Damping design method and system for damping ring of labyrinth sealing structure

Abstract

The invention discloses a labyrinth seal structure damping ring vibration attenuation design method and system, and the method comprises the steps: determining the vibration stress range and allowable vibration stress of a labyrinth seal structure according to an existing labyrinth seal structure material; the method comprises the following steps: selecting basic parameters of a damping ring according to an existing labyrinth sealing structure; according to the vibration stress range and the basic parameters, determining modal displacement of a damping ring mounting position, dangerous point vibration stress and vibration kinetic energy, and calculating friction energy consumption of the damping ring under different vibration stress and a damping ratio capable of being provided to obtain a damping characteristic curve of the damping ring; determining a critical vibration stress, a peak damping ratio and a corresponding vibration stress according to the damping characteristic curve; and according to the critical vibration stress, the peak damping ratio and the corresponding vibration stress, the damping ring parameters meeting the requirements of the labyrinth sealing structure are determined by combining the allowable vibration stress and the damping vibration attenuation characteristics under different damping ring parameters. According to the method, the damping ring vibration reduction design time can be effectively shortened.

Description

Technical Field

[0001] The invention belongs to the technical field of aero-engine vibration reduction structure design, and in particular relates to a vibration reduction design method and system for a damping ring of a comb tooth sealing structure. Background Art

[0002] The comb seal structure is a key component in aircraft engines. It works in extreme environments of high temperature, high pressure and high speed, and is subjected to high static stress and alternating stress for a long time. It is easy to fail due to high cycle fatigue due to vibration problems. Therefore, vibration reduction design must be carried out to avoid failure caused by resonance and instability. Due to the harsh working environment, the application of damping technologies such as rubber is limited. Dry friction dampers are widely used in vibration reduction design of aircraft engines because of their insensitivity to temperature changes, simple structure and obvious vibration reduction effect.

[0003] In the comb seal structure of aircraft engines, the damping ring is a dry friction damper and is often interference-fitted into the mounting groove. When rotating at high speed, the damping ring is close to the ring groove. When vibration occurs, relative movement may occur between the damping ring and the ring groove, generating friction, thereby dissipating vibration energy, increasing system damping, and reducing structural vibration stress. In order to meet the vibration reduction requirements of different comb seal structures, it is necessary to comprehensively consider factors such as working state, speed, vibration form and damping ring form, and design the shape and quality parameters of the damping ring to meet the vibration reduction requirements within a certain working speed range.

[0004] The existing vibration reduction design and analysis methods for the damping ring of the comb-teeth sealing structure usually adopt the technology of numerical solution of nonlinear steady-state response, solve it through forward modeling, take the aerodynamic excitation force as input, solve the system vibration equation, calculate the displacement response, and optimize the damping ring parameters to minimize the displacement response to perform vibration reduction analysis. However, these methods have obvious shortcomings, including that the aerodynamic excitation force is difficult to accurately obtain and changes with the working conditions, resulting in reliance on the assumption of simplified excitation force to solve the response, which is not accurate; it is necessary to traverse the amplitude of the excitation force, which consumes a lot of computing power and has the problem of solution convergence; in addition, the existing methods mainly focus on vibration displacement, while in fact the high cycle fatigue of the comb-teeth sealing structure pays more attention to stress, and the minimum displacement response does not necessarily lead to stress reduction, which leads to a gap between theory and engineering practice, so it is necessary to develop an analysis method characterized by vibration stress. Summary of the invention

[0005] In order to solve the above technical problems, the present invention proposes a vibration reduction design method and system for a damping ring of a comb tooth sealing structure to solve the above problems existing in the prior art.

[0006] To achieve the above objectives, in a first aspect, the present invention provides a vibration reduction design method for a damping ring of a comb tooth sealing structure, comprising:

[0007] Determine the vibration stress range and allowable vibration stress of the comb tooth sealing structure according to the existing comb tooth sealing structure materials;

[0008] According to the existing comb teeth sealing structure, the basic parameters of the damping ring are selected, wherein the basic parameters include: material, installation position, shape, and size;

[0009] Determine the modal displacement, the vibration stress at the dangerous point and the modal vibration kinetic energy of the comb tooth sealing structure at the damping ring installation position according to the vibration stress range and the basic parameters;

[0010] According to the modal displacement, the vibration stress of the dangerous point and the modal vibration kinetic energy, the friction energy consumption of the damping ring under different vibration stresses and the damping ratio that can be provided are calculated to obtain the damping characteristic curve of the damping ring;

[0011] According to the damping characteristic curve, determining the critical vibration stress, the peak damping ratio and the corresponding vibration stress;

[0012] According to the critical vibration stress, peak damping ratio and corresponding vibration stress, combined with the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters, the damping ring parameters that meet the requirements of the comb tooth sealing structure are determined.

