 are respectively , and Furthermore, the length of the integrated elastic support section with measurable axial force is... The elastic modulus is .

[0048] Step S202: Based on the cross-sectional geometry of spring clip 1, elastic ring 2, and spring clip 3, calculate the moments of inertia of the cross-sections of spring clip 1, elastic ring 2, and spring clip 3 about their own centroidal principal axes.

[0049] Specifically, step S202 above includes: Step S2021: Based on the cross-sectional shape and geometric dimensions of spring clip 1 and spring clip 2, calculate the moments of inertia of the cross-sections of spring clip 1 and spring clip 2 about their own centroidal principal axes.

[0050] Step S2022: Based on the annular cross-section of the elastic ring 2 and its inner and outer diameters, calculate the moment of inertia of the cross-section of the elastic ring 2 about its own centroidal principal axis.

[0051] For example, the section of the elastic bar 1 is about its centroidal principal axis The moment of inertia is The section of elastic ring 2 is about its centroidal principal axis The moment of inertia is The section of the elastic bar 23 is aligned with its centroidal principal axis. The moment of inertia is .

[0052] like Figure 5 As shown, when spring clip 1 and spring clip 2 are rectangular cross-sections, all spring clips 1 and 2 are about their own centroids. (Center) The distance from the long side of the rectangular section is The centroidal principal axis Moment of inertia and for:

[0053] In the formula, Number of pop-up bars The width of the rectangular cross-section of elastic bar 1 and elastic bar 3. The height of the rectangular cross-section of elastic bar 1 and elastic bar 2 3.

[0054] Reference Figure 6 When elastic clip 1 and elastic clip 2 have trapezoidal cross-sections, all elastic clips 1 and 2 about their own centroids (Center) The height of the distance from the long side of the trapezoidal section is The centroidal principal axis Moment of inertia and for:

[0055] In the formula, Number of pop-up bars The width of the shorter side of the trapezoidal cross-section of elastic bar 1 and elastic bar 2 is given by [reference to a specific unit]. Let the width of the longer side of the trapezoidal cross-section of elastic bar 1 and elastic bar 2 be denoted as . The height of the trapezoidal cross-section of elastic bar 1 and elastic bar 2 3.

[0056] Reference Figure 7 When spring bar 1 and spring bar 2 are fan-shaped When the cross-section is cut, all spring clips 1 and 2 are about their own centroids. (Center) The centroid of the entire cross section formed by all spring clips 1 or 3 The distance is , Fan-shaped Centroid To the centroid of the entire cross section distance, Fan-shaped Centroid To the centroid of the entire cross section distance, , They are fan rings Centroid To the fan shape Centroid and sector Centroid The centroidal principal axis (distance) Moment of inertia and for:

[0057] In the formula, Number of pop-up bars The inner arc of the annular section of elastic clip 1 and elastic clip 2 extends to the centroid of the entire section. distance, The thickness of the annular cross-section of spring clip 1 and spring clip 2 is given. It is half the central angle of the annular cross section of spring clip 1 and spring clip 2.

[0058] Elastic ring 2 relative to its own centroid centroidal principal axis Moment of inertia for:

[0059] In the formula, , These are the inner and outer diameters of the elastic ring 2, respectively.

[0060] Step S203: Based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis, the total deflection of the free end under radial load is calculated using the superposition method.

[0061] Specifically, step S203 above includes: Step S2031: Based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, calculate the first deflection of the free end under radial load only, and the second deflection under bending moment only.

[0062] For example, when the free end (i.e., point D) is subjected only to radial load (i.e., radial force) When the force is applied, calculate the first deflection at that point. For example... Figure 8 As shown, the axial force can be measured by an integrated elastic support. The point is only subjected to radial force When in action, Point deflection It is possible Point fixed ( The point is only subjected to radial force effect), Point fixed ( The point is only subjected to radial force (function) and Point fixed ( The point is only subjected to radial force When the function is Point deflection , , The corresponding results are obtained by superposition. for Point fixed, The point is only subjected to radial force When in action Deflection at a point for Point fixed, The point is only subjected to radial force When in action The deflection at a point. Specifically: Integrated spring support with measurable axial force Point fixed, The point is only subjected to radial force When in action, Point deflection for:

