Anti-resonance zone control and vibration suppression method, system, equipment and medium

Abstract

The present invention provides a method, system, device, and medium for controlling and suppressing vibrations in an anti-resonance zone, relating to the field of machining technology, and specifically to a method for controlling and suppressing the anti-resonance zone of a follower ball support for mirror milling of thin-walled parts. The method comprises: a workpiece modal parameter identification step, which receives and analyzes a thin-walled workpiece vibration signal input by a user, and transmits the modal parameter information of the thin-walled part obtained after analysis to an anti-resonance zone frequency identification step; an anti-resonance zone frequency identification step, which receives the modal parameter information of the thin-walled part, calculates the frequency response curve of the thin-walled part-pneumatic support coupling system, extracts the anti-resonance zone frequency, and transmits it to a tool processing instruction generation step; and a tool processing instruction generation step, which receives the anti-resonance zone frequency, determines milling stability in combination with relevant tool information, and determines whether to output a tool processing instruction based on the milling stability. The present invention can achieve vibration suppression in the mirror milling of large thin-walled parts.

Description

Technical Field

[0001] The present invention relates to the field of machining technology, and in particular to an anti-resonance zone control and vibration suppression method for a follower ball support for mirror milling of thin-walled parts, and more particularly to an anti-resonance zone control and vibration suppression method, system, equipment and medium. Background Art

[0002] Large, thin-walled aluminum alloy components are crucial structural elements in aerospace vehicles, such as aircraft skins, rocket tank sections, and tank bottoms. These components are large in size and thin in wall thickness. To balance structural strength with the vehicle's transport capacity, their wall thickness must be strictly controlled (±0.1mm). However, during machining, the weak rigidity of these thin-walled components can easily lead to significant deformation and severe vibration, making it impossible to guarantee the wall thickness. Efficient and precise thinning of large, thin-walled components has long been an internationally recognized manufacturing challenge.

[0003] Mirror milling, a new generation of green machining technology, is the latest development trend for large, thin-walled, curved parts. During mirror milling, the milling mechanism and support mechanism move symmetrically along the workpiece, relying on follower supports to improve the local dynamic characteristics of the thin-walled part's machining area. How to combine the dynamic characteristics of thin-walled parts with auxiliary supports to reduce vibration during machining is a key issue in achieving efficient and stable mirror milling of large, thin-walled parts. The dynamic characteristics of the pneumatic support coupling system for thin-walled parts exhibit anti-resonance regions, which, from a machining dynamics perspective, demonstrate insensitivity to related simple harmonic excitations. This has important applications in milling vibration suppression. Accurately understanding the formation mechanism of this anti-resonance region is crucial for fully realizing the performance of pneumatic supports. However, due to the complex interaction between thin-walled parts and support mechanisms, existing research on pneumatic supports is primarily experimental, relying on in-process vibration signals and post-machined surface quality to reflect the vibration suppression effect, and failing to explore the coupling mechanism between thin-walled parts and pneumatic supports. Existing research has limited understanding of the coupling mechanism of pneumatic supports for thin-walled parts, significantly hindering the full realization of the support performance of pneumatic supports.

[0004] The invention patent with publication number CN110153781B discloses a vibration suppression device and method for thin-walled workpiece processing based on a bending actuator, including a vibration detection unit, a signal acquisition unit, a power amplification unit, a control computer, a programmable signal generator, and a bending actuator; the bending actuator is used to apply a reverse vibration suppression force to the thin-walled workpiece and actively control the regenerative chatter during the milling process. Summary of the Invention

[0005] In view of the deficiencies in the prior art, the present invention provides a method, system, device and medium for regulating and suppressing vibration in an anti-resonance region.

[0006] According to the present invention, a method, system, device and medium for regulating and suppressing vibration in an anti-resonance region are provided, and the scheme is as follows:

[0007] In a first aspect, a method for regulating and suppressing vibration in an anti-resonance region is provided, the method comprising:

[0008] Workpiece modal parameter identification step: receiving and analyzing the thin-walled workpiece vibration signal input by the user, and sending the modal parameter information of the thin-walled workpiece obtained after analysis to the anti-resonance region frequency identification step;

[0009] Anti-resonance region frequency identification step: receiving modal parameter information of the thin-walled part, calculating a frequency response curve of the thin-walled part-pneumatic support coupling system, extracting the anti-resonance region frequency and sending it to the tool processing instruction generation step;

[0010] The tool processing instruction generating step includes receiving the anti-resonance zone frequency, determining the milling stability in combination with relevant tool information, and determining whether to output the tool processing instruction according to the milling stability.

