Vibration transmission path analysis method of roller centrifugal casting machine

Abstract

The invention provides a vibration transmission path analysis method for a roller centrifugal casting machine, and relates to the technical field of vibration analysis, a three-dimensional geometric model of the roller centrifugal casting machine is established, a finite element method is adopted to analyze each component unit, and a mass matrix and a stiffness matrix of each component unit are obtained; performing modal analysis based on the mass matrix and the stiffness matrix of each component unit, and determining a maximum deformation point of each component unit; when the maximum deformation point of each component unit is a linear system, calculating a vibration transmission weight passing through each maximum deformation point in the linear system; when the maximum deformation point of each component unit is a nonlinear system, the vibration transmission weight passing through a plurality of transmission paths formed by the maximum deformation points is calculated, and the potential vibration problem is found in the early stage.

Description

Technical Field

[0001] The invention proposes a vibration transfer path analysis method for a roller centrifugal casting machine, and relates to the technical field of vibration analysis. Background Art

[0002] The vibration generated by the roller centrifugal casting machine during operation and its transmission are mainly caused by multiple factors. For example, the imbalance of rotating parts: including the rotating shaft, casting head and other rotating parts of the centrifugal casting machine. If the mass distribution is uneven, unbalanced force will be generated during rotation, which will cause vibration. Another example is structural defects: such as casting defects, welding cracks, etc. These defects may cause stress concentration under high-speed rotation or force conditions, leading to local vibration. Another example is improper installation: If the parts are not installed properly or not fixed firmly, vibration is also likely to occur. As the use time increases, the bearings may wear, resulting in an increase in the gap, thereby generating vibration. Elastic components such as rubber seals and springs may also become a source of vibration as their performance deteriorates over time.

[0003] Analyzing the vibration transmission path of a centrifugal roller casting machine usually involves dynamic analysis in mechanical engineering. This method can help identify and understand how vibration propagates in the equipment, so that measures can be taken to reduce or eliminate unnecessary vibration and improve the stability and service life of the equipment.

[0004] In the existing technology, there are many technical problems when analyzing the vibration transmission path of the roller centrifugal casting machine. For example, when building a three-dimensional geometric model, if the model is overly simplified or ignores certain details (such as material nonlinearity, contact surface friction, etc.), it may cause a large deviation between the analysis results and the actual situation. For another example, the vibration data collection during the operation of the actual equipment may be subject to various restrictions, such as difficult sensor layout and severe signal interference, which will affect the accuracy of subsequent analysis. At the same time, the roller centrifugal casting machine may involve multiple physical phenomena such as fluid flow, heat conduction, and electromagnetic fields during operation. The interaction of these multiple physical fields makes vibration analysis more complicated.

[0005] Analyzing the vibration transmission path of the roller centrifugal casting machine can not only improve the stability of the roller centrifugal casting machine, extend its service life, reduce maintenance costs, but also improve production efficiency. For example, through improved design and optimization, the vibration reduction effect of the centrifuge has been significantly improved, and a temperature monitoring system has been added to achieve more accurate automatic control, thereby improving the reliability and efficiency of the equipment. In addition, the causes of mill vibration and its suppression measures are discussed, emphasizing the reduction of vibration by adjusting design parameters and increasing system damping, which is also of reference value for centrifugal casting machines. Summary of the invention

[0006] In order to solve the above technical problems, the present invention proposes a vibration transmission path analysis method for a roller centrifugal casting machine, comprising the following steps:

[0007] Step 1: Establish a three-dimensional geometric model of the roller centrifugal casting machine, use the finite element method to analyze multiple component units, and obtain the mass matrix and stiffness matrix of the multiple component units;

[0008] Step 2: Perform modal analysis based on the mass matrix and stiffness matrix of each component unit to determine the maximum deformation point of each component unit;

[0009] Step 3: When the deformation variable of the maximum deformation point of each component unit is linearly distributed, the vibration transfer weight passing through each maximum deformation point in the vibration system is calculated to determine the component unit with the largest vibration transfer weight;

[0010] Step 4: When the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, calculate the path vibration weight of the transmission path composed of multiple maximum deformation points in the vibration system, and determine the vibration source component unit of the transmission path with the largest path vibration weight.