[0013] Preferably, determining the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the vibration kinetic energy according to the vibration stress range and the basic parameters includes:

[0014] According to the basic parameters and the vibration stress range, the modes of the comb tooth sealing structure at different rotation speeds are calculated by the finite element method, and a Campbell diagram is drawn to find out the modes with resonance risks, and determine the dangerous vibration modes and dangerous rotation speeds that need to be paid attention to;

[0015] According to the dangerous rotation speed, a prestressed modal analysis of the grate tooth sealing structure is performed by using the finite element method;

[0016] According to the prestressed modal analysis, the modal displacement at the monitoring point of the comb tooth sealing structure under the dangerous vibration mode, the vibration stress at the dangerous point and the vibration kinetic energy are obtained.

[0017] Preferably, according to the modal displacement, the vibration stress at the dangerous point and the modal vibration kinetic energy, the friction energy consumption of the damping ring under different vibration stresses and the damping ratio that can be provided are calculated, and the damping characteristic curve of the damping ring is obtained, including:

[0018] According to the modal displacement, vibration stress at the dangerous point and modal vibration kinetic energy, the vibration displacement and structural vibration kinetic energy under the current vibration stress are obtained through the proportional conversion relationship between the vibration parameters and the modal parameters under the small deformation condition;

[0019] According to the selected rotation speed and mode, the contact normal pressure per unit length of the contact surface between the damping ring and the comb teeth sealing structure is obtained;

[0020] According to the vibration displacement, structural vibration kinetic energy and contact normal pressure under the current vibration stress, the critical angle of the slip and sticking area on the contact surface between the comb tooth sealing structure and the damping ring is calculated;

[0021] According to the critical angle, the friction energy consumption of the contact surface within one vibration cycle is calculated;

[0022] Calculating the equivalent damping ratio provided by the damping ring under the current vibration stress according to the friction energy consumption and the structural vibration kinetic energy;

[0023] By changing the input vibration stress σ, the equivalent damping ratio of the damping ring under a series of vibration stresses is obtained, and the damping characteristic curve of the damping ring is formed.

[0024] Preferably, the calculation formula of the critical angle between the slip and sticky regions is:

[0025]

[0026] Contact surface friction energy E f The calculation formula is:

[0027]

[0028] The calculation formula of the equivalent damping ratio ζ is:

[0029]

[0030] Among them, θ0 is the critical angle, N is the vibration node diameter of the grate seal structure, P is the contact positive pressure per unit length of the contact surface, B is the vibration displacement of the dangerous point under the current vibration stress σ, R f is the radius of the contact surface, E is the Young's elastic modulus of the damping ring material, C s With R s are the radial semi-thickness of the comb seal structure and the radius of the neutral layer, C d With R d are the radial semi-thickness of the damping ring and the radius of the neutral layer, E k is the vibration kinetic energy.

[0031] Preferably, determining the damping ring parameters that meet the requirements of the comb teeth sealing structure includes:

[0032] Obtain the allowable vibration stress of the comb tooth sealing structure;

[0033] comparing the vibration stress corresponding to the peak damping ratio with the allowable vibration stress;

[0034] If the vibration stress corresponding to the peak damping ratio is significantly different from the allowable vibration stress, different damping ring design parameters are selected and the calculation is repeated;

[0035] If the vibration stress corresponding to the peak damping ratio is close to the allowable vibration stress, the optimal damping ring design parameters are obtained.