[0011] Preferably, the anti-resonance zone frequency identification step specifically includes: receiving modal parameter information of the thin-walled workpiece, solving the frequency response curve of the thin-walled workpiece-pneumatic support coupling system based on the modal parameter information of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database, and the contact stiffness parameters of the two, extracting the anti-resonance zone frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the frequency response curve, and then sending the anti-resonance zone frequency to the tool processing instruction generation step.

[0012] Preferably, solving the frequency response curve of the thin-walled component-pneumatic support coupling system includes:

[0013] The overall pneumatic support device is regarded as substructure B, the thin-walled component is regarded as substructure A, and the thin-walled component pneumatic support coupling system is regarded as a combination C of the two after flexible connection. Point 1 is the coupling point, point 1a is the center of the thin-walled component, and point 1b is the equivalent action point of the support device. The two points are coupled together through a flexible connection. The frequency response of the thin-walled component pneumatic support combination is obtained by calculating the substructure frequency response. The specific process is as follows:

[0014] Assume external force Acting on point 1a of the thin-walled part in the assembly, since the action point is at the connection point, the load balance condition satisfies formula (1):

[0015]

[0016] in, represents the external force on substructure A at 1a; represents the external force on substructure B at 1b; according to the viscous damping model, the degree of freedom coordination conditions of the flexible connection satisfy equations (2) and (3), where the contact stiffness coefficient is: K c =k c +icc ω,

[0017]

[0018]

[0019] Among them, K c represents the stiffness coefficient; k c represents the contact stiffness; c c represents contact damping; represents the displacement of point 1a in the assembly C; represents the displacement of point 1a in substructure A; represents the displacement of point 1b in the assembly C; represents the displacement of point 1b in substructure B; Substitute equation (3) into equation (2), and then according to the definition of transfer function ( and ), formula (2) Written in the form of formula (4):

[0020]

[0021] Substituting formula (4) into formula (1), we get and The relationship equation (5):

[0022]

[0023] Sequentially transform formula (3), Substitute the transfer function into equation (5) In the definition of It is expressed as formula (6):

[0024]

[0025] According to formula (6), the frequency response of the thin-walled pneumatic support assembly is Through the frequency response of the thin-walled part itself Pneumatic support frequency response and the connection stiffness K c The pneumatic support frequency response can be obtained by the design parameters of the support device, which satisfies the form of formula (7):

[0026]

[0027] in, represents the equivalent modal mass; represents the equivalent viscous damping; represents the equivalent modal stiffness.

[0028] Preferably, the tool processing instruction generating step specifically includes: receiving anti-resonance zone frequency information of the thin-walled workpiece-pneumatic support coupling system, determining a tool pass frequency matching the anti-resonance zone frequency, and determining a tool rotation speed in combination with relevant tool information including the number of tool teeth specified by the user, and then determining the milling stability of the spindle tool under different tool overhang lengths in the database under specified processing conditions for the tool length specified by the user;

[0029] If the milling is stable, a processing instruction containing tool information and speed information is output; otherwise, an instruction is output to remind the user to change the tool overhang length, number of teeth, or change the support ball material to meet the milling stability requirements.

[0030] In a second aspect, an anti-resonance region control and vibration suppression system is provided, the system comprising:

[0031] Workpiece modal parameter identification module: receives and analyzes the thin-walled workpiece vibration signal input by the user, and sends the modal parameter information of the thin-walled workpiece obtained after analysis to the anti-resonance region frequency identification module;

[0032] Anti-resonance region frequency identification module: receives the modal parameter information of the thin-walled part, calculates the frequency response curve of the thin-walled part-pneumatic support coupling system, extracts the anti-resonance region frequency and sends it to the tool processing instruction generation module;

[0033] Tool processing instruction generation module: receives the anti-resonance zone frequency, determines the milling stability in combination with relevant tool information, and determines whether to output the tool processing instruction according to the milling stability.

[0034] Preferably, the anti-resonance zone frequency identification module specifically includes: receiving modal parameter information of the thin-walled workpiece, solving the frequency response curve of the thin-walled workpiece-pneumatic support coupling system based on the modal parameter information of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database and the contact stiffness parameters of the two, extracting the anti-resonance zone frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the frequency response curve, and then sending the anti-resonance zone frequency to the tool processing instruction generation module.

