JP2006266825A - Determination method on vibration mode of structure and computer program for determining vibration mode of structure - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To surely determine a marked specific vibration mode from among various vibration modes with respect to an axisymmetrical structure. <P>SOLUTION: Multiple roots of a specific marked vibration mode are set on a tire which is an axisymmetrical structure, the vibration mode being marked in evaluating the characteristic frequency thereof (step S201). Then, mode correlation coefficients are calculated between a characteristic vector of a determination object vibration mode on which it is determined whether the object vibration mode is the same vibration mode as the marked vibration mode, and characteristic vectors possessed by the respective multiple roots (step S202). The sum of mode correlation coefficients with respect to the respective multiple roots is taken as a vibration mode determination index MJ (step S203). The determination index MJ is compared with a previously determined prescribed vibration mode determination threshold C to determine whether or not the object vibration mode is the same vibration mode as the marked vibration mode based on the result of the comparison (steps S205 and S206). <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to a vibration mode analysis of a structure.

  It is known that the natural frequency of a structure affects various characteristics. The natural frequency in a specific vibration mode is used as an index for various characteristics of the structure, and the structure is designed and evaluated. The natural frequency of the vibration mode is obtained by conducting an excitation experiment on an actual structure or predicting it by a finite element method (FEM) or other numerical analysis. In addition, the method for obtaining the natural frequency of the vibration mode by numerical analysis can be used for a method such as optimization analysis in which a target is set for the natural frequency in a specific vibration mode to obtain an optimal design plan. .

  In order to obtain the natural frequency in a specific vibration mode, since there are an infinite number of vibration modes in an actual structure, it is necessary to distinguish and take out the focused vibration mode from among them. In order to discriminate and extract the focused vibration mode from countless vibration modes, the frequency range where the vibration mode is expected to appear is specified, and obtained by vibration mode analysis by experiment, natural vibration analysis by finite element method, etc. There is a method of displaying the mode shape of vibration and judging it visually. Further, using the mode correlation coefficient and mass normalized mode orthogonality disclosed in Non-Patent Document 1, the similarity of the vibration mode shape is evaluated, and the focused vibration mode is discriminated and extracted from the result. There is also a technique.

Mode analysis handbook January 10, 2000 First edition first edition issued Corona

  However, structures that can be regarded as being substantially axially symmetric, such as tires and wheels, have the same natural frequency, and when the vibration mode is rotated by a predetermined angle around the symmetry axis, the vibration mode There are multiple roots with matching shapes. In this double root mode shape, the position of the vibration antinode or node around the axis of symmetry is undefined. As a result, the focused vibration mode may not be discriminated depending on the position of the vibration antinode or node.

  Therefore, the present invention has been made in view of the above, and in evaluating a natural frequency in a specific vibration mode of interest in an axially symmetric structure, the present invention is not limited to various vibration modes existing in the structure. It is an object of the present invention to provide a structure vibration mode discriminating method and a computer program for discriminating a vibration mode of a structure that can reliably discriminate a specific vibration mode focused on.

  In order to achieve the above-described object, a vibration mode determination method for a structure according to the present invention includes a procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axially symmetric, When the target vibration mode has multiple roots, the procedure for setting the combination of the multiple roots, the eigenvector of the discrimination target vibration mode for determining whether or not the vibration mode is the same as the target vibration mode, and each of the multiple roots The procedure for calculating the sum of mode correlation coefficients with the eigenvector and using this as a vibration mode discrimination index is compared with the vibration mode discrimination index and a predetermined predetermined vibration mode discrimination threshold, and based on the comparison result And a step of determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode.

  This method of discriminating the vibration mode of a structure is used to discriminate the vibration mode of a structure having axial symmetry such as a disk or a sphere, or a structure that can be regarded as substantially axially symmetric, such as a tire or a wheel. . And, the sum of the mode correlation coefficient between the eigenvector of the vibration mode to be discriminated in the structure after changing the structure and the constituent material, and the respective roots of the target vibration mode for evaluating the natural frequency, etc., This is used as a vibration mode discrimination index. And it is discriminate | determined by this vibration mode discrimination | determination index | indication whether the discrimination | determination object vibration mode is the same vibration mode as the attention vibration mode. As a result, when evaluating the natural frequency of a specific vibration mode of interest in an axisymmetric structure, the specific vibration of interest is selected from the various vibration modes present in the structure after the structure has been changed. The mode can be reliably identified and extracted. In addition, since the mode correlation coefficient does not require a mass matrix, it is also suitable for an experimental mode analysis in which it is difficult to set the mass matrix. Furthermore, even in the case of performing theoretical mode analysis by, for example, numerical simulation using a computer, it is not necessary to store a mass matrix, which is preferable because the calculation load is reduced. The axial symmetry as used in the present invention does not include a relatively minute shape change such as a tire tread pattern or a wheel design (hereinafter the same).

  The structural vibration mode discrimination method according to the present invention includes a procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axisymmetric, and the target vibration mode has a multiple root. In this case, the mass normalization mode of the procedure for setting the combination of the multiple roots, the eigenvector of the discrimination target vibration mode for determining whether or not the vibration mode is the same as the vibration mode of interest, and the eigenvector of each of the multiple roots The procedure for calculating the sum of squares of orthogonality and using this as a vibration mode discrimination index is compared with the vibration mode discrimination index and a predetermined vibration mode discrimination threshold set in advance, and the discrimination target is based on the comparison result. And a procedure for determining whether or not the vibration mode is the same vibration mode as the target vibration mode.

  This method of discriminating the vibration mode of a structure is used to discriminate the vibration mode of a structure having axial symmetry such as a disk or a sphere, or a structure that can be regarded as substantially axially symmetric, such as a tire or a wheel. . Then, the sum of squares of the orthogonality of the mass normalization mode between the eigenvector of the vibration mode to be discriminated in the structure after changing the structure, the constituent material, etc., and the respective heavy roots of the target vibration mode for evaluating the natural frequency etc. Is used as a vibration mode discrimination index. And it is discriminate | determined by this vibration mode discrimination | determination index | indication whether the discrimination | determination object vibration mode is the same vibration mode as the attention vibration mode. As a result, when evaluating the natural frequency of a particular vibration mode of interest in an axisymmetric structure, the particular vibration mode of interest among various vibration modes existing in the structure after the structure has been changed. Can be reliably identified and extracted. In addition, since the mass normalization mode orthogonality is theoretically established through the mass matrix and the stiffness matrix, the discrimination accuracy of the particular vibration mode of interest is improved.

