KR101555499B1 - Method and apparatus for designing rotor system to avoid resonance - Google Patents

Abstract

A method and an apparatus for designing resonance avoidance of a rotating shaft system are disclosed. The method for designing a resonance avoidance system of a rotating shaft system includes the steps of acquiring information about a natural frequency in a modeled first rotating shaft system, acquiring first strain information about a rotating shaft element included in the first rotating shaft system, Determining a rigid reinforcing rotating-shaft component that should reinforce the stiffness among the rotating-shaft components, generating a second rotating-shaft system that performs reinforcement of the first rotating-shaft system by performing rigid- Determining whether resonance is avoided with respect to the second rotary shaft system, and determining, when resonance is avoided with respect to the second rotary shaft system, that the second rotary shaft system is the finally modeled final rotary shaft system.

Description

BACKGROUND OF THE INVENTION 1. Field of the Invention [0001]

The present invention relates to a design method, and more particularly to a resonance avoidance design method and apparatus.

As the manufacturing tendency of the rotating machine is made lighter and more compact, the speed is increased and the ratio of the length to the diameter of the rotating body is decreased, so that the length of the shaft becomes longer. As a result, noise and vibration problems of rotating machines become more serious than before, and the possibility of noise pollution as well as durability of the system is increasing.

Rotating machines may include most power generating devices, such as steam turbines, gas turbines, compressors, pumps, centrifuges, engines and generators, or industrial plants using them. They change the excitation force, damping force and vibration mode according to the rotation speed, and can distinguish the vibration by the transverse vibration (bending vibration), the longitudinal vibration and the non-vibration vibration according to the vibration direction or the vibration source. Therefore, in order to solve the vibration problem of the rotating machine, it is necessary to grasp the causes of these vibrations,

Various methods for analyzing the vibration of the rotating body have been studied. The vibration state of the rotating shaft is affected by the stiffness, mass distribution, moment of inertia, unbalance and bearing characteristics of the shaft in the ideal case. In actual operation, additional factors acting on the rotor, for example, static load due to gear power transmission, excitation due to pulsation of fluid, coupling, spring and damping effect due to sealing and electromagnetic attraction, etc. This greatly affects the vibration state of the rotating body.

Since large turbine generators are connected with a plurality of rotors, they contain several natural frequencies up to the operating speed because of low torsional stiffness. Therefore, the problem of torsional vibration of the shaft system is considered important in the designing stage. Numerous researches have been carried out on the shaking vibration analysis of ships, automobiles and industrial machinery, including torsional vibration analysis of shaft turbine generators and torsional vibration analysis of propulsion shafts of ships and automobile engines.

A first object of the present invention is to provide a resonance avoidance design method of a rotary shaft system.

A second object of the present invention is to provide an apparatus for performing a resonance avoidance design method of a rotary shaft system.

According to an aspect of the present invention, there is provided a method of designing a resonance avoidance system for a rotary shaft, comprising the steps of: acquiring information about a natural frequency in a modeled first rotary shaft; Determining a rigid reinforcing rotating shaft component that should be reinforced in the stiffness of the rotating shaft component on the basis of the first strain information, determining a first stiffness information for the included stiffness reinforcing rotating shaft component, Modeling the first rotary shaft system to generate a second rotary shaft system that performs remodeling of the first rotary shaft system; determining whether resonance is avoided with respect to the second rotary shaft system; And determining the second rotary axis as the last modeled final rotary axis when the second rotary axis is avoided. Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue of the first rotational axis, the first strain information includes information on the length of the rotational axis element measured before the rotational motion of the first rotational axis, The length information of the rotation axis element deformed after the movement can be calculated by comparing. When the critical speed due to the bending mode of the rotating shaft system is included in the resonance region of the rated rotation speed, calculate the strain of each element, and the portion with the greatest strain is the portion with the weakest stiffness. can do. Wherein the step of determining whether resonance is avoided with respect to the second rotary shaft system includes obtaining second strain information on a rotary shaft element included in the second rotary shaft system and comparing the second strain information with the first strain information It may be determined whether or not the strain is improved. The information on the natural frequency includes information on an eigenvector and an eigenvalue, and the information on the natural frequency can be calculated based on a discrete equation of motion satisfying a fixed-stage boundary condition The eigenvalues may be derived based on the eigenvectors. In addition, the first strain information may be calculated based on an operational deflection shape (ODS) during operation, and the ODS may be forcibly vibrated by the external force F, And may include information on the deformed shape of the element.

