Main control type elastic bearing dry friction damper parameter selection method and related device

Abstract

The invention discloses a parameter selection method of a master control type elastic supporting dry friction damper and a related device. The parameter selection method comprises the following steps: establishing a one-dimensional simplified analysis model of the master control type elastic supporting dry friction damper; based on the one-dimensional simplified analysis model, analyzing an influence rule of the positive pressure N on the amplitude of the damper; based on the one-dimensional simplified analysis model, analyzing an influence rule of the friction coefficient mu on the amplitude of the damper; based on the one-dimensional simplified analysis model, analyzing an influence rule of the friction force mu * N on the amplitude of the damper; based on the one-dimensional simplified analysis model, analyzing an influence rule of the excitation frequency f on the amplitude of the damper; in combination with the critical rotating speed requirement of a rotor system, the parameter selection criterion of the master control type elastic bearing dry friction damper is determined, and the method and the related device can achieve parameter selection of the master control type elastic bearing dry friction damper by considering parameter coupling and working condition adaptation.

Description

Technical Field

[0001] This invention belongs to the field of vibration reduction technology for aero-engine rotor systems, and relates to a method for selecting parameters of a master-controlled elastic support dry friction damper and related devices. Background Technology

[0002] To achieve a high thrust-to-weight ratio, modern high-performance aero engines typically employ flexible rotor systems with operating speeds far exceeding the first-order critical speed. During start-up and shutdown, the rotor must repeatedly traverse the critical speed region, easily triggering resonance and generating significant vibrations. This leads to increased component stress, shortened lifespan, and even system instability. The master-controlled elastic support dry friction damper, with its advantages of "real-time adjustment of friction pair contact pressure and dynamic change of system equivalent damping," has become the core device for suppressing rotor resonance. The rationality of its parameters directly determines the vibration reduction effect.

[0003] Existing parameter selection schemes rely too heavily on empirical design, lack quantitative relationships, and rarely consider the synergistic effects of parameter coupling. Therefore, there is an urgent need for a parameter selection scheme for master-controlled elastic support dry friction dampers that is based on theoretical models and takes into account both parameter coupling and working condition adaptation, in order to solve the above-mentioned technical pain points. Summary of the Invention

[0004] The purpose of this invention is to overcome the shortcomings of the prior art and provide a method and related device for selecting parameters of a master-controlled elastic support dry friction damper. This method and related device can achieve parameter selection of a master-controlled elastic support dry friction damper by taking into account both parameter coupling and working condition adaptation.

[0005] To achieve the above objectives, this invention discloses a method for selecting parameters of a master-controlled elastic support dry friction damper, comprising: A simplified one-dimensional analytical model of a master-controlled elastic support dry friction damper is established. Based on the one-dimensional simplified analysis model, the influence of normal force N on damper amplitude is analyzed; the influence of friction coefficient μ on damper amplitude is analyzed; the influence of friction force μ×N on damper amplitude is analyzed; and the influence of excitation frequency f on damper amplitude is analyzed. Based on the critical speed requirements of the rotor system, the parameter selection criteria for the master-controlled elastic support dry friction damper are determined.

[0006] Furthermore, the one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper is a one-dimensional two-degree-of-freedom spring-mass model.

[0007] Furthermore, the one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper includes a dynamic mass block, an equivalent mass point of the static friction plate, and the equivalent stiffness and damping of the elastic support.

[0008] Furthermore, the motion differential equation of the one-dimensional simplified analytical model of the master-controlled elastic support dry friction damper is as follows:

[0009] Where x1 is the displacement of m1, x2 is the displacement of m2, sgn() is the sign function, k1 is the bending stiffness of the squirrel cage elastic support, k2 is the shear contact stiffness of the interface between the dynamic and static friction plates, c1 is the structural damping coefficient of the squirrel cage elastic support, c2 is the structural damping coefficient of the contact interface, and f c F is the Coulomb friction force between the dynamic and static friction pairs, μ is the coefficient of friction, N is the normal force applied by the counterweight, and F is the normal force. x Fx is the simple harmonic excitation force acting on m1, where F0 is the amplitude of the excitation force, Ω = 2πf is the excitation angular frequency, and f is the excitation frequency.

[0010] Furthermore, in the process of analyzing the influence of friction on the damper amplitude, the excitation parameters μ×N=3N, 4.5N, and 9N were set, and different values ​​of N and μ were taken. F0=5N and f=130-140Hz. The frequency sweep curves of the spring support amplitude were calculated for the three cases.