  The structural vibration mode discrimination method according to the present invention includes a procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axisymmetric, and the target vibration mode has a multiple root. A mode correlation coefficient between the procedure for setting the combination of the multiple roots, the eigenvector of the vibration mode to be determined to determine whether the vibration mode is the same as the vibration mode of interest, and the eigenvector of each of the multiple roots, Or a procedure for comparing the value of the mass normalization mode orthogonality between the eigenvector of the vibration mode to be discriminated and the eigenvector of each of the multiple roots with a predetermined vibration mode discrimination threshold determined in advance, and the discrimination based on the comparison result And a procedure for determining whether or not the target vibration mode is the same vibration mode as the target vibration mode.

  This method of discriminating the vibration mode of a structure is used to discriminate the vibration mode of a structure having axial symmetry such as a disk or a sphere, or a structure that can be regarded as substantially axially symmetric, such as a tire or a wheel. . Then, the mode correlation coefficient between each eigenvector of the target vibration mode for evaluating the eigenvector and the natural frequency of the discrimination target vibration mode in the structure after changing the structure or the constituent material, or the discrimination target vibration mode The value of mass normalization mode orthogonality between the eigenvector and the eigenvector of the multiple root is compared with a predetermined predetermined vibration mode discrimination threshold. Then, based on the comparison result, it is determined whether or not the determination target vibration mode is the same vibration mode as the target vibration mode. As a result, when evaluating the natural frequency of a particular vibration mode of interest in an axisymmetric structure, the particular vibration mode of interest among various vibration modes existing in the structure after the structure has been changed. Can be reliably identified and extracted.

  The structural vibration mode discriminating method according to the present invention is characterized in that, in the structural vibration mode discriminating method, the vibration mode discrimination threshold is 0.70 or more and 0.99 or less.

  Since this structure vibration mode discriminating method has the same configuration as the structure vibration mode discriminating method, the same functions and effects as the structure vibration mode discrimination method are achieved. Furthermore, in this structure vibration mode discrimination method, the vibration mode discrimination threshold is 0.70 or more and 0.99 or less. In numerical analysis using a computer, the vibration mode of a structure whose structure or constituent material has been changed slightly changes, and the vibration mode discrimination index, mode correlation coefficient, or mass normalized mode orthogonality value contains an error. However, according to the present invention, it is possible to discriminate a specific vibration mode focused on from the various vibration modes present in the structure. Further, although an experimental error occurs in the experimental analysis, according to the present invention, the particular vibration mode of interest can be reliably determined.

  The structural vibration mode discriminating method according to the present invention is the reference body in which the target vibration mode is set when the radial order of the discrimination target vibration mode is n in the structural vibration mode discriminating method. Is characterized by having 2 × n or more vibration acquisition points around the symmetry axis.

  Since this structure vibration mode discriminating method has the same configuration as the structure vibration mode discriminating method, the same functions and effects as the structure vibration mode discrimination method are achieved. Here, in the theoretical mode analysis using a computer, a detailed analysis model is generally used. However, when the radial order of the vibration mode to be discriminated is n as in the vibration mode discrimination method of this structure, attention is paid. Nodes for extracting eigenvectors from the analysis model are set so that the vibration mode has nodes in 2 × n or more cross sections around the symmetry axis. As a result, the eigenvector of the analysis result can be reduced to the minimum scale necessary for determining the vibration mode of interest, and the vibration mode determination index, the mode correlation coefficient, or the value of the mass normalized mode orthogonality can be calculated. As a result, in numerical analysis using a computer, a CPU (Central Processing Unit), memory, and other hardware resources can be used effectively. Also in the experimental mode analysis, the calculation time for determining the vibration mode can be shortened.

  The structure vibration mode determination method according to the present invention is the vibration mode determination method of the structure, in the case where there are a plurality of vibration modes in which the mode determination index is equal to or greater than the vibration mode determination threshold, The mode of the number of multiple roots from the mode is set as a discrimination target vibration mode.

  Since this structure vibration mode discriminating method has the same configuration as the structure vibration mode discriminating method, the same functions and effects as the structure vibration mode discrimination method are achieved. Here, by reducing the eigenvector, vibration modes in which the vibration mode discrimination index is equal to or greater than the vibration mode discrimination threshold may be calculated more than the number of multiple roots. This is because the order of vibration modes that can be expressed is limited in the reduced eigenvector. For this reason, it is not possible to distinguish between the vibration mode of interest and a vibration mode having a higher order (frequency). However, as in the present invention, from the vibration mode having the lowest order, if the vibration modes corresponding to the number of multiple roots of the vibration mode of interest are determined as the vibration modes of interest, among various vibration modes existing in the structure, The particular vibration mode of interest can be determined reliably.

  The structural vibration mode discrimination method according to the present invention is characterized in that, in the structural vibration mode discrimination method, the target structure is a tire.

  Since the tire can be regarded as a substantially axisymmetric structure, according to the present invention, in evaluating the natural frequency in a specific vibration mode of interest, various tires existing in the tire after changing the structure or the like are used. From the vibration modes, it is possible to reliably determine and extract a particular vibration mode of interest.