In order to achieve the second object of the present invention, there is provided an apparatus for designing resonance avoidance of a rotating shaft system according to an aspect of the present invention, the apparatus including a processor, Obtains first strain information on the rotation axis component included in the first rotation axis system and determines a rigid reinforcement rotation axis component that should reinforce the stiffness among the rotation axis components on the basis of the first strain information A second rotation axis system in which the rigidity reinforcing rotation axis element is rigidly reinforced to perform remodeling of the first rotation axis system is generated and it is determined whether resonance is avoided with respect to the second rotation axis system, When the resonance is avoided with respect to the second rotary shaft system, the second rotary shaft system is determined to be the finally modeled final rotary shaft system Can. Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue of the first rotational axis, the first strain information includes information on the length of the rotational axis element measured before the rotational motion of the first rotational axis, Can be calculated by comparing length information of the rotational axis element deformed after the movement. The rigid reinforcing rotary shaft element may be a rotary shaft element having the largest strain among the rotary shaft elements whose strain is measured. The processor may be configured to obtain second strain information for a rotational axis component included in the second rotational axis and to compare the second strain information with the first strain information to determine whether the strain is improved. The information on the natural frequency includes information on an eigenvector and an eigenvalue, and the information on the natural frequency can be obtained based on a discrete equation of motion satisfying a fixed-stage boundary condition The eigenvalues may be derived based on the eigenvectors. In addition, the first strain information may be calculated based on an operational deflection shape (ODS) during operation, and the ODS may be forcibly vibrated by the external force F, And may include information on the deformed shape of the element.

As described above, by using the rotary shaft type resonance avoidance designing method and apparatus according to the embodiment of the present invention, information on the strain per element in the rotary shaft system is obtained, and the rotation axis of the element of the rotary shaft system, The elements of the system can be reinforced. By using such a method, it is possible to prevent the amplitude phenomenon from occurring due to resonance.

FIG. 1 is a flowchart showing a method of reinforcing a rotating shaft system according to an embodiment of the present invention.
2 is a conceptual diagram showing various models of rotation axes according to an embodiment of the present invention.
3 is a conceptual diagram illustrating a method of analyzing a natural frequency for a rotary shaft system according to an embodiment of the present invention.
4 is a conceptual diagram illustrating a method for determining deformation information of a rotary shaft system according to an embodiment of the present invention.
5 is a conceptual diagram illustrating a resonance avoidance designing method according to an embodiment of the present invention.
FIG. 6 is a graph showing the amount of deformation of a rotary shaft due to reinforcement according to an embodiment of the present invention.
7 is a conceptual diagram showing a rotating shaft type stiffening apparatus according to an embodiment of the present invention.

While the invention is susceptible to various modifications and alternative forms, specific embodiments thereof are shown by way of example in the drawings and will herein be described in detail. It should be understood, however, that the invention is not intended to be limited to the particular embodiments, but includes all modifications, equivalents, and alternatives falling within the spirit and scope of the invention. Like reference numerals are used for like elements in describing each drawing.

The terms first, second, etc. may be used to describe various components, but the components should not be limited by the terms. The terms are used only for the purpose of distinguishing one component from another. For example, without departing from the scope of the present invention, the first component may be referred to as a second component, and similarly, the second component may also be referred to as a first component. And / or < / RTI > includes any combination of a plurality of related listed items or any of a plurality of related listed items.

It is to be understood that when an element is referred to as being "connected" or "connected" to another element, it may be directly connected or connected to the other element, . On the other hand, when an element is referred to as being "directly connected" or "directly connected" to another element, it should be understood that there are no other elements in between.

The terminology used in this application is used only to describe a specific embodiment and is not intended to limit the invention. The singular expressions include plural expressions unless the context clearly dictates otherwise. In the present application, the terms "comprises" or "having" and the like are used to specify that there is a feature, a number, a step, an operation, an element, a component or a combination thereof described in the specification, But do not preclude the presence or addition of one or more other features, integers, steps, operations, elements, components, or combinations thereof.