[0011] Furthermore, in the process of analyzing the influence of the excitation frequency f on the damper amplitude, the frictional force increases, F0=5N, f=130-140Hz, and the sweep frequency amplitude is calculated when the frictional force is greater than the excitation force amplitude of 5N, equal to the excitation force amplitude of 5N, and less than the excitation force amplitude of 5N.

[0012] Furthermore, the specific steps for determining the parameter selection criteria for the master-controlled elastic support dry friction damper are as follows: draw a three-dimensional polygonal graph based on the relationship between amplitude, excitation frequency and friction force.

[0013] This invention discloses a parameter selection system for a master-controlled elastic support dry friction damper, comprising: A module is established to create a simplified one-dimensional analytical model of a master-controlled elastic support dry friction damper. The first analysis module is used to analyze the influence of the normal force N on the damper amplitude based on the one-dimensional simplified analysis model; the second analysis module is used to analyze the influence of the friction coefficient μ on the damper amplitude based on the one-dimensional simplified analysis model; the third analysis module is used to analyze the influence of the friction force μ×N on the damper amplitude based on the one-dimensional simplified analysis model; and the fourth analysis module is used to analyze the influence of the excitation frequency f on the damper amplitude based on the one-dimensional simplified analysis model. The determination module is used to determine the parameter selection criteria for the master-controlled elastic support dry friction damper based on the critical speed requirements of the rotor system.

[0014] This invention discloses a computer device, including a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, it implements the steps of the parameter selection method for the master-controlled elastic support dry friction damper.

[0015] This invention discloses a computer-readable storage medium storing a computer program, which, when executed by a processor, implements the steps of the parameter selection method for the master-controlled elastic support dry friction damper.

[0016] The present invention has the following beneficial effects: The parameter selection method and related device for the master-controlled elastic support dry friction damper described in this invention establishes a one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper during specific operation. Based on this one-dimensional simplified analysis model, the parameters of the master-controlled elastic support dry friction damper are selected, clarifying the quantitative relationship between normal pressure, friction coefficient, excitation frequency, and amplitude. Combined with the characteristics of the rotor's critical speed, a parameter combination with "excellent vibration reduction effect, low wear risk, and strong adaptability to operating conditions" is output, providing precise guidance for damper design. It is applicable to the vibration reduction design of flexible rotor systems in high-speed rotating machinery such as aero-engines and gas turbines, especially for the optimized selection of normal pressure, friction coefficient, and structural parameters of the master-controlled elastic support dry friction damper, ensuring that the vibration amplitude is minimized when the rotor passes through the critical speed. Attached Figure Description

[0017] To more clearly illustrate the technical solutions of the embodiments of this application, the drawings used in the description of the embodiments of this application will be briefly introduced below. Obviously, the drawings described below are only some embodiments of this application. For those skilled in the art, other drawings can be obtained based on these drawings without creative effort.

[0018] Figure 1 This is a flowchart of the method of the present invention; Figure 2To simplify the schematic diagram of a one-dimensional, two-degree-of-freedom spring-mass system, m1 represents the mass of the elastic support and the dynamic friction plate excluding the contact interface; m2 is the mass of the contact interface of the dynamic friction plate; k1 and c1 are the bending stiffness and structural damping coefficient of the squirrel cage, respectively; k2 is the shear contact stiffness of the contact interface of the dynamic friction plate; and c2 is the structural damping between the dynamic friction plate and its contact interface. The magnitude of the frictional force is f. c ; Figure 3 A comparison chart of calculated and experimental results of displacement response per unit excitation force under no-load conditions; Figure 4 The amplitude curves of the elastic support under different frictional forces are shown. Figure 5 This is a three-dimensional curve showing the relationship between vibration amplitude, friction force, and excitation frequency. Detailed Implementation

[0019] 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, not all, of the embodiments of the present invention. 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.

[0020] In the description of this invention, it should be understood that the terms "comprising" and "including" indicate the presence of the described features, integrals, steps, operations, elements and / or components, but do not exclude the presence or addition of one or more other features, integrals, steps, operations, elements, components and / or collections thereof.

[0021] It should also be understood that the terminology used in this specification is for the purpose of describing particular embodiments only and is not intended to limit the invention. As used in this specification and the appended claims, the singular forms “a,” “an,” and “the” are intended to include the plural forms unless the context clearly indicates otherwise.