[0063] When the free end (i.e., point D) is only subjected to bending moment When applied, calculate the second deflection at that point. For example... Figure 9 As shown, the axial force can be measured by an integrated elastic support. The point is only subjected to bending moment When in action, Point deflection It is possible Point fixed ( The point is only subjected to bending moment effect), Point fixed ( The point is only subjected to bending moment (function) and Point fixed ( The point is only subjected to bending moment When the function is Point deflection , , The corresponding results are obtained by superposition. for Point fixed, The point is only subjected to bending moment When in action Deflection at a point for Point fixed, The point is only subjected to bending moment When in action The deflection at a point. Specifically: Integrated spring support with measurable axial force Point fixed, The point is only subjected to bending moment When in action, Point deflection for:

[0064] Step S2032: The first deflection and the second deflection are superimposed to obtain the total deflection of the free end under radial load.

[0065] Integrated spring support with measurable axial force Point fixed, Point at radial force and bending moment Under the combined effect, Point deflection for:

[0066] The bending moment in step S203 above is the bending moment at the free end without considering the actual angular constraint capacity of the free end. Since this bending moment is an unknown quantity, it is necessary to obtain the bending moment at the free end without considering the actual angular constraint capacity during the execution of step S203. In an optional embodiment, the bending moment at the free end without considering the actual angular constraint capacity can be obtained through the following steps: Step a1: Based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis, the total rotation angle of the free end under radial load is calculated using the superposition method.

[0067] Based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, the first rotation angle of the free end under radial load alone and the second rotation angle under bending moment alone are calculated. The first and second rotation angles are superimposed to obtain the total rotation angle of the free end under radial load.

[0068] For example, when the free end (i.e., point D) is subjected only to radial load (i.e., radial force) When this function is applied, calculate the first turning angle at that point. For example... Figure 8 As shown, the axial force can be measured by an integrated elastic support. The point is only subjected to radial force When in action, The corner of the point It is possible Point fixed ( The point is only subjected to radial force effect), Point fixed ( The point is only subjected to radial force (function) and Point fixed ( The point is only subjected to radial force When the function is The corner of the point , , The corresponding results are obtained by superposition. for Point fixed, The point is only subjected to radial force When in action The corner of the point, = , for Point fixed, The point is only subjected to radial force When in action The corner of the point, = Specifically: Integrated spring support with measurable axial force Point fixed, The point is only subjected to radial force When in action, The corner of the point for:

[0069] When the free end (i.e., point D) is only subjected to bending moment When applied, calculate the second turning angle at that point. For example... Figure 9 As shown, the axial force can be measured by an integrated elastic support. The point is only subjected to bending moment When in action, The corner of the point and deflection It is possible Point fixed ( The point is only subjected to bending moment effect), Point fixed ( The point is only subjected to bending moment (function) and Point fixed ( The point is only subjected to bending moment When the function is The corner of the point , , The corresponding results are obtained by superposition. for Point fixed, The point is only subjected to bending moment When in action The corner of the point, = , for Point fixed, The point is only subjected to bending moment When in action The corner of the point, = Specifically: Integrated spring support with measurable axial force Point fixed, The point is only subjected to bending moment When in action, The corner of the point for:

[0070] Integrated spring support with measurable axial force Point fixed, Point at radial force and bending moment Under the combined effect, The corner of the point for:

[0071] Step a2: Based on the total rotation angle and the preset total rotation angle condition, determine the bending moment at the free end when the actual angular constraint capacity of the free end is not considered.

[0072] Specifically, the preset total turning angle condition is as follows: The angle of the point satisfies Therefore, without considering the actual angular constraint capacity of the free end, the bending moment at the free end is:

[0073] Step S204: Based on the radial load and total deflection, determine the radial stiffness of the integrated elastic support with measurable axial force.

[0074] Specifically, step S204 above includes: Step S2041: Based on the ratio of radial load to total deflection, determine the basic radial stiffness of the integrated elastic support with measurable axial force when the actual angular constraint capacity of the free end is not considered.