Hereinafter, preferred embodiments of the present invention will be described in detail with reference to the accompanying drawings. Hereinafter, the same reference numerals will be used for the same constituent elements in the drawings, and redundant explanations for the same constituent elements will be omitted.

Shafts (or shafts) are used to transmit power in many mechanical devices, including transportation machines such as ships and automobiles. In designing the shaft, strength and stiffness as well as vibration design are important. Hereinafter, in the embodiment of the present invention, a method of adjusting a design parameter of a shaft so as to avoid resonance by grasping a natural frequency through free vibration analysis of shafting in vibration design . Various methods can be used for the modeling method for the axis analysis.

In the conventional algorithms for reducing vibration, calculation and analysis of weak stiffness parts are not performed when resonance occurs in the rotating shaft system. However, as in the embodiment of the present invention, it is possible to use a method of adjusting the design parameters of the rotary shaft system so as to avoid the resonance by grasping the natural frequency through the free vibration analysis of the rotary shaft system. By using this method, it is possible to avoid the resonance by analyzing the stiffness reinforcing position in the rotary shaft system, thereby reducing the vibration of the rotary shaft system. Hereinafter, this method will be specifically described in the embodiment of the present invention.

FIG. 1 is a flowchart showing a method of reinforcing a rotating shaft system according to an embodiment of the present invention.

Referring to FIG. 1, a rotational axis system is modeled (step S100).

The rotary axis system can be modeled in various ways. The rotational axis system can be modeled through one-dimensional modeling, two-dimensional modeling, or three-dimensional modeling. Modeling of the rotary axis system can be performed based on object modeling programs such as modeling software.

2 is a conceptual diagram showing various models of a rotary shaft according to an embodiment of the present invention.

In order to variously model the rotary shaft system, various information can be inputted. For example, variables used for modeling a rotary axis are Behavior, Materials, Rotors, Damping & Stiffness, Boundary Condition (Constraints, Ground Bearing ...), Assembly (Bearing, Joints, ...), Loads like unbalance Can be input.

For example, the behavior may include information about the attributes of the model, volume, and body type of the rotor. Materials may contain information about the material properties of the material constituting the rotary axis. The rotors may include information about the axis that performs the rotation in consideration of the direction of the rotation axis system. Damping & Stiffness can include information about the damping and stiffness of the bearing when the rotating shaft is supported by the bearing.

The natural frequency of the rotary shaft system can be analyzed (step S110).

The eigenvalues and the eigenvectors of the rotary shaft system can be extracted by analyzing the natural frequency of the rotary shaft system. Various methods can be used for extracting eigenvalues and eigenvectors of the rotating shaft system. That is, according to the embodiment of the present invention, modeling is performed on the rotary shaft system, and the rotary shaft system in which the modeling is performed is analyzed to obtain eigenvalues and eigenvectors to obtain information on the vibration of the rotary body. Information on the natural frequency of the rotary shaft system can be analyzed based on the rotary shaft modeled according to step S100. Methods for calculating such modeling, eigenvalue and eigenvector will be described later.

And deformation information on the elements of the rotating shaft system is extracted (step S120).

The rotation axis system may include a plurality of rotation axis elements, and information about the amount of deformation of each rotation axis element may be acquired for each rotation axis element. The deformation amount may be a value calculated based on the deformed length when the rotation axis is rotated based on the original length information in a state where the rotation is not performed. For example, the deformation amount may be a length (? L) of an element deformed by a vector amount calculated on the basis of the length information (L) of a specific element in a rotational axis system in which initial modeling has been performed. As another example, according to the embodiment of the present invention, deformation information of the rotating body such as deformation amount and strain can be calculated by using the virtual displacement amount by the eigenvector extracted through the natural frequency analysis of the rotating shaft system. The method of calculating the deformation information for the elements of the rotary shaft system will be described later.

* Determine the rotation axis element to reinforce the stiffness among the respective rotation axis elements (step S130).

For example, strain information for each rotational axis element can be obtained by analyzing the strain rate of each rotational axis element of the rotational axis system. For example, it is possible to detect the position of the maximum deformation element having the largest deformation among the elements of the rotating shaft system.

And performs rotation-axis-shaped reinforcement (step S140).