[0036] In a second aspect, the present invention discloses a vibration reduction design system for a comb tooth sealing structure damping ring, comprising:

[0037] A first determination module is used to determine the vibration stress range and allowable vibration stress of the comb tooth sealing structure according to the existing comb tooth sealing structure material;

[0038] A selection module is used to select basic parameters of the damping ring according to the existing comb tooth sealing structure, wherein the basic parameters include: material, installation position, shape, and size;

[0039] A second determination module is used to determine the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the modal vibration kinetic energy according to the vibration stress range and the basic parameters;

[0040] A first calculation module is used to calculate the friction energy consumption of the damping ring and the damping ratio that can be provided under different vibration stresses according to the modal displacement, the vibration stress of the dangerous point and the modal vibration kinetic energy, so as to obtain the damping characteristic curve of the damping ring;

[0041] A third determination module is used to determine the critical vibration stress, the peak damping ratio and the corresponding vibration stress according to the damping characteristic curve;

[0042] The second calculation module is used to determine the damping ring parameters that meet the requirements of the comb tooth sealing structure according to the critical vibration stress, peak damping ratio and its corresponding vibration stress, combined with the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters.

[0043] In a third aspect, the present invention further discloses a computer device, comprising a memory, a processor, and a computer program stored in the memory, wherein the processor executes the computer program to implement the steps of the method described in the first aspect.

[0044] In a fourth aspect, the present invention further discloses a computer-readable storage medium having a computer program stored thereon, which implements the steps of the method described in the first aspect when executed by a processor.

[0045] In a fifth aspect, the present invention further discloses a computer program product, including a computer program, which implements the steps of the method described in the first aspect when executed by a processor.

[0046] Compared with the prior art, the present invention has the following advantages and technical effects:

[0047] The present invention provides a vibration reduction design method for a damping ring of a comb tooth sealing structure, comprising: 1) determining the vibration stress range and allowable vibration stress of the comb tooth sealing structure; 2) selecting basic parameters such as material, installation position, shape, and size of the damping ring according to the existing comb tooth sealing structure; 3) determining the vibration displacement of the damping ring installation position and the vibration stress of the dangerous point through a finite element calculation program; 4) calculating the friction energy consumption of the damping ring under different vibration stresses and the damping ratio that can be provided according to the method of the present invention, obtaining the damping characteristic curve of the damping ring, and then determining the critical vibration stress, peak damping ratio and its corresponding vibration stress, etc.; 5) determining the damping ring parameters that meet the requirements of the comb tooth sealing structure according to the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters.

[0048] The present invention establishes an analysis method for the vibration reduction characteristics of the damping ring of the engine comb seal structure, providing a basis and reference for the subsequent structural design of the damping ring. The method of the present invention can be used to evaluate the vibration reduction effect of the existing damping ring design on the one hand, and determine whether the design goal is achieved; on the other hand, the design parameters of the damping ring structure can be optimized to meet the design requirements of the damping ratio: before the main structure assessment point reaches the allowable vibration stress, the damping ring can provide the largest possible damping ratio, and the critical vibration stress is relatively small, that is, the damping ring design point needs to be located on the left half of the damping characteristic curve.

[0049] Compared with other damper vibration reduction analysis methods, the present invention does not require contact-related nonlinear dynamic response calculations, and can effectively shorten the design time of damping ring vibration reduction. The present invention uses vibration stress rather than traditional vibration displacement, and uses vibration stress, which is more concerned in the design stage, as a characterization quantity to guide the design, and is suitable for vibration reduction design stages that require repeated iterations. BRIEF DESCRIPTION OF THE DRAWINGS

[0050] The drawings constituting a part of the present application are used to provide a further understanding of the present application. The illustrative embodiments and descriptions of the present application are used to explain the present application and do not constitute an improper limitation on the present application. In the drawings:

[0051] Figure 1 It is a flow chart of a vibration reduction design method of a damping ring of a comb teeth sealing structure according to an embodiment of the present invention;

[0052] Figure 2 A schematic diagram of the geometric shape of a comb tooth sealing structure according to an embodiment of the present invention;

[0053] Figure 3 It is a meridian view of the comb teeth sealing structure of an embodiment of the present invention and a schematic diagram of its assembly with a rectangular cross-section open damping ring;

[0054] Figure 4Schematic diagram of the grate seal structure parameters of an embodiment of the present invention, wherein (a) is the modal total displacement, and (b) is the modal von Mises stress;

[0055] Figure 5 is a damping characteristic curve diagram of an embodiment of the present invention;

[0056] Figure 6 1 is a damping characteristic curve under different damping ring mass densities according to an embodiment of the present invention. DETAILED DESCRIPTION

[0057] It should be noted that, in the absence of conflict, the embodiments and features in the embodiments of the present application can be combined with each other. The present application will be described in detail below with reference to the accompanying drawings and in combination with the embodiments.