[0075] Not considering The radial stiffness of the integrated elastic support base can be measured by the axial force of the actual angular constraint capability. for

[0076] Furthermore, based on the above results, it can be concluded that, without considering... The axial force of the actual angular constraint capability of the integrated elastic support can be measured by the radial force. and Point deflection The relationship can be represented as:

[0077] Through radial force and Point deflection The relationship can be used to calculate the deformation of the spring support under radial load, and then evaluate the influence of the spring support on the critical speed and vibration characteristics of the rotor system, providing core input for the structural design and parameter optimization of the spring support.

[0078] Step S2042 introduces a moment distribution coefficient to correct the radial stiffness of the foundation, obtaining the actual radial stiffness of the integrated elastic support with measurable axial force when considering the actual angular constraint capacity of the free end. The moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity of the free end when the actual angular constraint capacity of the free end is not considered.

[0079] Specifically, considering The actual angular constraint capacity of the point is determined by introducing a moment distribution factor. , . Depend on The angular constraint capability of the point is determined. When the point is free or hinged, ; When the point has no corner constraint, Integrated spring support with measurable axial force. The point is close to having no corner constraints, but not completely without corner constraints, so it depends on the actual situation ( It will be slightly greater than 0.5). such as correction factor .

[0080]

[0081] Therefore, considering The actual radial stiffness of the integrated elastic support can be measured by the axial force of the actual angular constraint capability. for:

[0082] Furthermore, based on the above results, it can be concluded that, considering The axial force of the actual angular constraint capability of the integrated elastic support can be measured by the radial force. and Point deflection The relationship can be represented as:

[0083] The radial stiffness of the axially force-measurable integrated spring support determines the critical speed of the rotor system and the radial displacement at the rotor system bearings. By designing a suitable radial stiffness for the axially force-measurable integrated spring support, the critical speed of the rotor system can be kept away from its commonly used operating speed while maintaining a certain critical speed margin (e.g., 20% critical speed margin). The radial displacement at the rotor system bearings can be used to limit excessive radial deflection of the rotor system (e.g., radial deflection not exceeding 0.4 times the single-sided clearance of the oil film to avoid rotor-stator rubbing) and excessive fatigue stress (e.g., the fatigue stress of the spring bar does not exceed the fatigue limit to avoid fatigue failure of the spring bar).

[0084] Step S205: Based on the bending moment distribution of the three-segment mechanical model under radial load, and combined with the moments of inertia of the sections of elastic clip 1 and elastic clip 2 about their own centroidal principal axes, calculate the fatigue stress at each connection end of elastic clip 1 and elastic clip 2.

[0085] Specifically, step S205 includes: Step S2051: Based on the bending moment distribution of the three-segment mechanical model under radial load, determine the first bending moment at each connection end of elastic clip 1 and elastic clip 2 3 without considering the actual angular constraint capacity of the free end. Based on the first bending moment and the moment of inertia of the cross sections of elastic clip 1 and elastic clip 2 3 about their own centroidal principal axes, calculate the basic fatigue stress at each connection end of elastic clip 1 and elastic clip 2 3 without considering the actual angular constraint capacity of the free end.

[0086] Specifically, such as Figure 10 The figure shown is the internal force diagram of the integrated elastic support with measurable axial force, where Q B and Q C Let B and C be the shear forces, respectively. Ignore the shear forces at points B and C. Integrated elastic support with measurable axial force for actual angular constraint capability at the point point, point, point, First bending moment at point , , , They are respectively: , , , .

[0087] Based on the first bending moment, calculate the minimum and maximum fatigue stresses at key points on spring clip 1 and spring clip 3, respectively.

[0088] In one embodiment, the connecting end surfaces of spring strip 1 and spring strip 3 are taken as key points, namely... Figure 4 For points A, B, C, and D in the diagram, the method for calculating the maximum and minimum fatigue stress values ​​at these key points is as follows: generally , without considering The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip 1. Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0089]

[0090] Not considering The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip 1. Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0091]

[0092] Not considering The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip II.3 Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0093]

[0094] Not considering The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip II.3 Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0095]

[0096] Step S2052: Introduce a moment distribution coefficient to correct the first moment, and obtain the second moment at each connection end of elastic clip 1 and elastic clip 3 when considering the actual angular constraint capacity of the free end. Based on the second moment and the moments of inertia of the sections of elastic clip 1 and elastic clip 3 about their own centroidal principal axes, calculate the actual fatigue stress at each connection end of elastic clip 1 and elastic clip 3 when considering the actual angular constraint capacity of the free end. The moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity of the free end when the actual angular constraint capacity of the free end is not considered.