[0022] It should also be further understood that the term "and / or" as used in this specification and the appended claims refers to any combination and all possible combinations of one or more of the associated listed items, and includes such combinations. For example, A and / or B can represent three cases: A alone, A and B simultaneously, and B alone. Additionally, the character " / " in this invention generally indicates that the preceding and following objects have an "or" relationship.

[0023] It should be understood that although terms such as first, second, third, etc., may be used in the embodiments of the present invention to describe the preset range, these preset ranges should not be limited to these terms. These terms are only used to distinguish the preset ranges from one another. For example, without departing from the scope of the embodiments of the present invention, the first preset range may also be referred to as the second preset range, and similarly, the second preset range may also be referred to as the first preset range.

[0024] Depending on the context, the word "if" as used here can be interpreted as "when," "when," "in response to determination," or "in response to detection." Similarly, depending on the context, the phrase "if determination" or "if detection (of the stated condition or event)" can be interpreted as "when determination," "in response to determination," "when detection (of the stated condition or event)," or "in response to detection (of the stated condition or event)."

[0025] 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, not all, of the embodiments of the present invention. The components of the embodiments of the present invention described and shown in the accompanying drawings can generally be arranged and designed in various different configurations. Therefore, the following detailed description of the embodiments of the present invention provided in the accompanying drawings is not intended to limit the scope of the claimed invention, but merely to illustrate selected embodiments of the invention. All other embodiments obtained by those skilled in the art based on the embodiments of the present invention without inventive effort are within the scope of protection of the present invention.

[0026] The accompanying drawings illustrate various structural schematic diagrams according to embodiments disclosed in this invention. These drawings are not to scale, and some details have been enlarged for clarity, and some details may have been omitted. The shapes of the various regions and layers shown in the drawings, as well as their relative sizes and positional relationships, are merely exemplary and may deviate from reality due to manufacturing tolerances or technical limitations. Furthermore, those skilled in the art can design regions / layers with different shapes, sizes, and relative positions as needed.

[0027] Example 1 refer to Figure 1 The parameter selection method for the master-controlled elastic support dry friction damper of the present invention includes the following steps: 1) Establish a one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper. The one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper is a one-dimensional two-degree-of-freedom spring-mass model, including a dynamic mass block, a static friction plate equivalent mass, and the equivalent stiffness and damping of the elastic support. The accuracy of the one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper is verified by impact test; 2) Based on the one-dimensional simplified analysis model, analyze the influence of normal force N on the damper amplitude; 3) Based on the one-dimensional simplified analysis model, analyze the influence of friction coefficient μ on the damper amplitude; 4) Based on the one-dimensional simplified analysis model, analyze the influence of friction force μ×N on the damper amplitude; 5) Based on the one-dimensional simplified analysis model, analyze the influence of excitation frequency f on the damper amplitude. 6) Determine the parameter selection criteria for the master-controlled elastic support dry friction damper based on the critical speed requirements of the rotor system.

[0028] The specific operation of step 1) is as follows: 11) Model construction: Considering the structural characteristics of the master-controlled elastic support dry friction damper, and referring to the ball / chassis dry friction model, it is simplified into a one-dimensional two-degree-of-freedom spring-mass system, such as... Figure 2 As shown. The model contains two core mass points: m1 is the total mass of the squirrel cage elastic support and the dynamic friction plate, which is regarded as a dynamic mass block; m2 is the equivalent mass point of the static friction plate.

[0029] 12) Define model parameters; Stiffness parameters: k1 is the bending stiffness of the squirrel cage elastic support, used to simulate the deformation characteristics of the elastic support; k2 is the shear contact stiffness of the contact interface between the dynamic friction plate and the static friction plate, used to simulate the elastic deformation of the contact surface. Damping parameters: c1 is the structural damping coefficient of the squirrel cage elastic support, and c2 is the structural damping coefficient of the contact interface; Friction parameter: f c Let f be the Coulomb friction force between the dynamic and static friction pairs, satisfying f c =μN, where μ is the coefficient of friction and N is the normal force applied by the counterweight; Excitation parameters: F x Fx is the simple harmonic excitation force acting on m1, where F0 is the amplitude of the excitation force, Ω = 2πf is the excitation angular frequency, and f is the excitation frequency.

[0030] 13) Establish the differential equations of motion; Based on Newton's second law, force analysis is performed on m1 and m2, and the differential equation of motion of the system is established as follows:

[0031] The contact interface and the static friction plate can be represented by a one-dimensional Coulomb model as follows:

[0032] The system of equations can be rewritten as follows:

[0033] Where x1 is the displacement of m1, x2 is the displacement of m2, and sgn() is the sign function used to characterize the direction of friction.