[0058] It should be noted that the steps shown in the flowcharts of the accompanying drawings can be executed in a computer system such as a set of computer executable instructions, and that, although a logical order is shown in the flowcharts, in some cases, the steps shown or described can be executed in an order different from that shown here.

[0059] Embodiment 1

[0060] like Figure 1 As shown, this embodiment provides a vibration reduction design method for a damping ring of a comb tooth sealing structure, which can obtain the vibration reduction characteristics of the damping ring and characterize it with a damping characteristic curve, that is, a curve showing the change of the equivalent damping ratio provided by the damping ring with the vibration stress of the dangerous point of the comb tooth sealing structure under the mode of interest. It includes:

[0061] Step 1: Determine the vibration stress range and allowable vibration stress σ according to the comb seal structural material a ;

[0062] In this embodiment, the geometric shape of the comb teeth sealing structure is as follows: Figure 2 As shown, its meridian plane diagram and the schematic diagram of assembly with the rectangular cross-section open damping ring are shown in Figure 3 As shown, the sealing structure material is GH4169. According to engineering experience, the vibration stress consideration range is about 0-150Mpa (it can also be adjusted in time according to actual conditions), and it is expected that the damping ring can achieve the best damping and vibration reduction effect in the vibration stress range above 10MPa. Therefore, in this embodiment, the vibration stress range of the comb tooth sealing structure is selected as 0-150MPa, and the allowable vibration stress is 12MPa.

[0063] Step 2: According to the comb teeth sealing structure, select the material, installation position, shape, size, etc. of the damping ring, and set the mass density of the damping ring material as ρ d , the radius of the damping ring is R d , the cross-sectional area of ​​the damping ring is A d, the friction coefficient is μ;

[0064] In this step, the selected damping ring material can be the same as the comb teeth sealing structure material, which can withstand higher temperatures; the damping ring installation position can be preliminarily selected as the maximum possible vibration displacement of the main structure;

[0065] In this embodiment, a rectangular cross-section open damping ring is selected, and the damping ring material selected is GH4169 material; its installation position is preliminarily selected as the free end of the comb tooth sealing structure, and the specific size parameters of the damping ring are shown in Table 1.

[0066] Table 1 Damping ring parameters

[0067]

[0068] Step 3: Calculate the modes of the comb seal structure at different speeds using the finite element method, and draw the corresponding Campbell diagram to find out the modes that may have resonance risks and determine the dangerous vibration modes and dangerous speeds that need to be paid attention to;

[0069] In this step, the finite element method is used to perform modal calculations and the Campbell diagram is drawn, which are conventional technical means in the art and will not be described in detail here.

[0070] The dangerous speed of this embodiment is Ω=2227 r / min, and the low-order dangerous mode is 6-pitch diameter 1st order.

[0071] Step 4: For the dangerous vibration mode and dangerous speed determined in step 3, the prestressed modal analysis of the comb tooth sealing structure under the dangerous speed is performed by finite element method;

[0072] In this step, the mode obtained in this embodiment is as follows Figure 4 As shown, it is the 1st order vibration mode of 6 node diameters.

[0073] Step 5: For the dangerous speed determined in step 3, the prestressed modal analysis of the grate seal structure under this dangerous speed is performed by finite element method, and the modal displacement B at the monitoring point of the grate seal structure under the vibration mode of interest is extracted. ref , modal vibration stress σ at the dangerous point ref and the modal vibration kinetic energy E of the entire structure k,ref ;

[0074] In this step, the monitoring point of the vibration amplitude is generally selected as the upper edge position of the damping ring installation position, such as Figure 3 As shown in A; the monitoring point of the modal stress amplitude is selected at the point where the modal vibration stress of the comb tooth sealing structure is the largest, that is, as the danger point, such as the pitch-diameter vibration, which is generally at the top of the comb tooth or the root of the entire sealing structure; the modal vibration kinetic energy is the kinetic energy of the entire structure;

[0075] In this embodiment, the modal displacement and stress results of the comb tooth sealing structure calculated by the finite element method are as follows: Figure 4 (a) and Figure 4 (b) shows that the modal parameters shown in Table 2 are extracted for subsequent vibration reduction design analysis.