[0035] Preferably, solving the frequency response curve of the thin-walled component-pneumatic support coupling system includes:

[0036] The overall pneumatic support device is regarded as substructure B, the thin-walled component is regarded as substructure A, and the thin-walled component pneumatic support coupling system is regarded as a combination C of the two after flexible connection. Point 1 is the coupling point, point 1a is the center of the thin-walled component, and point 1b is the equivalent action point of the support device. The two points are coupled together through a flexible connection. The frequency response of the thin-walled component pneumatic support combination is obtained by calculating the substructure frequency response. The specific process is as follows:

[0037] Assume external force Acting on point 1a of the thin-walled part in the assembly, since the action point is at the connection point, the load balance condition satisfies formula (1):

[0038]

[0039] in, represents the external force on substructure A at 1a; represents the external force on substructure B at 1b; according to the viscous damping model, the degree of freedom coordination conditions of the flexible connection satisfy equations (2) and (3), where the contact stiffness coefficient is: K c =k c +ic c ω,

[0040]

[0041]

[0042] Among them, K c represents the stiffness coefficient; k c represents the contact stiffness; c c represents contact damping; represents the displacement of point 1a in the assembly C; represents the displacement of point 1a in substructure A; represents the displacement of point 1b in the assembly C; represents the displacement of point 1b in substructure B; Substitute equation (3) into equation (2), and then according to the definition of transfer function ( and ), formula (2) Written in the form of formula (4):

[0043]

[0044] Substituting formula (4) into formula (1), we get and The relationship equation (5):

[0045]

[0046] Sequentially transform formula (3), Substitute the transfer function into equation (5) In the definition of It is expressed as formula (6):

[0047]

[0048] According to formula (6), the frequency response of the thin-walled pneumatic support assembly is Through the frequency response of the thin-walled part itself Pneumatic support frequency response and the connection stiffness K c The pneumatic support frequency response can be obtained by the design parameters of the support device, which satisfies the form of formula (7):

[0049]

[0050] in, represents the equivalent modal mass; represents the equivalent viscous damping; represents the equivalent modal stiffness.

[0051] Preferably, the tool processing instruction generation module specifically includes: receiving anti-resonance zone frequency information of the thin-walled workpiece-pneumatic support coupling system, determining a tool pass frequency matching the anti-resonance zone frequency, and determining a tool rotation speed in combination with relevant tool information including the number of tool teeth specified by the user, and then determining the milling stability of the spindle tool under different tool overhang lengths in the database under specified processing conditions.

[0052] If the milling is stable, a processing instruction containing tool information and speed information is output; otherwise, an instruction is output to remind the user to change the tool overhang length, number of teeth, or change the support ball material to meet the milling stability requirements.

[0053] According to a third aspect, a device is provided, comprising:

[0054] one or more processors;

[0055] a storage device for storing one or more programs,

[0056] When the one or more programs are executed by the one or more processors, the one or more processors are caused to implement the steps in the method.

[0057] In a fourth aspect, a computer-readable storage medium storing a computer program is provided, wherein the computer program implements the steps in the method when executed by a processor.

[0058] Compared with the prior art, the present invention has the following beneficial effects:

[0059] 1. This invention explores the coupling mechanism between thin-walled parts and pneumatic supports, reveals that contact stiffness is the key to the formation of anti-resonance zones, and provides guidance for fully utilizing the support performance of pneumatic support devices;

[0060] 2. By adopting analysis methods such as modal identification and stability lobe diagram, a reasonable basis is provided for the selection of tool parameters in the mirror milling of large thin-walled parts;

[0061] 3. By adopting a spindle speed control method based on the anti-resonance region frequency, an effective way is provided for suppressing vibration during mirror milling of large thin-walled parts;

[0062] 4. By reasonably selecting the tool speed, the tool frequency and anti-resonance frequency are matched, thereby greatly reducing the amplitude during milling and ensuring milling stability. BRIEF DESCRIPTION OF THE DRAWINGS

[0063] Other features, objects and advantages of the present invention will become more apparent upon reading the detailed description of non-limiting embodiments with reference to the following drawings:

[0064] Figure 1 It is a schematic diagram of the overall process of the present invention;

[0065] Figure 2 Schematic diagram of substructure decomposition of the pneumatic support coupling system for thin-walled parts;

[0066] Figure 3 The milling stability lobe diagram of the spindle tool end under different tool overhang lengths. DETAILED DESCRIPTION

[0067] The present invention will be described in detail below with reference to specific embodiments. The following examples will help those skilled in the art to further understand the present invention, but are not intended to limit the present invention in any form. It should be noted that, for those skilled in the art, several changes and improvements can be made without departing from the scope of the present invention. These all fall within the scope of protection of the present invention.