[0011] In the preferred technical solution, in the step 2, the position coordinates of the grid points on the grid of the component unit are assumed to be (x, y), and the modal analysis is implemented by solving the following characteristic equation:

[0012]

[0013] Among them, M T is the mass matrix, K T is the stiffness matrix, C T is the damping matrix, ω i is the ith grid point eigenfrequency of the component unit, is the vibration mode vector of the corresponding ith grid point, and solving the eigenvalue equation gives a series of characteristic frequencies ω of the grid points. i and the corresponding vibration mode vector

[0014] In a preferred technical solution, after the vibration type is obtained, the deformation of the component unit under each vibration mode vector is analyzed, and the position with the largest deformation amplitude in the component unit is determined, which is the maximum deformation point of the component unit.

[0015] In the preferred technical solution, in step three, when analyzing vibration transfer, when the deformation variable of the maximum deformation point of each component unit is linearly distributed, the transfer function and the vibration signal intensity data are used to comprehensively calculate the vibration transfer weight passing through each maximum deformation point in the vibration system.

[0016] In the preferred technical solution, the vibration transfer weight C of the maximum deformation point of the jth component unit to the target point is j Expressed as:

[0017] C j =H j (ω j )F j (ω j )

[0018] The synthesized vibration transfer weight P:

[0019] P=∑ j C j =∑ j H j (ω j )F j (ω j );

[0020] Among them, H j (ω j ) is the transfer function of the maximum deformation point of the jth component unit to the target point, F j (ω j ) is the vibration signal intensity of the maximum deformation point of the jth component unit, ω j is the characteristic frequency of the maximum deformation point of the jth component unit.

[0021] In the preferred technical solution, in the step 4, when the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, it is assumed that there are M vibration source signals in the vibration system, and the mth vibration source signal is x m (m=1,2,…,M), there are N response paths, and the nth response path is r n (n=1,2,…,N); then the total response R at the vibration frequency is:

[0022] R = ZX;

[0023] In the formula, R = [r 1 ,r 2 ,…,r n ,…,r N ] T , the vibration source signal matrix X is [x 1 ,x 2 ,…,x m ,…,x M ] T ; Z is the N×M transmissibility matrix, and the constituent elements of the transmissibility matrix are Z nm is the transfer function from the mth vibration source input to the nth response path, then the vibration transfer weight of the mnth transfer path is expressed as C nm :

[0024] C nm =Z nm x m .

[0025] In the preferred technical solution, given the transfer function H(ω) between the vibration source and the target point and the response function S(ω) of the target point, the excitation force L(ω) is calculated according to the following formula:

[0026]

[0027] in, is the vibration amplitude at the target point, and ω is the vibration frequency.

[0028] In the preferred technical solution, in the step one, the design drawings, material properties, and geometric dimension information of the roller centrifugal casting machine are collected; the boundary conditions used in the simulation are clarified, and a three-dimensional geometric model of the roller centrifugal casting machine is created using modeling software; and the roller centrifugal casting machine is decomposed into multiple component units through discretization.

[0029] In the preferred technical solution, meshing is performed according to the geometric characteristics of each component unit, and the mass matrix M of each component unit is calculated using the finite element method. T , stiffness matrix K T And the damping matrix C T .

[0030] In a preferred technical solution, in step one, the multiple component units include: a motor unit, a transmission unit, rollers and bearings, and a centrifugal casting unit.

[0031] Compared with the prior art, the present invention has the following beneficial technical effects:

[0032] 1: Establish a three-dimensional geometric model of the centrifugal roller casting machine, use the finite element method to analyze each component unit, and obtain the mass matrix and stiffness matrix of each component unit; through the modal analysis of each component unit, obtain the position coordinates of the maximum deformation point of each component unit. By determining the maximum deformation point through modal analysis, it is possible to accurately identify which component units play a key role in the vibration, thereby helping to quickly locate the vibration source.