[0076] Table 2 Modal parameters of the comb seal structure obtained by finite element method

[0077]

[0078] Step 6: This embodiment innovatively traverses the vibration stress σ of the grate seal structure from small to large within the vibration stress range of the grate seal structure, and uses the modal displacement B at the monitoring point extracted in step 5 ref , vibration stress at dangerous point σ ref and the vibration kinetic energy E of the entire structure k,ref , according to the proportional conversion relationship between vibration parameters and modal parameters under small deformation conditions σ / σ ref =B / B ref =(E k / E k,ref ) 1 / 2 , and obtain the vibration displacement B and structural vibration kinetic energy E under the current vibration stress σ k ;

[0079] In this embodiment, the maximum modal vibration kinetic energy E k,ref =41895J, modal vibration stress at dangerous point σ ref =3703MPa, see Table 2 for specific values, see the first column of Table 4 for the input vibration stresses, and the input can start from 0MPa.

[0080] Step 7: According to the selected dangerous speed and mode, obtain the contact normal pressure P per unit length of the contact surface between the damping ring and the comb seal structure; the contact stiffness k can be estimated according to the selected contact model. t , k n ;

[0081] In this step, the contact positive pressure per unit length P only considers the contact positive pressure caused by centrifugal action, and assumes that the positive pressure is evenly distributed. The calculation method of the contact positive pressure per unit length is P = ρ d A d ω 2 R d , where ρ d is the mass density of the damping ring material, A d Damping ring cross-sectional area, R d is the radius of the damping ring, ω is the rotational angular velocity of the comb teeth sealing structure;

[0082] In this embodiment, the contact normal pressure per unit length P=0.83N / mm is obtained; in addition, in order to simplify the calculation, the classical Coulomb friction model is adopted, assuming that the contact normal pressure is uniformly distributed along the circumference during the vibration process, and the damping ring and the mounting groove are not separated during the vibration process, so the contact stiffness k is not considered for the time being. t , k n .

[0083] Step 8: Calculate the critical angle θ0 of the sliding and sticking areas on the contact surface between the comb tooth sealing structure and the damping ring. At this angle, the static friction force is equal to the sliding friction force.

[0084] In this step, the critical angle θ0 between the slip and sticky regions is calculated as:

[0085]

[0086] Where N is the number of vibration pitch diameters of the comb tooth sealing structure, P is the contact normal pressure per unit length of the contact surface obtained in step 7, B is the vibration displacement B under the current vibration stress σ of the dangerous point obtained in step 6, and R f is the radius of the contact surface, E is the Young's elastic modulus of the damping ring material, C s With R s are the radial semi-thickness of the comb seal structure and the radius of the neutral layer, C d With R d are the radial semi-thickness of the damping ring and the radius of the neutral layer, respectively. It is worth noting that the critical angle θ0 needs to be calculated for each vibration stress σ.

[0087] In this embodiment, the dimension parameters of the damping ring and the comb teeth sealing structure are shown in Table 3. The critical angle θ0 calculated from each vibration stress is shown in the second column of Table 4.

[0088] Table 3 Dimensional parameters of damping ring and comb seal structure

[0089]

[0090] Step 9: Calculate the friction energy E of the contact surface during one vibration cycle f ;

[0091] As an innovative implementation method to increase the contact surface friction energy E f The calculation method is:

[0092]

[0093] It is worth noting that the friction energy E needs to be calculated for each vibration stress σ f In this embodiment, the friction energy E calculated from each vibration stress is f See the data in column 3 of Table 4.