[0097] consider Integrated elastic support with measurable axial force for actual angular constraint capability at the point point, point, point, The second bending moment at the point , , , They are respectively:

[0098]

[0099]

[0100]

[0101] Based on the second bending moment, calculate the minimum and maximum fatigue stresses at key points on spring clip 1 and spring clip 3, respectively.

[0102] In one embodiment, the connecting end surfaces of spring strip 1 and spring strip 3 are taken as key points, namely... Figure 4 For points A, B, C, and D in the diagram, the method for calculating the maximum and minimum fatigue stress values ​​at these key points is as follows: generally ,consider The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip 1. Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0103]

[0104] In the formula, The maximum flexural section modulus, = , It is the minimum flexural section modulus. = .

[0105] consider The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip 1. Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0106]

[0107] In the formula, The maximum flexural section modulus, = , It is the minimum flexural section modulus. = .

[0108] consider The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip II.3 Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0109]

[0110] In the formula, The maximum flexural section modulus, = , It is the minimum flexural section modulus. = .

[0111] consider The axial force of the point-actual angular constraint capability can be measured by the integrated elastic support clip II.3 Minimum fatigue stress on the surface of the elastic clip at the point and maximum value for:

[0112]

[0113] In the formula, The maximum flexural section modulus, = , It is the minimum flexural section modulus. = .

[0114] The fatigue stress of the axial force measurable integrated spring support can provide a basis for its strength assessment, ensuring that the axial force measurable integrated spring support will not suffer fatigue failure under the action of rotor bearing radial load (rotor vibration load).

[0115] In the optimization of integrated elastic support structure parameters with measurable axial force, radial stiffness and fatigue stress can be used as optimization targets or constraints. Their analytical calculation formulas can provide a parameterized optimization model for structural parameter optimization, which can ensure the safe operation and long-term operation of the rotor support system.

[0116] The integrated elastic support radial performance calculation method provided in this embodiment has the following beneficial effects: 1) The moments of inertia about the centroidal principal axis of elastic clip 1 and elastic clip 2 3 are given for rectangular cross sections, trapezoidal cross sections and arc-shaped cross sections, respectively. This can more accurately reflect the actual bending resistance characteristics of the elastic clip and provide the prerequisite for more accurate calculation of the radial stiffness and fatigue stress of the integrated elastic support with measurable axial force (including the intersecting elastic clip 1 and elastic clip 2 and elastic ring 2).

[0117] 2) For the first time, analytical calculation formulas for the radial stiffness of the integrated elastic support with measurable axial force are given, both without considering the actual angular constraint capacity of the support bearing end and with considering the actual angular constraint capacity. Corresponding correction coefficients are also given. The radial stiffness of the integrated elastic support with measurable axial force can be quickly and accurately calculated using analytical calculation methods.

[0118] 3) For the first time, fatigue stress formulas are given for the integrated axial force measurable spring support without considering the actual angular constraint capacity of the spring support bearing end and with the actual angular constraint capacity. This allows for a faster and more accurate assessment of the fatigue strength of the spring bar at each critical location of the integrated axial force measurable spring support.

[0119] 4) The precise analytical calculation formulas for radial stiffness and fatigue stress of the integrated elastic support with measurable axial force, compared with the finite element method, can provide a fast and reliable means for the optimized design and stiffness and strength assessment of the integrated structure with measurable axial force while ensuring accuracy (the error between the analytical results and the finite element calculation results is less than 5%).

[0120] Existing methods can use the finite element method (FEM) to calculate radial stiffness and fatigue stress, and experimental methods to obtain these parameters. However, when using the FEM to calculate radial stiffness and fatigue stress, if the spring support parameters change, it is necessary to re-model (update) the FEM and perform response calculations, which is labor-intensive and computationally inefficient, especially for the optimized design of squirrel-cage spring supports. Experimental methods require the fabrication of an integrated spring support with measurable axial force, and are generally used for experimental verification after optimization design. If experimental methods are used directly in the optimization design stage, multiple sets of spring support prototypes need to be fabricated, and the optimal prototype parameters may not be obtained. Furthermore, this results in a significant waste of fabrication and experimental resources, and is extremely inefficient. The radial stiffness calculation results of the integrated spring support with measurable axial force of this invention have been verified by both FEM calculations and experimental results, and the fatigue stress results have also been verified by FEM results. The verification results show that the radial stiffness and fatigue stress calculation results of the integrated spring support with measurable axial force of this invention are accurate and reliable, with low computational load and high computational efficiency, making it suitable for the structural parameter optimization design and radial stiffness and strength assessment of integrated spring supports with measurable axial force.