[0033] 2: When the deformation variable of the maximum deformation point of each component unit is linearly distributed, the vibration transfer weight passing through each maximum deformation point in the vibration system is calculated, and the component unit with the largest vibration transfer weight is determined. When the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, the path vibration weight of the transmission path passing through multiple maximum deformation points in the vibration system is calculated, and the vibration source component unit of the transmission path with the largest path vibration weight is determined. Analyzing the vibration system as both a linear and a nonlinear system can provide a more comprehensive understanding of the vibration transmission mechanism, and maintain the stability and reliability of the system under complex working conditions.

[0034] 3: By analyzing the vibration transmission path, it is possible to analyze which parts may fail prematurely due to excessive vibration, so as to take preventive measures and extend the life of the equipment. By detecting potential vibration problems early, small faults can be repaired before they develop into big problems, thus reducing downtime and maintenance costs. BRIEF DESCRIPTION OF THE DRAWINGS

[0035] In order to more clearly illustrate the technical solutions in the embodiments of the present invention, the accompanying drawings required for use in the description of the embodiments will be briefly introduced below. Obviously, the accompanying drawings in the following description are only some embodiments of the present invention. For ordinary technicians in this field, other accompanying drawings can be obtained based on these accompanying drawings without paying creative labor.

[0036] Figure 1 It is a schematic flow chart of a vibration transmission path analysis method of a roller centrifugal casting machine of the present invention;

[0037] Figure 2 This is a schematic diagram of mesh division of a component unit of a roller centrifugal casting machine;

[0038] Figure 3 It is the waveform of the collected vibration signal after preprocessing. DETAILED DESCRIPTION

[0039] In order to make the purpose, technical solution and advantages of the embodiments of the present application clearer, the technical solution in the embodiments of the present application will be clearly and completely described below in conjunction with the drawings in the embodiments of the present application. Obviously, the described embodiments are part of the embodiments of the present application, not all of the embodiments. Based on the embodiments in the present application, all other embodiments obtained by ordinary technicians in this field without creative work are within the scope of protection of this application.

[0040] In the drawings of the specific embodiments of the present invention, in order to better and more clearly describe the working principles of the various components in the system, the connection relationship of the various parts in the device is shown, which only clearly distinguishes the relative position relationship between the various components, and cannot constitute a limitation on the signal transmission direction, connection sequence and structural size, size and shape of each part within the component or structure.

[0041] Secondly, the term "one embodiment" or "embodiment" as used herein refers to a specific feature, structure, or characteristic that may be included in at least one implementation of the present invention. The term "in one embodiment" that appears in different places in this specification does not necessarily refer to the same embodiment, nor does it refer to a separate or selective embodiment that is mutually exclusive with other embodiments.

[0042] Example 1

[0043] like Figure 1 FIG. 1 is a flow chart of a vibration transfer path analysis method for a roller centrifugal casting machine according to Example 1. The vibration transfer path analysis method comprises the following steps:

[0044] Step 1: Establish a three-dimensional geometric model of the roller centrifugal casting machine, use the finite element method to analyze multiple component units, and obtain the mass matrix and stiffness matrix of multiple component units.

[0045] Collect basic information such as design drawings, material properties (such as density, elastic modulus, Poisson's ratio, etc.), and geometric dimensions of the roller centrifugal casting machine; clarify the boundary conditions used in the simulation, such as fixed constraints, rotation constraints, etc. Use modeling software to create a three-dimensional geometric model of the roller centrifugal casting machine.

[0046] Through discretization, the roller centrifugal casting machine is decomposed into many small and simple component units, including motor unit, transmission unit, roller and bearing and centrifugal casting unit.

[0047] Select the appropriate mesh type (such as tetrahedron, hexahedron, etc.) according to the geometric characteristics and analysis requirements of each component unit, and use finite element analysis software (such as ANSYS, Abaqus, Nastran, etc.) to perform mesh division. Figure 2 For critical areas (such as connections and high stress areas), it may be necessary to refine the mesh to improve the calculation accuracy.

[0048] For each component unit mesh, the finite element method is used to calculate its mass matrix M T , stiffness matrix K T , and if damping is considered, there is also the damping matrix C T These matrices are all square matrices of size n×n, where n is the total number of degrees of freedom.

[0049] Step 2: Perform modal analysis based on the mass matrix and stiffness matrix of each component unit to determine the maximum deformation point of each component unit.