[0094] Step 10: Friction energy E calculated in step 9 f And the structural vibration kinetic energy E obtained in step 6 k , using the energy method, calculate the equivalent damping ratio ζ provided by the damping ring under the current vibration stress σ;

[0095] As an additional innovative implementation method, the calculation method of the equivalent damping ratio ζ is:

[0096]

[0097] Step 11: Change the magnitude of the input vibration stress σ to obtain the equivalent damping ratio of the damping ring under a series of vibration stresses, thereby forming a damping characteristic curve of the damping ring, that is, a curve showing the variation of the equivalent damping ratio that the damping ring can provide with respect to the vibration stress at the dangerous point of the comb tooth sealing structure under the mode of interest;

[0098] In this step, the curve of the change of the equivalent damping ratio of the damping ring with the vibration stress of the dangerous point is the damping characteristic curve.

[0099] In this embodiment, the vibration stress of the dangerous point, the critical angle of the slip and sticking area, the friction energy consumption of the contact surface within a vibration cycle and the corresponding equivalent damping ratio are shown in Table 4. The resulting damping characteristic curve is as follows: Figure 5 shown.

[0100] Table 4 Damping ring vibration reduction analysis data

[0101]

[0102] Step 12: Extract the peak damping ratio ζ from the damping characteristic curve obtained in step 11 max and its corresponding vibration stress σ m , this peak damping ratio vibration stress σ m and allowable vibration stress σ a Compare; when the peak damping ratio vibration stress σ m and allowable vibration stress σ a When the difference is large, it is considered that the proposed damping ring design parameters in step 2 are not optimal; then select different damping ring design parameters, repeat steps 2 and steps 6 to 10 (if vibration reduction analysis is required for different vibration modes, steps 2 to 10 need to be repeated) until the two vibration stresses are close, and it is considered that the optimal damping ring design parameters are obtained.

[0103] In this embodiment, the critical vibration stress σ cr , peak damping ratio ζ max and its corresponding vibration stress σ m like Figure 5 As shown, they are σ cr =1.8MPa,ζmax =1.3%,σ m =6.5MPa. Allowable vibration stress σ a According to experience, it is taken as 12MPa. At this time, the peak damping ratio vibration stress σ m and allowable vibration stress σ a The difference is large, and the damping ring design parameters need to be changed.

[0104] In this embodiment, the damping ring mass density is taken as an example to optimize the design of parameters. d The new damping ring density ρ is taken as a multiple of ’ d Damping ring, repeat steps 2 and 6 to 10, calculate and draw the damping characteristic curves under different damping ring mass densities, such as Figure 6 As shown. When the peak damping ratio vibration stress σ m and allowable vibration stress σ a When approaching, the density is 2ρ d As the optimized damping ring density value.

[0105] The open damping ring involved in the present invention cannot contact the bottom surface of the installation groove of the comb tooth sealing structure at all places under the static interference installation condition, but there is a non-contact area with a certain angle range near the opening. The size of the non-contact area is related to the contact surface pressure, and the contact pressure mainly comes from the centrifugal load of the structural rotation. As the speed increases, the non-contact area will gradually decrease, which will improve the vibration reduction effect of the damping ring to a certain extent.

[0106] Beneficial effects of this embodiment:

[0107] This embodiment establishes an analysis method for the vibration reduction characteristics of the damping ring of the engine comb seal structure, providing a basis and reference for the subsequent structural design of the damping ring. On the one hand, this embodiment can be used to evaluate the vibration reduction effect of the existing damping ring design to determine whether the design goal is achieved; on the other hand, the design parameters of the damping ring structure can be optimized to meet the design requirements of the damping ratio: before the main structure assessment point reaches the allowable vibration stress, the damping ring can provide the largest possible damping ratio, and the critical vibration stress is relatively small, that is, the damping ring design point needs to be located on the left half of the damping characteristic curve.

[0108] Compared with other damper vibration reduction analysis methods, this embodiment does not need to perform nonlinear dynamic response calculations involving contact, which can effectively shorten the design time of damping ring vibration reduction. In addition, this embodiment uses the vibration stress, which is more concerned in the design stage, as a characterization quantity to guide the design, and is suitable for the vibration reduction design stage that requires repeated iterations. Taking the nonlinear dynamic response calculation method containing dry friction contact based on the reduction model as an example, when calculating a single damping characteristic curve under a certain set of damping ring parameters in this embodiment, each time a vibration stress-damping ratio data point is obtained, it is necessary to calculate dozens of dynamic responses under the excitation frequency to determine the displacement response and stress response of the resonance. The calculation time of a damping characteristic curve is about 20 hours, while the method of this embodiment is about 2 hours, and the time cost is reduced by more than 90%; and the more damping ring parameter combinations considered, the more vibration stress points, and the more dangerous modes, the higher the calculation efficiency of the method of this embodiment, and the more obvious the advantages.