[0034] Specifically, in step 11), the simplified model assumes m2=0 because the contact area is small. At this time, the size of m1 is the sum of the mass of the squirrel cage and the moving friction plate. The specific operation of step 2) is as follows: 21) A rat cage with bar length L=65mm, width b=4mm, and thickness h=4mm is selected for calculation. Its total mass m1=4.08kg, first natural frequency 135Hz, and modal damping ratio ζ=0.1%; 22) Through simulation calculations and comparative verification with impact tests, a frequency sweep test was conducted under no-load conditions with an excitation force F0 = 5N and f = 130-140Hz. The frequency response curves calculated by the simplified model and the experimental frequency response curves were compared, and the results are as follows: Figure 3 As shown.

[0035] 23) Set the excitation parameter F0=5N, μ as a fixed value, increase it from 0.3 to 0.5, f=130-140Hz, and normal force N=3-30N to gradually increase for simulation calculation.

[0036] Specifically, in step 23), the simulation takes k1 = 2.95 × 10 6 N·m -1 c1 = 6.9 N·s·m -1 k2 = 1.8 × 10 9 N·m -1 c2 = 6.9 N·s·m -1 The calculation time step was set to 1×10. -4 s, 1×10 -5 s, 1×10 -6 The simplified model's transient response within 8 seconds is calculated, and the time-domain result after 4 seconds is Fourier transformed to obtain the frequency-domain response. The results are compared to select the subsequent calculation time step.

[0037] In step 3), during the analysis of the influence of the friction coefficient μ on the damper amplitude, the excitation parameter F0 = 5N, N is a fixed value, f = 130-140Hz, and the friction coefficient μ gradually increases. Simulation calculations are performed in the range of N = 3-30N.

[0038] In step 4), during the analysis of the influence of friction on the damper amplitude, the excitation parameters μ×N=3N, 4.5N, and 9N are set. That is, when the friction is the same, different N and μ are taken, F0=5N, f=130-140Hz, and the frequency sweep curve of the spring support amplitude is calculated in the three cases.

[0039] In step 5), during the analysis of the influence of the excitation frequency f on the damper amplitude, the frictional force increases, F0 = 5N, f = 130-140Hz. The sweep frequency amplitude is calculated for the following conditions: frictional force greater than the excitation force amplitude of 5N, equal to the excitation force amplitude of 5N, and less than the excitation force amplitude of 5N. Figure 4 As shown.

[0040] In step 5), the specific operation for determining the parameter selection criteria of the master-controlled elastic support dry friction damper is as follows: Plot a three-dimensional line graph showing the relationship between amplitude, excitation frequency, and friction force. The results are as follows: Figure 5 As shown, with increasing friction, the vibration amplitude first decreases and then remains constant. When the friction is less than the excitation force amplitude of 5N, the closer the excitation frequency is to the first natural frequency of the elastic support B, the larger the vibration amplitude. When the friction is greater than the excitation force amplitude of 5N, the vibration amplitude increases slightly with increasing excitation frequency, but generally remains around 10. -9 On the order of m.

[0041] This invention has the following characteristics: Sufficient theoretical support: A simplified analytical model is established to quantify the relationship between parameters and amplitude, improving the accuracy of parameter selection and avoiding blind trial and error; Parameter synergistic optimization: By balancing the normal force and the coefficient of friction based on the wear relationship between friction and excitation force, the vibration reduction effect is ensured while reducing the risk of wear. Strong adaptability to operating conditions: Parameters are selected based on the rotor's critical speed characteristics to avoid the damper's natural frequency overlapping with the rotor speed, thus amplifying vibrations; High engineering applicability: It outputs clear parameter ranges and combination schemes, which can directly guide the design of damper parameters.

[0042] Example 2 The master-controlled elastic support dry friction damper parameter selection system of the present invention includes: A module is established to create a simplified one-dimensional analytical model of a master-controlled elastic support dry friction damper. The first analysis module is used to analyze the influence of the normal force N on the damper amplitude based on the one-dimensional simplified analysis model; the second analysis module is used to analyze the influence of the friction coefficient μ on the damper amplitude based on the one-dimensional simplified analysis model; the third analysis module is used to analyze the influence of the friction force μ×N on the damper amplitude based on the one-dimensional simplified analysis model; and the fourth analysis module is used to analyze the influence of the excitation frequency f on the damper amplitude based on the one-dimensional simplified analysis model. The determination module is used to determine the parameter selection criteria for the master-controlled elastic support dry friction damper based on the critical speed requirements of the rotor system.