  The following computer program for vibration mode discrimination according to the present invention includes the eigenvectors of the respective roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and the same vibration as the target vibration mode. A sum of mode correlation coefficients with the eigenvector of the discrimination target vibration mode to be discriminated whether or not the mode is determined, and using this as a vibration mode discrimination index, the vibration mode discrimination index, and a predetermined predetermined And a step of determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  The following computer program for vibration mode discrimination according to the present invention includes the eigenvectors of the respective roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and the same vibration as the target vibration mode. Calculating the sum of squares of mass normalized mode orthogonality with the eigenvector of the vibration mode to be discriminated to determine whether the mode is a mode, and using this as a vibration mode discrimination index, the vibration mode discrimination index, A procedure for comparing a predetermined vibration mode determination threshold value determined in advance and determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result. To do.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  The following computer program for vibration mode discrimination according to the present invention includes the eigenvectors of the respective roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and the same vibration as the target vibration mode. A mode correlation coefficient with the eigenvector of the discrimination target vibration mode to be discriminated whether or not it is a mode, or a value of mass normalized mode orthogonality between the eigenvector of the discrimination target vibration mode and the eigenvector of each of the multiple roots A procedure for comparing with a predetermined predetermined vibration mode determination threshold, and a procedure for determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result. Features.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  The vibration mode determination computer program according to the present invention is characterized in that the vibration mode determination threshold is 0.70 or more and 0.99 or less in the vibration mode determination computer program.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  In the computer program for vibration mode determination according to the present invention, when the radial order of the vibration mode to be determined is n in the computer program for vibration mode determination, the reference body that sets the vibration mode of interest is It is characterized by having 2 × n or more vibration acquisition points around the symmetry axis.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  In the computer program for vibration mode determination according to the present invention, when there are a plurality of vibration modes in which the mode determination index is equal to or greater than the vibration mode determination threshold in the vibration mode determination computer program, the vibration mode determination mode starts with a vibration mode having a low frequency. The mode of the number of multiple roots is set as a discrimination target vibration mode.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  The vibration mode discrimination computer program according to the present invention is characterized in that in the vibration mode discrimination computer program, the target structure is a tire.

  According to the computer program for vibration mode discrimination, the vibration mode discrimination method can be realized using a computer.

  According to the present invention, when evaluating the natural frequency in a specific vibration mode of interest in an axisymmetric structure, the specific vibration mode of interest is reliably selected from various vibration modes existing in the structure. Can be determined.

  Hereinafter, the present invention will be described in detail with reference to the drawings. The present invention is not limited to the best mode for carrying out the invention. In addition, constituent elements in the following embodiments include those that can be easily assumed by those skilled in the art or that are substantially the same. The present invention can be preferably applied to the determination of the vibration mode of the axially symmetric structure. In the following description, the tire is taken as an example of the axially symmetric structure, and the vibration mode of the structure according to the present invention is determined in the tire design. An example in which the method is applied will be described. Further, the present invention can be preferably applied to all mode analysis regardless of theoretical mode analysis by a computer or the like, or experimental mode analysis by a vibration experiment or the like.

  The vibration mode discrimination method for a structure according to this embodiment is applied to vibration mode analysis of a structure that can be regarded as being substantially axially symmetric, and has the following characteristics. That is, the vibration mode of interest to be determined is set for the reference body of the structure. Next, the sum of squares of the orthogonality of the mass normalized mode between the eigenvector of the vibration mode after the structure change of the reference body and the eigenvector of each of the multiple roots of the target vibration mode is calculated, and this is vibrated. Set as a mode discrimination index. Then, the calculated vibration mode discrimination index is compared with a predetermined threshold value, and the vibration mode after the structure change of the reference body is determined. In addition, the vibration mode discrimination | determination method of the axially symmetric structure which concerns on this Example is realizable by the simulation using a computer. Next, the vibration mode discrimination method for the structure according to this embodiment will be described.

  FIG. 1 is a flowchart showing a tire design method including a structure vibration mode discrimination method according to this embodiment. FIG. 2 is a flowchart showing the procedure of the structure vibration mode discrimination method according to this embodiment. FIGS. 3A and 3B are explanatory diagrams illustrating the axes of the tire. The Y axis shown in FIGS. 3A and 3B is an axis corresponding to the central axis of the tire 1. The X axis and the Z axis are each orthogonal to the Y axis, and the X axis and the Z axis are orthogonal to each other. Here, the Z-axis is a central axis in the direction parallel to the tire 1, that is, the width direction of the tire 1 (hereinafter referred to as the width direction central axis). FIGS. 4A and 4B are explanatory diagrams illustrating tire vibration modes. In this embodiment, an example will be described in which a tire is designed by performing a natural vibration analysis of a tire as a structure by a numerical simulation using a computer. First, the configuration of a vibration mode discriminating apparatus that executes the vibration mode discrimination method for a structure according to this embodiment will be described.

  FIG. 5 is an explanatory diagram showing a vibration mode discriminating apparatus for executing the structure vibration mode discriminating method according to this embodiment. The vibration mode discrimination method for a structure according to this embodiment can be realized by the vibration mode discrimination device 50 shown in FIG. As shown in FIG. 5, the vibration mode determination device 50 includes a processing unit 52 and a storage unit 54. Further, an input / output device 51 is connected to the vibration mode discriminating apparatus 50, and the physical property value of the rubber constituting the tire model, the physical property value of the wheel, or the boundary in the prediction calculation is provided by the input means 53 provided therein. Conditions, travel conditions, and the like are input to the processing unit 52 and the storage unit 54.

  Here, an input device such as a keyboard and a mouse can be used for the input means 53. The storage unit 54 stores a computer program including the structure vibration mode determination method according to this embodiment. Here, the storage unit 54 is a hard disk device, a magneto-optical disk device, a non-volatile memory such as a flash memory (a storage medium that can be read only such as a CD-ROM), or a RAM (Random Access Memory). Such a volatile memory or a combination thereof can be used.

  Further, the computer program may be capable of realizing the vibration mode discrimination method for a structure according to the present invention by a combination with a computer program already recorded in the computer system. Also, the computer program for realizing the function of the processing unit 52 is recorded on a computer-readable recording medium, and the program recorded on the recording medium is read into the computer system and executed, thereby executing the structure according to the present invention. An object vibration mode determination method may be executed. Here, the “computer system” includes hardware such as an OS (Operating System) and peripheral devices.

  The processing unit 52 includes a memory and a CPU. At the time of structural vibration mode determination, based on the set tire analysis model, input data, and the like, the processing unit 52 reads the program into a memory incorporated in the processing unit 52 and performs calculation. At that time, the processing unit 52 appropriately stores a numerical value in the middle of the calculation in the storage unit 54, and extracts the numerical value stored in the storage unit 54 and advances the calculation. The processing unit 52 may realize the function by dedicated hardware instead of the computer program. The prediction result is displayed on the display means 55 of the input / output device.