[0109] Embodiment 2

[0110] Based on the same inventive concept, this embodiment also provides a vibration reduction design system for a comb tooth sealing structure damping ring, comprising:

[0111] A first determination module is used to determine the vibration stress range and allowable vibration stress of the comb tooth sealing structure according to the existing comb tooth sealing structure material;

[0112] A selection module is used to select basic parameters of the damping ring according to the existing comb tooth sealing structure, wherein the basic parameters include: material, installation position, shape, and size;

[0113] A second determination module is used to determine the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the modal vibration kinetic energy according to the vibration stress range and the basic parameters;

[0114] A first calculation module is used to calculate the friction energy consumption of the damping ring and the damping ratio that can be provided under different vibration stresses according to the modal displacement, the vibration stress of the dangerous point and the modal vibration kinetic energy, so as to obtain the damping characteristic curve of the damping ring;

[0115] A third determination module is used to determine the critical vibration stress, the peak damping ratio and the corresponding vibration stress according to the damping characteristic curve;

[0116] The second calculation module is used to determine the damping ring parameters that meet the requirements of the comb tooth sealing structure according to the critical vibration stress, peak damping ratio and its corresponding vibration stress, combined with the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters.

[0117] The vibration reduction design system of a damping ring of a comb teeth sealing structure provided in this embodiment has all the advantages of the vibration reduction design method of a damping ring of a comb teeth sealing structure provided in the first embodiment.

[0118] Embodiment 3

[0119] This embodiment further discloses a computer device, including a memory, a processor, and a computer program stored in the memory, wherein the processor executes the computer program to implement the steps of the method described in the first embodiment.

[0120] Embodiment 4

[0121] This embodiment further discloses a computer-readable storage medium on which a computer program is stored. When the computer program is executed by a processor, the steps of the method described in the first embodiment are implemented.

[0122] Embodiment 5

[0123] This embodiment also discloses a computer program product, including a computer program, which implements the steps of the method described in the first embodiment when executed by a processor.

[0124] The above are only preferred specific implementations of the present application, but the protection scope of the present application is not limited thereto. Any changes or substitutions that can be easily thought of by a person skilled in the art within the technical scope disclosed in the present application should be included in the protection scope of the present application. Therefore, the protection scope of the present application should be based on the protection scope of the claims.

Claims

1. A vibration reduction design method for a comb tooth sealing structure damping ring, characterized in that: The following steps are involved: Determine the vibration stress range and allowable vibration stress of the comb tooth sealing structure according to the existing comb tooth sealing structure materials; According to the existing comb teeth sealing structure, the basic parameters of the damping ring are selected, wherein the basic parameters include: material, installation position, shape, and size; Determining the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the modal vibration kinetic energy according to the vibration stress range and the basic parameters; According to the modal displacement, the vibration stress of the dangerous point and the modal vibration kinetic energy, the friction energy consumption of the damping ring under different vibration stresses and the damping ratio that can be provided are calculated to obtain the damping characteristic curve of the damping ring; According to the damping characteristic curve, determining the critical vibration stress, the peak damping ratio and the corresponding vibration stress; According to the critical vibration stress, the peak damping ratio and the corresponding vibration stress, combined with the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters, the damping ring parameters that meet the requirements of the comb tooth sealing structure are determined.

2. The method according to claim 1, characterized in that Determining the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the vibration kinetic energy according to the vibration stress range and the basic parameters includes: According to the vibration stress range and the basic parameters, the modes of the comb tooth sealing structure at different speeds are calculated by the finite element method, and a Campbell diagram is drawn to find out the modes with resonance risks, and determine the dangerous vibration modes and dangerous speeds that need to be paid attention to; According to the dangerous rotation speed, a prestressed modal analysis of the grate tooth sealing structure is performed by using the finite element method; According to the prestressed modal analysis, the modal displacement at the monitoring point of the comb tooth sealing structure under the dangerous vibration mode, the vibration stress at the dangerous point and the vibration kinetic energy are obtained.