[0043] The module division in this embodiment is illustrative and represents only one logical functional division. In actual implementation, other division methods may be used. Furthermore, the functional modules in each embodiment of this application can be integrated into a single processor, exist as separate physical entities, or be integrated into a single module. The integrated modules described above can be implemented in hardware or as software functional modules.

[0044] Example 3 A computer device includes a memory, a processor, and a computer program stored in the memory and executable on the processor. When the processor executes the computer program, it implements the steps of a method for selecting parameters of a master-controlled elastic support dry friction damper. For example, the method includes: establishing a one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper; analyzing the influence of the normal force N on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of the friction coefficient μ on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of the friction force μ×N on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of the excitation frequency f on the damper amplitude based on the one-dimensional simplified analysis model; and determining the parameter selection criteria for the master-controlled elastic support dry friction damper in conjunction with the critical speed requirements of the rotor system. The memory may include main memory, such as high-speed random access memory (RAM), or non-volatile memory, such as at least one disk storage device. The processor, network interface, and memory are interconnected via an internal bus, which may be an industry-standard architecture bus, a peripheral component interconnection standard bus, or an extended industry-standard architecture bus. The bus can be categorized as an address bus, data bus, or control bus. The memory stores programs; specifically, the program may include program code, which includes computer operation instructions. The memory may include main memory and non-volatile memory, and provides instructions and data to the processor.

[0045] Example 4 A computer-readable storage medium stores a computer program that, when executed by a processor, implements the steps of a method for selecting parameters of a master-controlled elastic support dry friction damper. For example, the method includes: establishing a one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper; analyzing the influence of normal force N on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of friction coefficient μ on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of friction force μ×N on the damper amplitude based on the one-dimensional simplified analysis model; analyzing the influence of excitation frequency f on the damper amplitude based on the one-dimensional simplified analysis model; and determining the parameter selection criteria for the master-controlled elastic support dry friction damper in conjunction with the critical speed requirements of the rotor system. Specifically, the computer-readable storage medium includes, but is not limited to, volatile memory and / or non-volatile memory. The volatile memory may include random access memory (RAM) and / or cache memory, etc. The non-volatile memory may include read-only memory (ROM), hard disk, flash memory, optical disk, magnetic disk, etc.

[0046] Those skilled in the art will understand that embodiments of this application can be provided as methods, systems, or computer program products. Therefore, this application can take the form of a completely hardware embodiment, a completely software embodiment, or an embodiment combining software and hardware aspects. Furthermore, this application can take the form of a computer program product embodied on one or more computer-usable storage media (including but not limited to disk storage, CD-ROM, optical storage, etc.) containing computer-usable program code.

[0047] This application is described with reference to flowchart illustrations and / or block diagrams of methods, apparatus (systems), and computer program products according to embodiments of this application. It will be understood that each block of the flowchart illustrations and / or block diagrams, and combinations of blocks in the flowchart illustrations and / or block diagrams, can be implemented by computer program instructions. These computer program instructions can be provided to a processor of a general-purpose computer, special-purpose computer, embedded processor, or other programmable data processing apparatus to produce a machine, such that the instructions, which execute via the processor of the computer or other programmable data processing apparatus, generate instructions for implementing the flowchart... Figure 1 One or more processes and / or boxes Figure 1 A device that provides the functions specified in one or more boxes.

[0048] These computer program instructions may also be stored in a computer-readable storage medium that can direct a computer or other programmable data processing device to function in a particular manner, such that the instructions stored in the computer-readable storage medium produce an article of manufacture including instruction means, which are implemented in a process Figure 1One or more processes and / or boxes Figure 1 The function specified in one or more boxes.

[0049] These computer program instructions may also be loaded onto a computer or other programmable data processing equipment to cause a series of operational steps to be performed on the computer or other programmable equipment to produce a computer-implemented process, thereby providing instructions that execute on the computer or other programmable equipment for implementing the process. Figure 1 One or more processes and / or boxes Figure 1 The steps of the function specified in one or more boxes.

[0050] Other embodiments of the invention will readily occur to those skilled in the art upon consideration of the specification and disclosure of the invention. This application is intended to cover any variations, uses, or adaptations of the invention that follow the general principles of the invention and include common knowledge or customary techniques in the art not disclosed herein. The specification and examples are to be considered exemplary only, and the true scope and spirit of the invention are indicated by the following claims.