[0121] This embodiment also provides an integrated elastic support radial performance calculation device, which is used to implement the above embodiments and preferred embodiments; details already described will not be repeated. As used below, the term "module" can refer to a combination of software and / or hardware that performs a predetermined function. Although the device described in the following embodiments is preferably implemented in software, hardware implementation, or a combination of software and hardware, is also possible and contemplated.

[0122] This embodiment provides an integrated elastic support radial performance calculation device, such as... Figure 11 As shown, it includes: The mechanical model construction module 1101 is used to simplify the axial force measurable integrated spring support into a three-segment mechanical model. The three-segment mechanical model includes spring bar 1, elastic ring 2 and spring bar 3 connected in sequence. The end of spring bar 1 away from elastic ring 2 is a fixed end, and the end of spring bar 3 away from elastic ring 2 is a free end, which is used to bear radial load. The moment of inertia calculation module 1102 is used to calculate the moments of inertia of the cross sections of spring clip 1, elastic ring 2 and spring clip 3 about their own centroidal principal axes, based on the cross-sectional geometry of spring clip 1, elastic ring 2 and spring clip 3 respectively. The deflection calculation module 1103 is used to calculate the total deflection of the free end under radial load based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, using the superposition method. Radial stiffness determination module 1104 is used to determine the radial stiffness of the axial force measurable integrated elastic support based on radial load and total deflection. The fatigue stress determination module 1105 is used to calculate the fatigue stress at each connection end of elastic clip 1 and elastic clip 2 under radial load based on the bending moment distribution of the three-segment mechanical model and combined with the moment of inertia of the cross sections of elastic clip 1 and elastic clip 2 about their own centroidal principal axis.

[0123] The integrated elastic support radial performance calculation device provided in this embodiment of the invention can execute the integrated elastic support radial performance calculation method provided in any embodiment of the invention, and has the corresponding functional modules and beneficial effects for executing the method. Further functional descriptions of the above modules and units are the same as in the corresponding embodiments described above, and will not be repeated here.

[0124] Figure 12 This is a schematic diagram of the structure of an electronic device provided in an embodiment of the present invention.

[0125] The following is a detailed reference. Figure 12 The diagram illustrates a structural schematic suitable for implementing an electronic device according to embodiments of the present invention. The electronic device may include a processor (e.g., a central processing unit, graphics processor, etc.) 1201, which can perform various appropriate actions and processes according to a program stored in read-only memory (ROM) 1202 or a program loaded from memory 1208 into random access memory (RAM) 1203. The RAM 1203 also stores various programs and data required for the operation of the electronic device. The processor 1201, ROM 1202, and RAM 1203 are interconnected via a bus 1204. An input / output (I / O) interface 1205 is also connected to the bus 1204.

[0126] Typically, the following devices can be connected to I / O interface 1205: input devices 1206 including, for example, touchscreens, touchpads, keyboards, mice, cameras, microphones, accelerometers, gyroscopes, etc.; output devices 1207 including, for example, liquid crystal displays (LCDs), speakers, vibrators, etc.; memory devices 1208 including, for example, magnetic tapes, hard disks, etc.; and communication devices 1209. Communication device 1209 allows electronic devices to communicate wirelessly or wiredly with other devices to exchange data. Although Figure 12 Electronic devices with various devices are shown, but it should be understood that it is not required to implement or have all of the devices shown, and more or fewer devices may be implemented or have instead.

[0127] In particular, according to embodiments of the present invention, the processes described above with reference to the flowcharts can be implemented as computer software programs. For example, embodiments of the present invention include a computer program product comprising a computer program carried on a non-transitory computer-readable medium, the computer program containing program code for performing the methods shown in the flowcharts. In such embodiments, the computer program can be downloaded and installed from a network via a communication device 1209, or installed from a memory 1208, or installed from a ROM 1202. When the computer program is executed by the processor 1201, it performs the functions defined in the integrated elastic support radial performance calculation method of the embodiments of the present invention.