Based on the calculated strain, it is possible to increase the strain by performing shape reinforcement for a specific rotary axis element. That is, the shape of the rotating shaft can be modeled again so that the strain rate generated in each rotating shaft element is not large. The part with a large strain rate is a part where the stiffness is weak when resonance occurs, so that the shape of the rotating shaft system can be reinforced by reinforcing the rigidity of the part. For example, it is possible to perform a rotary shaft-like reinforcement for a rotation axis element having a maximum maximum strain value.

Whether or not to perform the rotary shaft type reinforcement based on the strain information can be determined on the basis of a specific threshold value, and the shape reinforcement can be performed on the rotation axis element only when the strain is equal to or greater than the threshold value.

It is determined whether or not resonance avoidance has occurred (step S150).

It is possible to judge whether or not the revolving shaft system, which is remodeled by reinforcing the rigidity of the rotary shaft element of the rotary shaft system, has become the resonance avoidance design. For example, it is possible to judge whether or not the resonance avoidance design for the rotary shaft system has been made by judging again whether the strain is lowered in the reinforced rotary shaft system. As to whether resonance is avoided in the rotating shaft element, a Kemble diagram which will be described later can be used. It is possible to quantitatively judge whether or not the strain of each element position is improved after reinforcing the rigidity of the weak axis of rotation. In addition, various other methods can be used to determine whether resonance avoidance has occurred.

It is possible to calculate the magnitude of the strain on the rotating shaft component in the rotating shaft system again to determine whether or not resonance avoidance has occurred. When the calculated strain is lower than a preset threshold value, it can be judged that the rotating body has become the resonance avoidance design. On the other hand, if the calculated strain rate is higher than or equal to a predetermined threshold value, it is determined that the rotary shaft system is not designed for the resonance avoidance, and then the rotor modeling for reinforcing the stiffness of the rotor element with high strain rate can be re-executed.

By using the above procedure, it is possible to find the stiffness point for the weak part in the rotary axis system, and to reinforce the rigidity of the part. Hereinafter, an embodiment of the present invention will be described with reference to a method of analyzing the natural frequency for a rotary shaft system and obtaining deformation information of the rotary shaft system. The method of analyzing the natural frequency for the rotary shaft system and obtaining the deformation information of the rotary shaft system can be implemented in hardware or software.

3 is a conceptual diagram illustrating a method of analyzing a natural frequency for a rotary shaft system according to an embodiment of the present invention.

3 is an exemplary rotary shaft system, which can reinforce the rigidity of the rotary shaft system through analysis of natural frequencies for various other rotary shaft systems.

Referring to FIG. 3, the rotary shaft system is a plan view showing the shape of a rotary shaft system having a multi-shaft system.

Since the size of the cross-section of the rotary shaft is in the order of A1 <A2 <A3, the mass and moment of inertia of each section also have different values. Therefore, when modeling the shape of a multi-axis system for vibration analysis, the unit step function is used to calculate the area, mass, and moment of inertia of each cross-section having different values in the z- The shape of the multi-axis system can be modeled.

Using the unit step function, the total cross-sectional area, mass, and moment of inertia of the rotary shaft system can be determined as shown in Equation 1 below.

&Quot; (1) &quot;

Where N is the number of segments separating the multi-stages of the rotary axis system, A is the area, m is the mass, and I is the area second order moment.

In the embodiment of the present invention, the equation of motion of the rotary axis system can be derived by the Hamilton's principle as follows.

&Quot; (2) &quot;

Here, T and U denote kinetic energy and strain energy, respectively, and the differential values of the kinetic energy and the strain energy can be calculated by Equation (3) below.

&Quot; (3) &quot;

에 관한 식은 x, y 축 2 방향의 병진 변위와 회전 변위에 관한 4개의 굽힘 진동 (bending vibration)식으로 유도되며,

와

는 각각 비틀림 진동(torsional vibration)과 축 방향 진동 (axial vibration)식으로 유도할 수 있다.Substituting Equation (3) into Equation (2), v and

Is derived from the four bending vibrations related to translational displacements and rotational displacements in the two directions of x and y axes,

Wow

Can be derived in the form of torsional vibration and axial vibration, respectively.

The bending, torsional and axial motion equations can be summarized as Equation (4) below.

&Quot; (4) &quot;

는 각각 전단 강성, 굽힘 강성, 비틀림 강성을 의미하며 b는 축 방향 운동 방정식의 질량 상수 계수를 의미한다.here

Are the shear stiffness, bending stiffness, and torsional stiffness, respectively, and b is the mass constant coefficient of the axial motion equation.