[0050] Modal analysis is used to study the dynamic characteristics of structures. It can determine the natural frequency (natural frequency) of the structure and its corresponding vibration mode. In modal analysis, the maximum deformation point refers to the location where the structure deforms the most under a certain vibration mode. These locations are usually the most fragile parts of the structure and are most likely to be damaged. Through modal analysis, these maximum deformation points can be found.

[0051] Assume that the position coordinates of the grid points on the grid of the component unit are (x, y), and the modal analysis is achieved by solving the following characteristic equation:

[0052]

[0053] Among them, ω i is the ith grid point eigenfrequency of the component unit, is the vibration mode vector of the corresponding i-th grid point. Through this analysis, the eigenvalue equation is solved to obtain the characteristic frequencies ω of a series of grid points. i and the corresponding vibration mode vector M T is the mass matrix, K T is the stiffness matrix, C T is the damping matrix.

[0054] Determination of the maximum deformation point:

[0055] After obtaining the vibration type, the deformation of the component unit under each vibration mode vector can be analyzed. The maximum deformation point is the position with the largest deformation amplitude in the component unit.

[0056] Preferably, the maximum deformation point can be determined intuitively by observing the vibration mode diagram, and can also be found quantitatively by calculating the amplitude of the vibration mode vector.

[0057] By comparing the deformation of the grid points on the grid of the component unit, Δ(x, y) is used to find the grid point with the largest deformation, i.e., the maximum deformation point. Specifically, it is necessary to find the maximum absolute value of Δ(x, y) and record the corresponding position coordinates of the maximum deformation point (x 0 ,y 0 ).

[0058] Here is a code example showing how to calculate the mode shape vectors, determine the deformation, find the points of maximum deformation, and record the coordinates:

[0059]

[0060] Step 3: When the deformation variable of the maximum deformation point of each component unit is linearly distributed, calculate the vibration transfer weight passing through each maximum deformation point in the vibration system, and determine the component unit with the largest vibration transfer weight.

[0061] When analyzing vibration transmission, when the deformation variable of the maximum deformation point of each component unit is linearly distributed, the vibration transmission weight passing through each maximum deformation point in the vibration system is comprehensively calculated using the transfer function and the vibration signal intensity data.

[0062] Specifically, the vibration transfer weight C of the maximum deformation point of the jth component unit to the target point is j Expressed as:

[0063] C j =H j (ω j )F j (ω j )

[0064] The synthesized vibration transfer weight P

[0065] P=∑ j C j =∑ j H j (ω j )F j (ω j );

[0066] Among them, H j (ω j ) is the transfer function of the maximum deformation point of the jth component unit to the target point, F j (ω j ) is the vibration signal intensity of the maximum deformation point of the jth component unit, ω j is the characteristic frequency of the maximum deformation point of the jth component unit.

[0067] The vibration transfer weight of each component unit is calculated in turn, and the component unit with the largest vibration transfer weight is determined.

[0068] Step 4: When the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, calculate the path vibration weight of the transmission path composed of multiple maximum deformation points in the vibration system, and determine the vibration source component unit of the transmission path with the largest path vibration weight.

[0069] When the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, suppose there are M vibration source signals in the vibration system, and the mth vibration source signal is x m (m=1,2,…,M), there are N response paths, and the nth response path is r n (n=1,2,…,N).

[0070] Each response path is determined by the response caused by the superimposed vibration of each vibration source signal.

[0071] The total response R at the vibration frequency is:

[0072] R = ZX;

[0073] In the formula, R = [r 1 ,r 2 ,…,r n ,…,r N ] T , the vibration source signal matrix X is [x 1 ,x 2 ,…,x m ,…,x M ] T ; Z is the N×M transmissibility matrix, and the constituent elements of the transmissibility matrix are Z nm is the transfer function from the mth vibration source input to the nth response path, then the path vibration weight of the mnth transfer path is expressed as C nm :

[0074] C nm =Z nm x m .

[0075] The path vibration weight of each transmission path in the vibration system is calculated in turn, and the vibration source component unit of the transmission path with the largest path vibration weight is determined.