  Here, a CRT (Cathode Ray Tube), a liquid crystal display device or the like can be used for the display means 55. The prediction result can also be output to a printer provided as necessary. Here, the storage unit 54 may be built in the processing unit 52 or may be in another device (for example, a database server). As an example of the latter, for example, the vibration mode determination device 50 may access the processing unit 52 and the storage unit 54 by communication from a terminal device including the input / output device 51. Next, the vibration mode discrimination method for the structure according to this embodiment will be described with reference to FIGS.

  The tire 1 shown in FIGS. 3-1 and 3-2 is an axisymmetric structure. That is, the tire 1 is a structure in which the geometric arrangement of the tire 1 is not changed by rotation around the axis Y corresponding to the central axis. In the tire design method according to this embodiment, attention is paid to the natural frequency of a specific vibration mode in the tire 1 which is an axisymmetric structure to be designed, and this is used as an index for performance evaluation. For this reason, first, the tire 1 serving as a design reference is set as a reference body (hereinafter referred to as a reference tire).

  As shown in FIG. 4A, there are various vibration modes in the tire. Among these vibration modes, in order to evaluate the natural frequency of the specific vibration mode in the tire design, a specific vibration mode to be focused on (hereinafter referred to as a focused vibration mode) is set (step S101). In this embodiment, for example, as shown in FIG. 4B, attention is paid to the translational vibration mode M1 and the rotational vibration mode M2, and these are set to the focused vibration mode.

  When the vibration mode of interest is set (step S101), the design of the reference tire structure and constituent materials is changed (step S102). In this embodiment, for example, using a tire analysis model created based on a finite element method or the like, natural vibration analysis of a tire analysis model created by a numerical analysis by a computer is performed. For this reason, in the design change of step S102, the structure and the constituent material of the analysis model of the reference tire are changed, and the analysis model of the design-changed tire is created. In addition, without using numerical analysis by a computer, a prototype of a tire whose design has been changed may be actually created and used to evaluate the natural frequency of the vibration mode of interest.

  When the structure of the reference tire and the design of the constituent material are changed (step S102), the natural frequency of the target vibration mode set in step S101 is evaluated using the analysis model of the design-changed tire. At this time, the vibration mode discriminating device 50 selects the target vibration mode set in step S101 by using the vibration mode discrimination method for the structure according to this embodiment from various vibration modes existing in the analysis model of the design-changed tire. The same vibration mode is discriminated (step S103). This determination procedure will be described later.

  When the vibration mode determination device 50 determines the target vibration mode (step S103), how the natural frequency of the target vibration mode changes with respect to the natural frequency of the reference vibration mode of the reference tire, for example. Evaluate (step S104). When the evaluation result does not reach the target value (step S105: No), the design change (step S102), the vibration mode discrimination (step S103), and the evaluation (step S104) are repeated. When the evaluation result reaches the target value (step S105: Yes), the tire design is finished. Next, a method for determining the vibration mode of the structure according to this embodiment will be described.

  FIGS. 6A and 6B are conceptual diagrams illustrating examples of vibration modes of the heavy roots that the reference tire has. FIG. 6-3 is an explanatory diagram illustrating a relationship between a vibration mode of a heavy root included in the reference tire and the same vibration mode. FIG. 6-4 is an explanatory diagram illustrating a mode correlation coefficient between the vibration mode of the multiple roots of the reference tire and the same vibration mode.

  In mode analysis of an axially symmetric structure such as a tire, if the natural frequency is the same and if a predetermined angle (α in this example) is rotated around the axis of symmetry (Y axis in this example), the vibration mode There are a plurality of vibration modes having the same shape (mode shape). For example, in the translational vibration mode of the tire shown in FIGS. 6A and 6B, for example, the first vibration mode a having the same natural frequency and the direction of vibration being parallel to the X axis, and the Y axis There is a second vibration mode b in which the vibration direction is inclined by an angle α (45 degrees in this example) with respect to the X axis. The first vibration mode a and the second vibration mode b have the same vibration mode shape, and when one of them is rotated by an angle α, the vibration mode shapes coincide with each other. The first vibration mode a and the second vibration mode are referred to as the multiple roots of the vibration mode. Here, the eigenvector of the first vibration mode a is φa, and the eigenvector of the second vibration mode b is φb.

In this embodiment, the mode correlation coefficient MAC is used to determine the same vibration mode as the target vibration mode from various vibration modes existing in the design-change tire. Here, in general, the mode correlation coefficient MAC between the vibration mode r and the vibration mode s is assumed that the eigenvector of the vibration mode r is φr and the eigenvector of the vibration mode s is φs.
MAC (φr, φs) = | φr ^H φs | ² / (| φr | ² | φs | ² )
It becomes. The mode correlation coefficient varies in the range of 0-1. When the vibration mode r and the vibration mode s are completely correlated, that is, when both are completely matched, the value is 1. When there is no correlation, the value is 0.

Here, i is a vibration mode in which the first vibration mode a is rotated about the Y axis by an angle θ (FIG. 6-3). At this time, the mode correlation coefficient between the first vibration mode a and the vibration mode i is set such that the eigenvector of the first vibration mode a is φa and the eigenvector of the vibration mode i is φi.
MAC (φa, φi) = | φa ^H φi | ² / (| φa | ² | φi | ² ). The mode correlation coefficient between the second vibration mode b and the vibration mode i is expressed as follows. When the eigenvector of the second vibration mode b is φb and the eigenvector of the vibration mode i is φi,
MAC (φb, φi) = | φb ^H φi | ² / (| φb | ² | φi | ² ).

  When the vibration mode i is rotated by the angle θ shown on the horizontal axis of FIG. 6-4, MAC (φa, φi) changes as shown by the solid line in FIG. 6-4, and MAC (φb, φi) It changes like a broken line 6-4. Here, the vibration mode i is obtained by rotating the first vibration mode a around the Y axis by a predetermined angle. As described above, the first vibration mode a and the second vibration mode b have the same vibration mode shape and natural frequency, and coincide with each other when they rotate around the Y axis. Mode i is completely correlated with first vibration mode a and second vibration mode b.

  If the mode correlation coefficient is 0.8 or more, it is determined that there is a correlation between the first vibration mode a (or the second vibration mode b) and the vibration mode i, and they match. That is, when the mode correlation coefficient threshold value is 0.8 and the mode correlation coefficient is equal to or greater than the threshold value, it can be determined that the first vibration mode a and the vibration mode i have a correlation.