In the embodiment of the present invention, the displacement function satisfying the fixed-end condition can be selected as expressed by Equation (5) below by vibration analysis of a beam having only one fixed boundary condition.

Equation (5)

는 기하학적 경계 조건을 만족하는 시험 함수(trial functions)을 의미하며,

는 임의의 상수 계수 값(arbitrary constants)을 의미하며,

의 값을 나타낸다.Where j is the order of the longitudinal mode shape of the beam.

Denotes the trial functions satisfying the geometric boundary condition,

Quot; means arbitrary constants,

Lt; / RTI &gt;

Using the extended Galerkin method, Equation (5) can be rearranged into Equation (2), which is Hamilton's principle, to obtain Equation (6) which is a discrete equation of motion satisfying the fixed-stage boundary condition. The embodiment of the present invention can acquire information on the eigenvectors and eigenvalues of the rotary axis based on the discretized equations of motion.

&Quot; (6) &quot;

과 강성 행렬(stiffness matrix)

는 6nx6n 대칭 행렬(symmetric matrix)이고,

는 6nx1 고유 벡터(eigenvectors)이다. 위와 같은 방법으로 회전축 계의 고유 벡터가 산출되고 산출된 고유 벡터에 따라 고유 값이 결정될 수 있다.Here, the mass matrix

And a stiffness matrix

Is a 6nx6n symmetric matrix,

Is the 6nx1 eigenvectors. The eigenvector of the rotating shaft system is calculated by the above method and the eigenvalue can be determined according to the calculated eigenvector.

In this case, n denotes the axial mode degree, and the larger the value, the larger the size of the matrix. Generally, in numerical analysis, as the number of n increases, the calculated eigenvalue becomes closer to the actual value.

The eigenvector and the eigenvalue of the rotating body can be calculated by analyzing the natural frequency of the rotating body by the above method.

4 is a conceptual diagram illustrating a method for determining deformation information of a rotary shaft system according to an embodiment of the present invention.

Fig. 4 shows a method for calculating deformation information of a rotary shaft system at a specific frequency. The deformation information of the rotating shaft system can be determined based on the information about the eigenvectors of the rotating shaft system.

Referring to FIG. 4, for example, the deformation information of the rotating shaft system can be calculated based on an operational deflection shape (ODS). The deformed shape during operation may be a deformed shape of a structure or a machine when a periodical excitation force is given due to the operation of the machine or the like. The ODS includes information such as the eigenmode and natural frequency.

에서의 변형 형상은 아래의 수학식 7과 같이 표현될 수 있다. An ODS can be defined as a deformed shape at an arbitrary frequency that an observer is interested in, in which two or more points of a structure / machine are forced by an external force. Frequency of the structure / machine forcing by external force {F}

The deformed shape at the center can be expressed by Equation (7) below.

&Quot; (7) &quot;

는 각각 r번째 고유 진동수, 모드 벡터 및 모달 감쇠비를 나타내는 변수일 수 있다. here,

May be variables representing the rth natural frequency, mode vector, and modal damping ratio, respectively.

In the embodiment of the present invention, two or more measurement points are set in order to extract information about the deformed shape of the rotary axis, one of them is fixed as a reference point, and a magnetic power spectrum is calculated from the signal of each measurement point, The phase of the vector can be calculated by calculating the mutual power spectrum between the measurement point and the reference point. Based on the information on the deformed shape calculated by this method, information on the strain can be obtained on the rotating shaft system.

5 is a conceptual diagram illustrating a resonance avoidance designing method according to an embodiment of the present invention.

Fig. 5 shows a method for determining whether or not the resonance avoidance design has been performed in the rotating shaft system that has been remodeled.

Referring to FIG. 5, it is a diagram used for understanding the resonance avoidance or resonance possibility of the rotary shaft system, and shows the whirl natural frequency with respect to the rotational speed in consideration of attenuation and ductility of the system.

In the embodiment of the present invention, the relative strain of each element at the critical velocity can be calculated and used by using the unbalance response analysis. The magnitude of the vibration can be evaluated with the vibration amount of the unbalance response analysis result.