[0128] Figure 12 The electronic device shown is merely an example and should not be construed as limiting the functionality and scope of the embodiments of the present invention.

[0129] This invention also provides a computer-readable storage medium. The methods described above according to embodiments of the invention can be implemented in hardware or firmware, or implemented as computer code that can be recorded on a storage medium, or implemented as computer code downloaded via a network and originally stored on a remote storage medium or a non-transitory machine-readable storage medium and then stored on a local storage medium. Thus, the methods described herein can be processed by software stored on a storage medium using a general-purpose computer, a dedicated processor, or programmable or dedicated hardware. The storage medium can be a magnetic disk, optical disk, read-only memory, random access memory, flash memory, hard disk, or solid-state drive, etc.; further, the storage medium can also include combinations of the above types of memory. It is understood that computers, processors, microprocessor controllers, or programmable hardware include storage components capable of storing or receiving software or computer code. When the software or computer code is accessed and executed by the computer, processor, or hardware, the integrated elastic support radial performance calculation method shown in the above embodiments is implemented.

[0130] A portion of this invention can be applied as a computer program product, such as computer program instructions, which, when executed by a computer, can invoke or provide the methods and / or technical solutions according to the invention through the operation of the computer. Those skilled in the art will understand that the forms in which computer program instructions exist in a computer-readable medium include, but are not limited to, source files, executable files, installation package files, etc. Correspondingly, the ways in which computer program instructions are executed by a computer include, but are not limited to: the computer directly executing the instructions, or the computer compiling the instructions and then executing the corresponding compiled program, or the computer reading and executing the instructions, or the computer reading and installing the instructions and then executing the corresponding installed program. Here, the computer-readable medium can be any available computer-readable storage medium or communication medium accessible to a computer.

[0131] Although embodiments of the invention have been described in conjunction with the accompanying drawings, those skilled in the art can make various modifications and variations without departing from the spirit and scope of the invention, and such modifications and variations all fall within the scope defined by the appended claims.

Claims

1. A method for calculating the radial performance of an integrated elastic support, characterized in that, The method includes: The axial force measurable integrated spring support is simplified into a three-segment mechanical model, which includes spring bar one, elastic ring and spring bar two connected in sequence. The end of spring bar one away from the elastic ring is a fixed end, and the end of spring bar two away from the elastic ring is a free end, which is used to bear radial load. Based on the cross-sectional geometry of the first elastic bar, the elastic ring, and the second elastic bar, calculate the moments of inertia of the cross-sections of the first elastic bar, the elastic ring, and the second elastic bar about their own centroidal principal axes, respectively. Based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis, the total deflection of the free end under the radial load is calculated using the superposition method. Based on the radial load and the total deflection, the radial stiffness of the axial force measurable integrated elastic support is determined; Based on the bending moment distribution of the three-segment mechanical model under the radial load, and combined with the moments of inertia of the cross sections of the first and second elastic clips about their own centroidal principal axes, the fatigue stress at each connection end of the first and second elastic clips is calculated.

2. The method for calculating the radial performance of an integrated elastic support according to claim 1, characterized in that, The step of calculating the moments of inertia of the cross-sections of the first elastic bar, the elastic ring, and the second elastic bar about their own centroidal principal axes, based on the cross-sectional geometry of the first elastic bar, the elastic ring, and the second elastic bar, respectively, includes: Based on the cross-sectional shape and geometric dimensions of the first and second elastic clips, calculate the moments of inertia of the cross-sections of the first and second elastic clips about their own centroidal principal axes, respectively. Based on the annular cross-section of the elastic ring and its inner and outer diameters, calculate the moment of inertia of the cross-section of the elastic ring about its own centroidal principal axis.

3. The method for calculating the radial performance of the integrated elastic support according to claim 1, characterized in that, Also includes: Based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis, the total rotation angle of the free end under the radial load is calculated using the superposition method. Based on the total rotation angle and the preset total rotation angle condition, the bending moment at the free end is determined without considering the actual angular constraint capacity of the free end.