  Using the mode correlation coefficients MAC (φa, φi) and MAC (φb, φi), it is determined whether or not the vibration mode i matches either the first vibration mode a or the second vibration mode b. To do. In this case, in the vicinity of θ = n × 45 degrees (n = 0, 1, 2,...), One of MAC (φa, φi) and MAC (φb, φi) is 0.8 or more. Therefore, it can be determined that the vibration mode i is correlated with either the first vibration mode a or the second vibration mode b. However, in the vicinity of θ = 25.5 degrees + n × 45 degrees, the values of MAC (φa, φi) and MAC (φb, φi) are small, so that the vibration mode i is the first vibration mode a and the second vibration. There is a high risk that it is determined that there is no correlation with any of the modes b.

  Thus, in an axially symmetric structure such as a tire, when trying to determine the target vibration mode using the mode correlation coefficients MAC (φa, φi), MAC (φb, φi), the vibration mode around the Y axis Depending on the angle θ of i, the vibration mode i may not be determined as the target vibration mode. On the other hand, if the threshold value of the mode correlation coefficient is set low in order to determine the vibration mode i as the target vibration mode, the determination accuracy of the target vibration mode decreases.

  Here, when the vibration mode i is completely correlated with the first vibration mode a and the second vibration mode b, as can be seen from FIG. 6-4, the mode correlation coefficients MAC (φa, φi) and MAC (φb, The sum of φi) is 1 regardless of the rotation angle of vibration mode i. On the other hand, when the vibration mode i is not correlated with the first vibration mode a and the second vibration mode b, the mode correlation coefficients MAC (φa, φi) and MAC (φb, φi) are both 0. The sum is 0 regardless of the rotation angle of the vibration mode i.

  Therefore, in this embodiment, after changing the structure or the like of the reference tire, the eigenvector φj of the discrimination target vibration mode j for determining whether or not the vibration mode is the same as the vibration mode of interest, and the vibration of interest of the reference tire The sum of the mode correlation coefficients MAC (φa, φj) and MAC (φb, φj) with the respective multiple roots of the mode is calculated. Then, the sum of both mode correlation coefficients is set as the vibration mode discrimination index MJ, and whether the discrimination target vibration mode j after changing the structure of the reference tire by the vibration mode discrimination index MJ is the target vibration mode. Determine whether or not.

Here, the mode phase between the eigenvector φa of the first vibration mode that is one of the roots of the vibration mode of interest of the reference tire and the eigenvector φj of the tire discrimination target vibration mode j after changing the structure or the like of the reference tire. The number of relationships (first mode correlation coefficient) is
MAC (φa, φj) = | φa ^H φj | ² / (| φa | ² | φj | ² ) = | φa ^H (αφa + βφb) | ² / (| φa | ² | αφa + βφb | ² ) = α ² | φa | ² / (α ² | φa | ² + β ² | φb | ² ).
Further, the mode phase relationship between the eigenvector φa of the second vibration mode, which is the other heavy root of the vibration mode of interest of the reference tire, and the eigenvector φj of the tire discrimination target vibration mode j after changing the structure or the like of the reference tire The number (second mode correlation coefficient) is
MAC (φb, φj) = β ² | φb | ² / (α ² | φa | ² + β ² | φb | ² ). Note that φj = αφa + βφb, α ² + β ² = 1, and MAC (φa, φb) = 0.

The vibration mode discrimination index MJ is the sum ΣMAC of the first mode correlation coefficient MAC (φa, φj) and the second mode correlation coefficient MAC (φb, φj).
MJ = ΣMAC = α ² | φa | ² / (α ² | φa | ² + β ² | φb | ² ) + β ² | φb | ² / (α ² | φa | ² + β ² | φb | ² )

  For example, when MJ = 1, it is determined that the discrimination target vibration mode j after changing the structure of the reference tire has a correlation with the target vibration mode set in the reference tire. On the other hand, for example, when MJ = 0, it is determined that the discrimination target vibration mode j after changing the structure of the reference tire has no correlation with the set target vibration mode. Here, when the structure or the like of the reference tire is changed, the vibration mode may change somewhat. In such a case, an error may be included in the value of the vibration mode determination index MJ.

  Therefore, when the vibration mode determination index MJ is equal to or greater than a predetermined vibration mode determination index threshold (hereinafter referred to as a vibration mode determination threshold) C, the determination target vibration mode j after changing the structure of the reference tire is It is determined that there is a correlation with the target vibration mode set in the reference tire. The vibration mode determination threshold C is preferably set in the range of 0.70 to 0.99, and more preferably in the range of 0.80 to 0.90. Next, the procedure of the vibration mode discrimination method for the structure according to this embodiment will be described with reference to FIG.

  First, the root of the vibration mode of interest is set in the reference tire (step S201). There are two double roots in the axisymmetric structure. Further, the vibration mode discrimination method of the structure according to this embodiment can be applied to a point-symmetric structure such as a sphere that can be regarded as being substantially axially symmetric. There are three multiple roots. In the structure vibration mode discrimination method according to this embodiment, the mode correlation coefficient is calculated using the eigenvector of the multiple root. The double root is determined and set by, for example, theoretical mode analysis from the set target vibration mode. Then, the obtained eigenvectors of the respective roots are stored in the storage unit 54 of the vibration mode discriminating apparatus 50 according to this embodiment. As a result, the root of the vibration mode of interest is set.

  Next, the processing unit 52 of the vibration mode discriminating apparatus 50 according to this embodiment includes the respective roots of the target tire vibration mode of the reference tire and the eigenvector of the vibration mode (discrimination target vibration mode) that is the discrimination target of the changed tire. Mode correlation coefficient MAC is obtained (step S202). Then, the processing unit 52 calculates the sum (ΣMAC) of the obtained mode correlation coefficients MAC, and sets this as the vibration mode discrimination index MJ (step S203). Thereafter, the processing unit 52 compares the vibration mode determination index MJ with the vibration mode determination threshold C (step S204).

  When MJ ≧ C (step S204; Yes), the processing unit 52 determines that the vibration mode to be determined for the changed tire is the same vibration mode as the target vibration mode of the reference tire (step S205). When MJ <C (step S204; No), the processing unit 52 determines that the vibration mode to be determined for the changed tire is a vibration mode different from the target vibration mode of the reference tire (step S206). According to the above procedure, the target vibration mode can be determined in the changed tire.