Referring to FIG. 5, the intersection of the 1X synchronous rotation speed line and the turning natural frequency line corresponds to the first critical rotation speed (first rotation axis: 18,165 rpm, second rotation axis: 11300 rpm) The first rotary axis system and the second rotary axis system can have a separation margin sufficient for the primary selection line dangerous speed and the rated speed.

By analyzing the unbalance response, it is possible to predict the amount of vibration generated in each rotary axis system.

Looking at the primary mode shape for each turning natural frequency at the rated speed, it can be predicted that the amount of vibration at the position of the lobe in the case of the first rotating shaft (upper graph in FIG. 5) is large. The primary mode shape for each turning natural frequency at the rated speed can be predicted to be large at a position where the motor and the core are connected to each other at the position of the lobe in the case of the second rotating shaft (upper graph in FIG. 5).

According to the embodiment of the present invention, when vibrations of a specific value or more are generated in the elements of the rotary shaft based on the vibration analysis of the rotary shaft system, the rigidity of the elements of the rotary shaft, can do.

The natural frequency analysis method of the rotating shaft system disclosed in FIG. 3, the method of determining the deformation information of the rotating shaft system disclosed in FIG. 4, and the resonance avoidance design method disclosed in FIG. 5 are implemented by software or hardware, , Determine the deformation information of the rotary shaft system, and use it to determine whether to avoid resonance.

FIG. 6 is a graph showing the amount of deformation of a rotary shaft due to reinforcement according to an embodiment of the present invention.

Referring to FIG. 6, there is shown a graph of information on the measured initial deformation amount before performing the stiffness reinforcement in the rotating shaft system and information on the deformation amount measured after performing the stiffness reinforcement in the rotating shaft system.

Fig. 6 shows the initial deformation amount before the stiffening reinforcement and the deformation amount after the stiffening reinforcement, which are measured in a rotary axis system divided into 15 elements.

Referring to the graph, in the rotation axis system corresponding to the elements 5 to 13, which are large in the initial deformation amount before the stiffness reinforcement measured in the rotary axis system divided into 15 elements, the elements are reinforced after the rigidity reinforcement according to the embodiment of the present invention It can be confirmed that the amount of deformation has changed to a small value.

That is, according to the embodiment of the present invention, the information about the initial deformation amount before the stiffening reinforcement is obtained by analyzing the natural frequency of the rotary shaft system, extracting the deformation amount of the elements of the rotary shaft system, can do.

Based on the obtained information, information (for example, elements 5 to 13) of the element having a large strain among the elements of the rotational axis can be acquired and rigidity reinforcement for the element can be performed. Or only the stiffness reinforcement for element 10 having the maximum strain may be preferentially performed.

It is possible to obtain information on the deformation amount after the rigid reinforcement is performed after performing the rigidity reinforcement for the element. It is possible to judge whether or not the rotary shaft system is resonant avoidance based on the information on the deformation amount after the stiffening reinforcement.

7 is a conceptual diagram showing a rotating shaft type stiffening apparatus according to an embodiment of the present invention.

7, the rotating shaft type stiffening apparatus includes a unique information extracting unit 700, a strain extracting unit 710, a stiffness enhancing unit 720, a resonance avoidance determining unit 730, and a processor 750 . The respective components of the rotating shaft type stiffening apparatus can be implemented for the operation of the rotating shaft type stiffening apparatus disclosed in Figs. 1 to 6 described above. Each constituent unit is divided into functional units for the convenience of description, and one constituent unit may be embodied as a plurality of constituent units or a plurality of constituent units may be embodied as one constituent unit.

The inherent information extracting unit 700 may be implemented to analyze the natural frequency of the rotary shaft system and extract eigenvalues and eigenvectors. In addition to the method described above with reference to FIG. 3, various methods can be used for extracting eigenvalues and eigenvectors of the rotating shaft system.

The strain extracting unit 710 may be configured such that the rotational axis includes a plurality of elements, and the deformation information about each rotational axis element can be acquired for each element. The amount of deformation and strain can be calculated by using the virtual displacement amount by the eigenvector extracted from the natural frequency analysis of the rotating shaft system.

The rigidity reinforcing portion 720 can be implemented to reinforce the rigidity of the rotary shaft with high strain based on the strain extracted from the strain extracting portion 710.