[0051] It should be understood that the present invention is not limited to the precise structure described above and shown in the accompanying drawings, and various modifications and changes can be made without departing from its scope. The scope of the invention is limited only by the appended claims.

[0052] The above description is merely a preferred embodiment of the present invention and does not constitute any limitation on the present invention. Any simple modifications, alterations, or equivalent structural changes made to the above embodiments based on the technical essence of the present invention shall still fall within the protection scope of the present invention.

Claims

1. A method for selecting parameters of a master-controlled elastic support dry friction damper, characterized in that, include: A simplified one-dimensional analytical model of a master-controlled elastic support dry friction damper is established. Based on the one-dimensional simplified analysis model, the influence of normal force N on the damper amplitude is analyzed. Based on the one-dimensional simplified analysis model, the influence of the friction coefficient μ on the damper amplitude is analyzed. Based on the one-dimensional simplified analysis model, the influence of frictional force μ×N on the damper amplitude is analyzed. Based on the one-dimensional simplified analysis model, the influence of the excitation frequency f on the damper amplitude is analyzed. Based on the critical speed requirements of the rotor system, the parameter selection criteria for the master-controlled elastic support dry friction damper are determined.

2. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 1, characterized in that, The simplified one-dimensional analysis model of the master-controlled elastic support dry friction damper is a one-dimensional two-degree-of-freedom spring-mass model.

3. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 1, characterized in that, The one-dimensional simplified analysis model of the master-controlled elastic support dry friction damper includes a dynamic mass block, an equivalent mass point of the static friction plate, and the equivalent stiffness and damping of the elastic support.

4. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 1, characterized in that, The motion differential equation of the simplified one-dimensional analytical model of the master-controlled elastic support dry friction damper is: Where x1 is the displacement of m1, x2 is the displacement of m2, sgn() is the sign function, k1 is the bending stiffness of the squirrel cage elastic support, k2 is the shear contact stiffness of the interface between the dynamic and static friction plates, c1 is the structural damping coefficient of the squirrel cage elastic support, c2 is the structural damping coefficient of the contact interface, and f c F is the Coulomb friction force between the dynamic and static friction pairs, μ is the coefficient of friction, N is the normal force applied by the counterweight, and F is the normal force. x Fx is the simple harmonic excitation force acting on m1, where F0 is the amplitude of the excitation force, Ω = 2πf is the excitation angular frequency, and f is the excitation frequency.

5. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 4, characterized in that, In analyzing the influence of friction on the damper amplitude, excitation parameters μ×N=3N, 4.5N, and 9N were set, and different values ​​of N and μ were taken. F0=5N and f=130-140Hz. The frequency sweep curves of the spring support amplitude were calculated for the three cases.

6. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 4, characterized in that, In the process of analyzing the influence of excitation frequency f on damper amplitude, the frictional force increases, F0=5N, f=130-140Hz. The sweep frequency amplitude is calculated when the frictional force is greater than the excitation force amplitude of 5N, equal to the excitation force amplitude of 5N, and less than the excitation force amplitude of 5N.

7. The parameter selection method for the master-controlled elastic support dry friction damper according to claim 4, characterized in that, The specific steps for determining the parameter selection criteria for a master-controlled elastic support dry friction damper are as follows: draw a three-dimensional polygonal graph based on the relationship between amplitude, excitation frequency, and friction force.

8. A parameter selection system for a master-controlled elastic support dry friction damper, characterized in that, include: A module is established to create a simplified one-dimensional analytical model of a master-controlled elastic support dry friction damper. The first analysis module is used to analyze the influence of the normal force N on the damper amplitude based on the one-dimensional simplified analysis model. The second analysis module is used to analyze the influence of the friction coefficient μ on the damper amplitude based on the one-dimensional simplified analysis model. The third analysis module is used to analyze the influence of frictional force μ×N on the damper amplitude based on the one-dimensional simplified analysis model; the fourth analysis module is used to analyze the influence of excitation frequency f on the damper amplitude based on the one-dimensional simplified analysis model. The determination module is used to determine the parameter selection criteria for the master-controlled elastic support dry friction damper based on the critical speed requirements of the rotor system.

9. A computer device comprising a memory, a processor, and a computer program stored in the memory and executable on the processor, characterized in that, When the processor executes the computer program, it implements the steps of the parameter selection method for the master-controlled elastic support dry friction damper as described in any one of claims 1-7.

10. A computer-readable storage medium storing a computer program, characterized in that, When the computer program is executed by the processor, it implements the steps of the parameter selection method for the master-controlled elastic support dry friction damper as described in any one of claims 1-7.

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