  The vibration mode discrimination index MJ used in this embodiment is the sum of the first mode correlation coefficient and the second mode correlation coefficient. Here, since the mode correlation coefficient does not require a mass matrix, it is also suitable for an experimental mode analysis in which it is difficult to set the mass matrix. In addition, for example, even in the case of performing theoretical mode analysis by numerical simulation using a computer, it is not necessary to store a mass matrix, so that the calculation load is reduced. This makes it possible to effectively use hardware resources.

  Next, a description will be given of a vibration acquisition location where vibration is acquired from the reference tire when determining whether or not the vibration mode is the same as the vibration mode of interest. FIG. 7A is an explanatory diagram of an example of a tire analysis model. FIG. 7-2 is an explanatory diagram of an example of a vibration mode discrimination model, that is, a vibration acquisition location. 7-3 and 7-4 are explanatory diagrams illustrating an example of a tire vibration mode. For example, in theoretical mode analysis by a computer or the like, analysis of a reference body of an axisymmetric structure created based on an analysis method such as a finite element method (FEM) or a boundary element method (BEM) Model 1M (FIG. 7-1) is used. Then, when the vibration mode is determined by the vibration mode determination method for the structure according to this embodiment, the eigenvector composed of the component at the node No. of the vibration mode determination model 1Mo obtained by thinning the nodes from the analysis model 1M is used. Calculate vibration mode discrimination index. That is, the node No. used for discrimination of the vibration mode can be considered as a vibration acquisition location in the actual structure (tire in this embodiment). In FIG. 7B, a diamond symbol (No) is a node, that is, a vibration acquisition location.

  The detailed analysis model 1M is used in the theoretical mode analysis using a computer. When the vibration mode is determined by the vibration mode determination method for the structure according to this embodiment, the minimum scale necessary for the determination is used. The vibration mode discrimination index MJ may be calculated by reducing the eigenvector. More specifically, when the radial direction of the discrimination target vibration mode in a structure (changed tire in this embodiment) having a changed structure or the like is n, a structure (in this embodiment) in which a focused vibration mode having a multiple root is set. In the example, the tire) may be set to have nodes (that is, vibration acquisition locations) in 2 × n or more cross sections around the symmetry axis (Y axis). That is, it is not necessary to use all the nodes when determining the vibration mode.

  For example, when the radial order of the discrimination target vibration mode in the changed tire whose structure or the like is changed is n, among the nodal points existing in the outer peripheral portion 1Mo of the analysis model 1M of the structure in which the target vibration mode having a multiple root is set It is sufficient that there are 2 × n nodes around the symmetry axis (Y axis). That is, even when there are more than 2 × n nodes No. in the outer peripheral portion 1Mo of the analysis model 1M, at least 2 × n nodes may be used when determining the vibration mode. As a result, it is not necessary to use all the nodes when determining the vibration mode, so the calculation time for determining the vibration mode can be shortened, and a detailed analysis model can be used for natural vibration analysis etc. Therefore, it is possible to realize a highly accurate analysis.

  Also, when the vibration mode is determined by the structure vibration mode determination method according to this embodiment, even in the experimental mode analysis, the analysis model is set to the minimum scale necessary for the determination, or the eigenvector is reduced. Thus, the vibration mode discrimination index MJ can be calculated. More specifically, when the radial direction of the discrimination target vibration mode in the structure (changed tire) having a changed structure or the like is n, the reference body (reference tire) of the structure in which the target vibration mode having a multiple root is set. May be set so as to have vibration acquisition points in 2 × n or more cross sections around the Y axis. Here, the cross section is preferably set at equiangular intervals around the symmetry axis. In the experiment mode analysis, vibration detection means such as a load cell is attached to the set vibration acquisition location, and the vibration mode of the changed tire or the reference tire is acquired. In this way, in the determination of the vibration mode, vibration acquisition locations can be reduced, so that the calculation time for determining the vibration mode can be shortened.

  For example, as shown in FIG. 7-3, when the order n of the vibration mode to be discriminated in the tire 1 is third order, the analysis model 1M (FIG. 7-1) has six or more cross sections around the Y axis. The vibration mode discrimination model 1Mo (FIG. 7-2) is set so as to have the node N. Further, as shown in FIG. 7-4, when the order n of the vibration mode to be discriminated in the tire 1 is the fourth order, the analysis model 1M (FIG. 7-1) has eight or more cross sections around the Y axis. The vibration mode discrimination model 1Mo (FIG. 7-2) is set so as to have the node N. As a result, when the vibration mode of the changed tire is determined, the vibration mode determination index MJ can be calculated by reducing the eigenvector to the minimum scale necessary for the determination, so that the calculation time can be shortened.

  In the structure vibration mode determination method according to this embodiment, there may be a case where a plurality of vibration modes in which the vibration mode determination index MJ is equal to or greater than the vibration mode determination threshold C may be calculated. In the vibration mode discrimination method for a structure according to this embodiment, there is a case where it is not possible to distinguish between the target vibration mode and a higher order (frequency) vibration mode. That is, there are cases where the vibration mode of interest cannot be determined. Therefore, when a plurality of vibration modes in which the vibration mode determination index MJ is greater than or equal to the vibration mode determination threshold C are calculated, the vibration mode of interest is selected from the vibration mode having the lowest order with respect to the vibration mode of the vibration mode determination threshold C or higher. Vibration modes corresponding to the number of multiple roots of the are determined as the vibration mode of interest.

(First modification)
FIG. 8 is a flowchart showing a vibration mode discrimination method for a structure according to a first modification of this embodiment. The first modified example has substantially the same configuration as the above example, but the eigenvector φj of the discrimination target vibration mode j after changing the structure or the like of the reference tire and the respective multiple roots of the reference vibration mode of the reference tire Are different from each other in that the mass normalization mode orthogonality is obtained and the square sum of the mass normalization mode orthogonality for each of the roots is set as the vibration mode discrimination index MJ. Since other configurations are the same as those of the above-described embodiment, description of common configurations is omitted. Here, the vibration mode discriminating method for the structure according to this modification can be realized by the vibration mode discriminating apparatus 50 of the above-described embodiment.