The resonance avoidance determination unit 730 may be implemented to perform additional determination as to whether or not the rotary shaft, which has performed rigidity reinforcement based on the rigidity reinforcement unit 720, avoids resonance.

The processor 750 may be implemented to control operations of the unique information extractor 700, the strain extractor 710, the stiffness enhancer 720, and the resonance avoidance determiner 730.

It will be understood by those skilled in the art that various changes in form and details may be made therein without departing from the spirit and scope of the invention as defined in the appended claims. It will be possible.

Claims (12)

In a resonance avoidance design method of a rotary shaft system,
Obtaining information on the natural frequency in the modeled first rotational axis system;
Obtaining first strain information about a rotation axis component included in the first rotation axis system;
Determining a rigid reinforcing rotating shaft element to be stiffened among the rotating shaft elements based on the first strain information;
Generating a second rotary shaft in which reinforcement of the rigid reinforcing rotary element is performed to perform remodeling of the first rotary shaft;
Determining whether resonance is avoided for the second rotary shaft; And
And determining the second rotary axis as the last modeled final rotary axis when the resonance is avoided for the second rotary axis,
Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue of the first rotary shaft,
Wherein the first strain information is calculated by comparing length information of the rotation axis element measured before the rotation motion of the first rotation axis system and length information of the rotation axis element after the rotation motion,
The rigid reinforcing rotating shaft element
Wherein the resonance avoidance design method is a rotational axis element having the largest strain among the rotational axis elements whose strain is measured.
delete delete The method of claim 1, wherein the step of determining whether resonance is avoided with respect to the second rotary shaft includes:
Obtaining a second strain information on a rotational axis component included in the second rotary shaft system and comparing the second strain information with the first strain information to determine whether the strain is improved, . The method according to claim 1,
Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue,
The information on the natural frequency is obtained based on the following equation, which is a discrete equation of motion satisfying a fixed-stage boundary condition,
&Lt; Equation &

remind

Is the frequency,

A mass matrix,

Is a 6nx6n symmetric matrix with a stiffness matrix,

Is a 6nx1 eigenvectors, where n is a natural number,
Wherein the eigenvalues are derived based on the eigenvectors. 2. The method according to claim 1,
The ODS is calculated on the basis of an operational deflection shape (ODS) during operation, and the ODS is subjected to forced oscillation by an external force F,

Wherein the information about the deformation shape of the rotating shaft element in the rotating shaft system includes information on the deformation shape of the rotating shaft element. A device for designing resonance avoidance of a rotating shaft system, the device comprising a processor,
The processor obtains information on the natural frequency in the modeled first rotational axis, acquires first strain information on the rotational axis component included in the first rotational axis, A rigidity-reinforced rotary-axis element that is to be reinforced with a medium stiffness is determined, rigidity reinforcement is performed on the rigid-reinforced rotary-shaft element to generate a second rotary-axis system in which remodeling is performed on the first rotary- To determine whether the resonance is avoided for the second rotary axis, and to determine the second rotary axis as the final modeled final rotary axis when the resonance is avoided for the second rotary axis,
Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue of the first rotary shaft,
Wherein the first strain information is calculated by comparing length information of the rotation axis element measured before the rotation motion of the first rotation axis system and length information of the rotation axis element after the rotation motion,
The rigid reinforcing rotating shaft element
Wherein the resonance avoidance designing device is a rotation axis element having the largest strain among the rotation axis elements whose strain is measured.
delete delete 8. The apparatus of claim 7,
Wherein the second strain information is obtained by obtaining second strain information on a rotational axis element included in the second rotary shaft and comparing the second strain information with the first strain information to determine whether the strain is improved, . 8. The method of claim 7,
Wherein the information on the natural frequency includes information on an eigenvector and an eigenvalue,
The information on the natural frequency is obtained based on the following equation, which is a discrete equation of motion satisfying a fixed-stage boundary condition,
&Lt; Equation &

remind

Is the frequency,

A mass matrix,

Is a 6nx6n symmetric matrix with a stiffness matrix,

Is a 6nx1 eigenvectors, where n is a natural number,
Wherein the eigenvalues are derived based on the eigenvectors. 8. The method according to claim 7,
The ODS is calculated on the basis of an operational deflection shape (ODS) during operation, and the ODS is subjected to forced oscillation by an external force F,

And the information on the deformation shape of the rotating shaft element in the rotating shaft system.

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