3. The method according to claim 1, characterized in that: According to the modal displacement, vibration stress at the dangerous point and modal vibration kinetic energy, the friction energy consumption of the damping ring under different vibration stresses and the damping ratio that can be provided are calculated, and the damping characteristic curve of the damping ring is obtained, including: According to the modal displacement, vibration stress at the dangerous point and modal vibration kinetic energy, the vibration displacement and structural vibration kinetic energy under the current vibration stress are obtained through the proportional conversion relationship between the vibration parameters and the modal parameters under the small deformation condition; According to the selected dangerous vibration mode and dangerous speed, the contact normal pressure per unit length of the contact surface between the damping ring and the comb teeth sealing structure is obtained; According to the vibration displacement, structural vibration kinetic energy and contact normal pressure under the current vibration stress, the critical angle of the slip and sticking area on the contact surface between the comb tooth sealing structure and the damping ring is calculated; According to the critical angle, the friction energy consumption of the contact surface within one vibration cycle is calculated; Calculating the equivalent damping ratio provided by the damping ring under the current vibration stress according to the friction energy consumption and the structural vibration kinetic energy; By changing the input vibration stress σ, the equivalent damping ratio of the damping ring under a series of vibration stresses is obtained, and the damping characteristic curve of the damping ring is formed.

4. The method according to claim 3, characterized in that The critical angle between slip and sticking regions is calculated as: Contact surface friction energy E f The calculation formula is: The calculation formula of equivalent damping ratio ζ is: Among them, θ0 is the critical angle, N is the vibration node number of the grate seal structure, P is the contact positive pressure per unit length of the contact surface, B is the vibration displacement of the dangerous point under the current vibration stress σ, R f is the radius of the contact surface, E is the Young's elastic modulus of the damping ring material, C s With R s are the radial semi-thickness of the comb seal structure and the radius of the neutral layer, C d With R d are the radial semi-thickness of the damping ring and the radius of the neutral layer, E k is the vibration kinetic energy.

5. The method according to claim 1, characterized in that The damping ring parameters that meet the requirements of the comb tooth sealing structure include: Obtain the allowable vibration stress of the comb tooth sealing structure; comparing the vibration stress corresponding to the peak damping ratio with the allowable vibration stress; If the vibration stress corresponding to the peak damping ratio is significantly different from the allowable vibration stress, different damping ring design parameters are selected and the calculation is repeated; If the vibration stress corresponding to the peak damping ratio is close to the allowable vibration stress, the optimal damping ring design parameters are obtained.

6. A vibration reduction design system for a comb tooth sealing structure damping ring, characterized in that: include: A first determination module is used to determine the vibration stress range and allowable vibration stress of the comb teeth sealing structure according to the existing comb teeth sealing structure materials; A selection module is used to select basic parameters of the damping ring according to the existing comb tooth sealing structure, wherein the basic parameters include: material, installation position, shape, and size; A second determination module is used to determine the modal displacement of the damping ring installation position, the vibration stress of the dangerous point and the modal vibration kinetic energy according to the vibration stress range and the basic parameters; A first calculation module is used to calculate the friction energy consumption of the damping ring and the damping ratio that can be provided under different vibration stresses according to the modal displacement, the vibration stress of the dangerous point and the modal vibration kinetic energy, so as to obtain the damping characteristic curve of the damping ring; A third determination module is used to determine the critical vibration stress, the peak damping ratio and the corresponding vibration stress according to the damping characteristic curve; The second calculation module is used to determine the damping ring parameters that meet the requirements of the comb tooth sealing structure according to the critical vibration stress, peak damping ratio and its corresponding vibration stress, combined with the allowable vibration stress and the damping vibration reduction characteristics under different damping ring parameters.

7. A computer device comprising a memory, a processor and a computer program stored in the memory, characterized in that: The processor executes the computer program to implement the steps of the method of claims 1-5.

8. A computer-readable storage medium having a computer program stored thereon, characterized in that: When the computer program is executed by a processor, the steps of the method according to claims 1 to 5 are implemented.

9. A computer program product, comprising a computer program, characterized in that When the computer program is executed by a processor, the steps of the method according to claims 1 to 5 are implemented.

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