4. The method for calculating the radial performance of the integrated elastic support according to claim 3, characterized in that, The step of calculating the total rotation angle of the free end under the radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis includes: Based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, the first rotation angle of the free end under radial load only and the second rotation angle under bending moment only are calculated respectively. The first and second rotation angles are superimposed to obtain the total rotation angle of the free end under the radial load.

5. The method for calculating the radial performance of the integrated elastic support according to claim 3, characterized in that, The step of calculating the total deflection of the free end under the radial load using the superposition method based on the three-segment mechanical model and the moments of inertia of each section about its own centroidal principal axis includes: Based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, the first deflection of the free end under radial load only and the second deflection under bending moment only are calculated respectively. The first deflection and the second deflection are superimposed to obtain the total deflection of the free end under the radial load.

6. The method for calculating the radial performance of an integrated elastic support according to claim 5, characterized in that, The step of determining the radial stiffness of the axially force-measurable integrated elastic support based on the radial load and the total deflection includes: Based on the ratio of the radial load to the total deflection, the basic radial stiffness of the axial force measurable integrated elastic support is determined without considering the actual angular constraint capacity of the free end. A moment distribution coefficient is introduced to correct the radial stiffness of the foundation, thereby obtaining the actual radial stiffness of the axial force measurable integrated elastic support when considering the actual angular constraint capacity of the free end. The moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity of the free end when the actual angular constraint capacity of the free end is not considered.

7. The method for calculating the radial performance of the integrated elastic support according to claim 3, characterized in that, The step of calculating the fatigue stress at each connection end of the elastic clips 1 and 2 based on the bending moment distribution under the radial load using the three-segment mechanical model and the moments of inertia of the cross sections of the elastic clips 1 and 2 about their own centroidal principal axes includes: Based on the bending moment distribution of the three-segment mechanical model under the radial load, the first bending moment at each connection end of the first and second elastic bars is determined without considering the actual angular constraint capacity of the free end. Based on the first bending moment and the moments of inertia of the cross sections of the first and second elastic bars about their own centroidal principal axes, the basic fatigue stress at each connection end of the first and second elastic bars is calculated without considering the actual angular constraint capacity of the free end. A moment distribution coefficient is introduced to correct the first moment, resulting in a second moment at each connection end of the first and second elastic bars when considering the actual angular constraint capacity of the free end. Based on the second moment and the moments of inertia of the sections of the first and second elastic bars about their own centroidal principal axes, the actual fatigue stress at each connection end of the first and second elastic bars when considering the actual angular constraint capacity of the free end is calculated. The moment distribution coefficient is determined based on the moment at the free end and the actual angular constraint capacity of the free end when the actual angular constraint capacity of the free end is not considered.

8. An integrated elastic support radial performance calculation device, characterized in that, The device includes: The mechanical model construction module is used to simplify the axial force measurable integrated spring support into a three-segment mechanical model. The three-segment mechanical model includes spring bar one, elastic ring and spring bar two connected in sequence. The end of spring bar one away from the elastic ring is a fixed end, and the end of spring bar two away from the elastic ring is a free end, which is used to bear radial load. The moment of inertia calculation module is used to calculate the moments of inertia of the cross sections of the first elastic bar, the elastic ring, and the second elastic bar about their own centroidal principal axes, based on the cross-sectional geometry of the first elastic bar, the elastic ring, and the second elastic bar, respectively. The deflection calculation module is used to calculate the total deflection of the free end under the radial load based on the three-segment mechanical model and the moment of inertia of each section about its own centroidal principal axis, using the superposition method. A radial stiffness determination module is used to determine the radial stiffness of the axial force measurable integrated elastic support based on the radial load and the total deflection. The fatigue stress determination module is used to calculate the fatigue stress at each connection end of the elastic clips one and two based on the bending moment distribution of the three-segment mechanical model under the radial load, combined with the moments of inertia of the cross sections of the elastic clips one and two about their own centroidal principal axes.

9. An electronic device, characterized in that, include: A memory and a processor are interconnected, the memory storing computer instructions, and the processor executing the computer instructions to perform the integrated elastic support radial performance calculation method according to any one of claims 1 to 7.

10. A computer-readable storage medium, characterized in that, The computer-readable storage medium stores computer instructions for causing a computer to execute the integrated elastic support radial performance calculation method according to any one of claims 1 to 7.

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