Mass normalization mode orthogonality between the eigenvector φa of the target vibration mode of the reference tire and the eigenvector φj of the tire discrimination target vibration mode j after changing the structure or the like of the reference tire (first mass normalization mode orthogonality) Is
A (φa, φj) = φa ^H Mφj.
Further, the mass normalized mode orthogonality between the eigenvector φb of the reference vibration mode of the reference tire and the eigenvector φj of the tire discrimination target vibration mode j after changing the structure or the like of the reference tire (second mass normalized mode orthogonality) Sex)
A (φb, φj) = φb ^H Mφj. Here, M is a mass matrix.

In this modification, the vibration mode discrimination index MJ is obtained by calculating the square of the first mass normalized mode orthogonality A (φa, φj) and the square of the second mass normalized mode orthogonality A (φb, φj). Since it is sum ΣA,
MJ = ΣA = A (φa, φj) ² + A (φa, φj) ²

In executing the structure vibration mode discrimination method according to this modification, first, the root of the vibration mode of interest is set in the reference tire (step S301). Next, the processing unit 52 of the vibration mode discriminating apparatus 50 according to this embodiment uses the mass normalization mode orthogonality between the respective roots of the target tire vibration mode of the reference tire and the eigenvector of the vibration mode that is the discrimination target of the changed tire. The property A is obtained (step S302). Then, the processing unit 52 calculates the sum of squares (ΣA ² ) of the obtained mass normalization mode orthogonality A, and sets this as the vibration mode discrimination index MJ (step S303). Thereafter, the processing unit 52 compares the vibration mode determination index MJ with the vibration mode determination threshold C (step S304).

  When MJ ≧ C (step S304; Yes), the processing unit 52 determines that the vibration mode to be determined for the changed tire is the same vibration mode as the target vibration mode of the reference tire (step S305). When MJ <C (step S304; No), the processing unit 52 determines that the vibration mode to be determined for the changed tire is a vibration mode different from the target vibration mode of the reference tire (step S306). According to the above procedure, the target vibration mode can be determined in the changed tire. Since the mass normalized mode orthogonality used in this modification is established via the mass matrix and the stiffness matrix, the determination accuracy is improved as compared with the mode correlation coefficient.

(Second modification)
FIG. 9 is a flowchart showing a vibration mode discrimination method for a structure according to a second modification of this embodiment. The second modified example has substantially the same configuration as the above-described embodiment or the first modified example, but differs in the following points. That is, the mode correlation coefficient or the mass normalized mode orthogonality between the eigenvector φj of the discrimination target vibration mode j after changing the structure of the reference tire and the respective multiple roots of the target vibration mode of the reference tire is obtained. The difference is that the mode correlation coefficient or the mass normalized mode orthogonality for each multiple root is individually compared with the vibration mode discrimination threshold. Since other configurations are the same as those of the above-described embodiment or the second modified example, description of common configurations is omitted.

  Here, the vibration mode discriminating method for the structure according to this modification can be realized by the vibration mode discriminating apparatus 50 of the above-described embodiment. In the following, an example in which the mode correlation coefficient is used as an index for determining the vibration mode will be described. However, the same applies when the mass normalized mode orthogonality is used as an index.

  First, the root of the vibration mode of interest is set in the reference tire (step S401). Next, the processing unit 52 of the vibration mode discriminating apparatus 50 according to this embodiment calculates the mode correlation coefficient between the respective roots of the target vibration mode of the reference tire and the eigenvector of the vibration mode that is the discrimination target of the changed tire. Obtained (step S402). Then, the processing unit 52 compares the first mode correlation coefficient MAC_a and the vibration mode determination threshold C among the obtained mode correlation coefficients (step S403).

  When MAC_a ≧ C (step S403; Yes), the processing unit 52 determines that the vibration mode to be determined for the changed tire is the same vibration mode as the target tire vibration mode of the reference tire (step S405). When MAC_a <C (step S403; No), the processing unit 52 compares the second mode correlation coefficient MAC_b with the vibration mode determination threshold C among the obtained mode correlation coefficients (step S404).

  When MAC_b ≧ C (step S404; Yes), the processing unit 52 determines that the vibration mode to be determined for the changed tire is the same vibration mode as the target tire vibration mode of the reference tire (step S405). When MAC_b <C is satisfied (step S404; No), the processing unit 52 determines that the vibration mode to be determined for the changed tire is a vibration mode different from the target vibration mode of the reference tire (step S406). According to the above procedure, the target vibration mode can be determined in the changed tire.

  As described above, the vibration mode discriminating method of the structure according to this embodiment and the modification thereof is applied to each of the multiple roots of the vibration mode focused on in the evaluation and design of the structure, and the structure in which the structure, the constituent material, etc. are changed. The vibration mode is discriminated using the mode correlation coefficient or the mass normalized orthogonality with the vibration mode to be discriminated whether or not it is the vibration mode of interest. As a result, when evaluating the vibration of an axially symmetric structure or a structure that can be regarded as being substantially axially symmetric, such as a sphere, it is possible to reliably select the vibration mode of interest from the various vibration modes that exist in the structure. Can be determined. In particular, in numerical analysis using a computer, the focused vibration mode can be reliably determined, so that errors can be greatly reduced. In addition, since it is not necessary to fix the position of the antinode or node of the vibration mode using a model that takes into account symmetry (for example, a 1/2 model), other vibration modes that are necessary in addition to the vibration mode of interest are also calculated. be able to.

  As described above, the structural vibration mode discriminating method and the structural vibration mode discriminating computer program according to the present invention are used to evaluate the natural frequency in a specific vibration mode of interest in an axisymmetric structure. This is useful, and is particularly suitable for reliably determining a specific vibration mode of interest.