[0076] In a preferred embodiment, by determining the path vibration weights of the transfer paths and understanding the impact of vibration transfer, measures can be taken to reduce or control the vibration transfer on these paths, and can assist in diagnosing potential problems in the centrifugal roller casting machine, such as loose parts, cracks, etc.

[0077] In a preferred embodiment, the vibration transfer weights of the transfer paths are experimentally verified.

[0078] After performing a vibration transfer weight analysis of the transfer path, the accuracy of the calculated results can be verified experimentally. For example, an impact hammer can be used to hit different parts of the structure and the response can be measured with an accelerometer. The data can then be analyzed to identify the eigenfrequencies and mode shape vectors of the system. The experimental results can be compared with the calculated results to confirm the validity of the theoretical model and adjust the model parameters as needed.

[0079] Example 2

[0080] Before the path analysis method, it is necessary to clarify the location and type of vibration source in the roller centrifugal casting machine. Determining the specific location and type of vibration source in the roller centrifugal casting machine is an important prerequisite for analyzing the vibration transmission path of the roller centrifugal casting machine.

[0081] Specific location of vibration source:

[0082] Motor unit: As a driving device, the running state of the motor unit directly affects the vibration of the centrifugal roller casting machine. Unbalanced operation of the motor, bearing damage or looseness, etc. may become vibration sources.

[0083] Transmission unit: The transmission unit includes gears, bearings, couplings and other components. When these components transmit power, if there are problems such as design defects, manufacturing errors or wear, they may cause vibration.

[0084] Rollers and bearings: Rollers and bearings are key components of the roller centrifugal casting machine. Their contact state, lubrication conditions and wear degree will affect the vibration.

[0085] Centrifugal casting unit: When the centrifugal casting machine is working, the eccentric retention of molten steel in the inner cavity of the casting mold will generate centrifugal force. This centrifugal force is an exciting force that may cause the equipment to resonate and thus produce abnormal vibration.

[0086] Type of vibration generated:

[0087] Torsional vibration: It mainly occurs in the transmission system of the roller centrifugal casting machine. Since the shaft system is not an absolute rigid body and has a certain degree of elasticity, different components produce instantaneous speeds of different sizes and phases during rotation, thus generating torsional vibration.

[0088] Horizontal vibration: During the roll changing or operation of the centrifugal roller casting machine, there is a certain horizontal offset between the centers of the working rolls and the support rolls, and a sufficient gap distance must be ensured between the frame and the roll system, all of which may lead to horizontal vibration.

[0089] Vertical vibration: Vertical vibration may be caused by factors such as uneven size of the rolled product, rough surface of the rolls or excessively high billet flow rate.

[0090] Electromagnetic vibration: In the roller centrifugal casting machine, the action of the electromagnetic field may also lead to the generation of electromagnetic vibration, which is generally generated by electromagnetic casting force.

[0091] Therefore, the vibration sources in the roller centrifugal casting machine may be located in the motor, transmission system, rollers and bearings, and centrifugal casting system, and may generate various types of vibrations such as torsional vibration, horizontal vibration, vertical vibration, and electromagnetic vibration.

[0092] The vibration signal intensity is collected at the specific location of the vibration source of the roller centrifugal casting machine using an acceleration sensor. The sensor should be placed at a location that can reflect the vibration characteristics of the vibration source to ensure the validity of the vibration signal.

[0093] A position close to the vibration source is selected as the transfer point, where the most direct input of the vibration signal can usually be detected.

[0094] Determine the target point and reference point, that is, the target position to be measured and the position where the vibration impact needs to be monitored or evaluated; the selection of the reference point should take into account the selection of the transfer point. Preferably, a point far away from the vibration source and relatively stable is selected as the reference point to better process the vibration signal.

[0095] The collected vibration signal needs to be preprocessed, including noise reduction (such as using digital filters to remove unnecessary noise) and signal smoothing (reducing random fluctuations). The purpose is to remove the interference components in the signal and retain the real vibration characteristics, such as Figure 3 shown.

[0096] Based on the preprocessed signal, the transfer function between the transfer point and the reference point and the target point is calculated. The transfer function reflects the frequency response characteristics between the system output and input, and can be used to analyze how the vibration is transmitted from the transfer point to the target point.