It is a flowchart which shows the design method of the tire containing the vibration mode discrimination | determination method of the structure based on this Example. It is a flowchart which shows the procedure of the vibration mode discrimination | determination method of the structure based on this Example. It is explanatory drawing which shows each axis | shaft of a tire. It is explanatory drawing which shows each axis | shaft of a tire. It is explanatory drawing which shows the vibration mode of a tire. It is explanatory drawing which shows the vibration mode of a tire. It is explanatory drawing which shows the vibration mode discrimination | determination apparatus which performs the vibration mode discrimination method of the structure based on this Example. It is a conceptual diagram which shows the vibration mode example of the heavy root which a reference | standard tire has. It is a conceptual diagram which shows the vibration mode example of the heavy root which a reference | standard tire has. It is explanatory drawing which shows the relationship between the vibration mode of the heavy root which a reference | standard tire has, and the vibration mode same as this. It is explanatory drawing which shows the mode correlation coefficient of the vibration mode of the heavy root which a reference | standard tire has, and the vibration mode same as this. It is explanatory drawing which shows an example of the analysis model of a tire. It is explanatory drawing which shows an example of the model for vibration mode discrimination | determination, ie, a vibration acquisition location. It is explanatory drawing which shows an example of the vibration mode of a tire. It is explanatory drawing which shows an example of the vibration mode of a tire. It is a flowchart which shows the vibration mode discrimination method of the structure which concerns on the 1st modification of this Example. It is a flowchart which shows the vibration mode discrimination method of the structure which concerns on the 2nd modification of this Example.

Explanation of symbols

DESCRIPTION OF SYMBOLS 1 Tire 1Mo Outer peripheral part 1M Analytical model 50 Vibration mode discrimination apparatus A Mass normalization mode orthogonality a 1st vibration mode b 2nd vibration mode C Vibration mode discrimination threshold j Discrimination object vibration mode MAC mode correlation coefficient MAC_a 1st mode phase Number of relations MAC_b Second mode correlation coefficient MJ Vibration mode discrimination index

Claims (14)

A procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axisymmetric,
When the vibration mode of interest has multiple roots, a procedure for setting the combination of the multiple roots;
The sum of the mode correlation coefficient between the eigenvector of the discrimination target vibration mode for determining whether or not the vibration mode is the same as the vibration mode of interest and the eigenvector of each of the multiple roots is calculated, and this is used as a vibration mode discrimination index. And the procedure
Comparing the vibration mode determination index with a predetermined vibration mode determination threshold value determined in advance, and determining whether the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result; ,
A method for discriminating a vibration mode of a structure, comprising: A procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axisymmetric,
When the vibration mode of interest has multiple roots, a procedure for setting the combination of the multiple roots;
The sum of squares of mass normalized mode orthogonality between the eigenvector of the discrimination target vibration mode for determining whether or not the vibration mode is the same as the vibration mode of interest and the eigenvector of each of the multiple roots is calculated. A procedure for determining vibration mode discrimination index;
Comparing the vibration mode determination index with a predetermined vibration mode determination threshold value determined in advance, and determining whether the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result; ,
A method for discriminating a vibration mode of a structure, comprising: A procedure for setting a target vibration mode to be evaluated with respect to a reference body of a structure that can be regarded as substantially axisymmetric,
When the vibration mode of interest has multiple roots, a procedure for setting the combination of the multiple roots;
It is determined whether or not the vibration mode is the same vibration mode as the target vibration mode. The mode correlation coefficient between the eigenvector of the discrimination target vibration mode and the eigenvector of each of the multiple roots, or the eigenvector of the discrimination target vibration mode. A procedure for comparing the value of the mass normalization mode orthogonality with the eigenvector possessed by the multiple roots with a predetermined predetermined vibration mode discrimination threshold;
A procedure for determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result;
A method for discriminating a vibration mode of a structure, comprising:   The vibration mode determination method for a structure according to any one of claims 1 to 3, wherein the vibration mode determination threshold value is 0.70 or more and 0.99 or less.   2. The reference body in which the target vibration mode is set has 2 × n or more vibration acquisition locations around a symmetry axis, where n is the radial order of the discrimination target vibration mode. The vibration mode discrimination | determination method of the structure of any one of -4.   6. When there are a plurality of vibration modes in which the mode discrimination index is equal to or greater than the vibration mode discrimination threshold, the number of multiple roots is selected as a discrimination target vibration mode from a vibration mode having a low frequency. The vibration mode discrimination method for a structure according to any one of the above.   The method for discriminating a vibration mode of a structure according to any one of claims 1 to 6, wherein the target structure is a tire. Eigenvectors of the respective multiple roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and a determination target vibration mode for determining whether or not the vibration mode is the same as the target vibration mode A procedure for calculating the sum of mode correlation coefficients with eigenvectors of
Comparing the vibration mode determination index with a predetermined vibration mode determination threshold value determined in advance, and determining whether the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result; ,
A computer program for discriminating a vibration mode of a structure, comprising: Eigenvectors of the respective multiple roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and a determination target vibration mode for determining whether or not the vibration mode is the same as the target vibration mode Calculating a sum of squares of the mass normalized mode orthogonality with the eigenvector of and using this as a vibration mode discrimination index;
Comparing the vibration mode determination index with a predetermined vibration mode determination threshold value determined in advance, and determining whether the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result; ,
A computer program for discriminating a vibration mode of a structure, comprising: Eigenvectors of the respective multiple roots of the target vibration mode set with respect to the reference body of the structure that can be regarded as substantially axisymmetric, and a determination target vibration mode for determining whether or not the vibration mode is the same as the target vibration mode A procedure for comparing a mode correlation coefficient with an eigenvector or a value of mass normalized mode orthogonality between an eigenvector of the vibration mode to be discriminated and an eigenvector of each of the multiple roots with a predetermined predetermined vibration mode discrimination threshold When,
A procedure for determining whether or not the determination target vibration mode is the same vibration mode as the target vibration mode based on the comparison result;
A computer program for discriminating a vibration mode of a structure, comprising:   The computer program for determining a vibration mode of a structure according to any one of claims 8 to 10, wherein the vibration mode determination threshold value is 0.70 or more and 0.99 or less.   9. The reference body in which the target vibration mode is set has 2 × n or more vibration acquisition locations around the symmetry axis, where n is the radial order of the discrimination target vibration mode. The computer program for vibration mode discrimination | determination of the structure of any one of -11.   13. When there are a plurality of vibration modes in which the mode determination index is equal to or greater than the vibration mode determination threshold, the number of multiple roots is selected as a determination target vibration mode from vibration modes having a low frequency. The computer program for vibration mode discrimination | determination of the structure of any one of these.   14. The computer program for determining a vibration mode of a structure according to any one of claims 8 to 13, wherein the target structure is a tire.

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