[0097] In vibration source identification, it is necessary to calculate the excitation force at the vibration source, and this embodiment adopts an inverse matrix method to solve it.

[0098] Given the transfer function H(ω) between the vibration source and the target point and the response function S(ω) of the target point, the excitation force L(ω) can be calculated according to the following formula:

[0099]

[0100] in, is the amplitude at the target point, and ω is the vibration frequency.

[0101] The physical meaning of this formula is that if the transfer characteristic H(ω) of the system to a certain frequency component and the response function S(ω) of the frequency component at the target point of the system are known, then the original excitation force L(ω) that causes this response can be calculated by the above formula. is the vibration amplitude at the target point.

[0102] The transfer function H(ω) can be obtained through experiments or theoretical analysis. In the experiment, a known excitation signal can be applied to the vibration system, the response of the vibration system can be measured, and then H(ω) can be obtained through Fourier transform. The frequency response function S(ω) can be obtained by measuring the response signal of the system at a certain target point and then performing Fourier transform.

[0103] In order to avoid the problem of ill-conditioned equations in the calculation process, it is preferred to set the number of reference points to at least twice the number of transfer points. This can increase the redundancy of the system and make the solution more robust.

[0104] Through the above steps, the vibration source in the roller centrifugal casting machine can be effectively identified, and the basis for the subsequent vibration transmission analysis can be provided. This method is widely used in the field of vibration state monitoring and vibration fault diagnosis of mechanical equipment.

[0105] In one embodiment, a computer device is further provided, including a memory and a processor, wherein a computer program is stored in the memory, and the processor implements the steps in the above method embodiments when executing the computer program.

[0106] In one embodiment, a computer-readable storage medium is provided, storing a computer program, which implements the steps in the above method embodiments when executed by a processor.

[0107] In one embodiment, a computer program product or computer program is provided, the computer program product or computer program includes computer instructions, the computer instructions are stored in a computer-readable storage medium. A processor of a computer device reads the computer instructions from the computer-readable storage medium, and the processor executes the computer instructions, so that the computer device performs the steps in the above-mentioned method embodiments.

[0108] Those skilled in the art can understand that all or part of the processes in the above-mentioned embodiment methods can be completed by instructing the relevant hardware through a computer program, and the computer program can be stored in a non-volatile computer-readable storage medium. When the computer program is executed, it can include the processes of the embodiments of the above-mentioned methods. Among them, any reference to the memory, database or other medium used in the embodiments provided in the present application can include at least one of non-volatile and volatile memory. Non-volatile memory can include read-only memory (ROM), magnetic tape, floppy disk, flash memory, optical memory, high-density embedded non-volatile memory, resistive random access memory (ReRAM), magnetoresistive random access memory (MRAM), ferroelectric random access memory (FRAM), phase change memory (PCM), graphene memory, etc. Volatile memory can include random access memory (RAM) or external cache memory, etc. As an illustration and not limitation, RAM can be in various forms, such as static random access memory (SRAM) or dynamic random access memory (DRAM). The database involved in each embodiment provided in this application may include at least one of a relational database and a non-relational database. Non-relational databases may include distributed databases based on blockchains, etc., but are not limited to this. The processor involved in each embodiment provided in this application may be a general-purpose processor, a central processing unit, a graphics processor, a digital signal processor, a programmable logic device, a data processing logic device based on quantum computing, etc., but are not limited to this.

[0109] The technical features of the above embodiments may be combined arbitrarily. To make the description concise, not all possible combinations of the technical features in the above embodiments are described. However, as long as there is no contradiction in the combination of these technical features, they should be considered to be within the scope of this specification.

[0110] The above-described embodiments only express several implementation methods of the present application, and the descriptions thereof are relatively specific and detailed, but they cannot be understood as limiting the scope of the present application. It should be pointed out that, for a person of ordinary skill in the art, several variations and improvements can be made without departing from the concept of the present application, and these all belong to the protection scope of the present application. Therefore, the protection scope of the present application shall be subject to the attached claims.

Claims

1. A vibration transmission path analysis method for a roller centrifugal casting machine, characterized in that: The steps include: Step 1: Establish a three-dimensional geometric model of the roller centrifugal casting machine, use the finite element method to analyze multiple component units, and obtain the mass matrix and stiffness matrix of the multiple component units; Step 2: Perform modal analysis based on the mass matrix and stiffness matrix of each component unit to determine the maximum deformation point of each component unit; Step 3: When the deformation variable of the maximum deformation point of each component unit is linearly distributed, the vibration transfer weight passing through each maximum deformation point in the vibration system is calculated to determine the component unit with the largest vibration transfer weight; Step 4: When the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, calculate the path vibration weight of the transmission path composed of multiple maximum deformation points in the vibration system, and determine the vibration source component unit of the transmission path with the largest path vibration weight.

2. The vibration transmission path analysis method according to claim 1, characterized in that: In the step 2, the position coordinates of the grid points on the grid of the component unit are assumed to be (x, y), and the modal analysis is implemented by solving the following characteristic equation: Among them, M T is the mass matrix, K T is the stiffness matrix, C T is the damping matrix, ω i is the ith grid point eigenfrequency of the component unit, is the vibration mode vector of the corresponding ith grid point, and solving the eigenvalue equation gives a series of characteristic frequencies ω of the grid points. i and the corresponding vibration mode vector 3. The vibration transmission path analysis method according to claim 2, characterized in that: After the vibration type is obtained, the deformation of the component unit under each vibration mode vector is analyzed, and the position with the largest deformation amplitude in the component unit is determined, which is the maximum deformation point of the component unit.

4. The vibration transmission path analysis method according to claim 1, characterized in that: In step three, when analyzing vibration transfer, when the deformation variable of the maximum deformation point of each component unit is linearly distributed, the vibration transfer weight passing through each maximum deformation point in the vibration system is comprehensively calculated using the transfer function and the vibration signal intensity data.

5. The vibration transmission path analysis method according to claim 4, characterized in that: The vibration transmission weight C of the maximum deformation point of the jth component element to the target point j Expressed as: C j =H j (oh j )F j (oh j ) The synthesized vibration transfer weight P: P=S j C j =S j H j (oh j )F j (oh j ); Among them, H j (ω j ) is the transfer function of the maximum deformation point of the jth component unit to the target point, F j (ω j ) is the vibration signal intensity of the maximum deformation point of the jth component unit, ω j is the characteristic frequency of the maximum deformation point of the jth component unit.

6. The vibration transmission path analysis method according to claim 1, characterized in that: In the fourth step, when the deformation variable of the maximum deformation point of each component unit is nonlinearly distributed, it is assumed that there are M vibration source signals in the vibration system, and the mth vibration source signal is x m (m=1,2,…,M), there are N response paths, and the nth response path is r n (n=1,2,…,N); then the total response R at the vibration frequency is: R = ZX; Where, R = [r1, r2, ..., r n ,…,r N ] T , the vibration source signal matrix X is [x1, x2,…, x m ,…,x M ] T ; Z is the N×M transmissibility matrix, and the constituent elements of the transmissibility matrix are Z nm is the transfer function from the mth vibration source input to the nth response path, then the vibration transfer weight of the mnth transfer path is expressed as C nm : C nm =Z nm x m 。 7. The vibration transmission path analysis method according to claim 6, characterized in that: Given the transfer function H(ω) between the vibration source and the target point and the response function S(ω) of the target point, the excitation force L(ω) is calculated according to the following formula: in, is the vibration amplitude at the target point, and ω is the vibration frequency.

8. The vibration transmission path analysis method according to claim 1, characterized in that: In the step 1, the design drawings, material properties, and geometric dimension information of the roller centrifugal casting machine are collected; the boundary conditions used in the simulation are clarified, and a three-dimensional geometric model of the roller centrifugal casting machine is created using modeling software; Through discretization, the centrifugal roller casting machine is decomposed into multiple component units.

9. The vibration transfer path analysis method according to claim 6, characterized in that: The mesh is divided according to the geometric characteristics of each component unit, and the mass matrix M of each component unit is calculated using the finite element method. T , stiffness matrix K T And the damping matrix C T .

10. The vibration transmission path analysis method according to claim 1, characterized in that: In the step 1, the multiple component units include: a motor unit, a transmission unit, rollers and bearings, and a centrifugal casting unit.

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