[0068] The embodiment of the present invention provides an anti-resonance region control and vibration suppression system, referring to Figure 1 As shown, the system includes: a workpiece modal parameter identification module, an anti-resonance region frequency identification module and a tool processing instruction generation module.

[0069] Specifically, the workpiece modal parameter identification module: The module receives the thin-walled workpiece vibration signal input by the user, and analyzes the signal based on the modal parameter identification algorithm to obtain the modal parameters such as modal frequency, damping, residue, etc. of the first several modes of the system, and then sends the modal parameters to the anti-resonance zone frequency identification module.

[0070] Anti-resonance zone frequency identification module: This module receives the modal parameter information of the thin-walled workpiece. Based on the experimental modal parameters of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database, as well as the contact stiffness parameters of the two, it solves the frequency response curve of the thin-walled workpiece-pneumatic support coupling system, extracts the anti-resonance zone frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the coupling system frequency response curve, and then sends the anti-resonance zone frequency to the tool processing instruction generation module.

[0071] The frequency response curve of the thin-walled part-pneumatic support coupling system is solved by:

[0072] Reference Figure 2 As shown in the figure, the overall pneumatic support device is considered as substructure B, and the thin-walled component is considered as substructure A. The thin-walled component pneumatic support coupling system can be considered as a flexible connection between the two components, namely, a combination C. Point 1 is the coupling point, point 1a is the center of the thin-walled component, and point 1b is the equivalent action point of the support device. The two points are coupled together by a flexible connection. Only the displacement degrees of freedom along the normal direction of the thin-walled component are considered in the coupling. Based on the above substructure model, the frequency response of the thin-walled component pneumatic support assembly can be calculated using the substructure frequency response. The specific process is as follows:

[0073] Assuming external force Acting on point 1a of the thin-walled part in the assembly, since the action point is at the connection point, the load balance condition satisfies formula (1):

[0074]

[0075] in, represents the external force on substructure A at 1a; represents the external force on substructure B at 1b; according to the viscous damping model, the degree of freedom coordination conditions of the flexible connection satisfy equations (2) and (3), where the contact stiffness coefficient is: K c =k c +ic c ω,

[0076]

[0077]

[0078] Among them, K c represents the stiffness coefficient; k c represents the contact stiffness; c c represents contact damping; represents the displacement of point 1a in the assembly C; represents the displacement of point 1a in substructure A; represents the displacement of point 1b in the assembly C; represents the displacement of point 1b in substructure B; Substitute equation (3) into equation (2), and then according to the definition of transfer function ( and ), formula (2) It can be written in the form of formula (4):

[0079]

[0080] Substituting formula (4) into formula (1), we can get and The relationship equation (5):

[0081]

[0082] Sequentially transform formula (3), Substitute the transfer function into equation (5) In the definition of It can be expressed as formula (6):

[0083]

[0084] According to formula (6), the frequency response of the thin-walled pneumatic support assembly is The frequency response of the thin-walled part itself can be Pneumatic support frequency response and the connection stiffness K c The pneumatic support frequency response can be obtained by the design parameters of the support device, which satisfies the form of formula (7):

[0085]

[0086] in, represents the equivalent modal mass; represents the equivalent viscous damping; represents the equivalent modal stiffness.

[0087] Tool processing instruction generation module: The module receives the anti-resonance zone frequency information of the thin-walled part-pneumatic support coupling system, and determines the tool pass frequency that matches it. It also determines the tool speed in combination with the tool information such as the number of tool teeth given by the user, and combines the spindle tool milling stability lobe diagram under different tool overhangs in the database to determine the milling stability of the user-given tool length under specified processing conditions. If it is stable, it outputs a processing instruction containing tool information and speed information. Otherwise, it outputs an instruction to remind the user to change the tool overhang, number of teeth, or change the support ball material to meet the milling stability requirements.

[0088] Specifically, the knife-through frequency is set to be equal to the anti-resonance zone frequency; the tool speed is set: according to the knife-through frequency F T (Hz) and the number of teeth N, the tool speed can be determined as F T *60 / N(rpm).

[0089] Judging milling stability: Observation Figure 2 As shown in the lobe diagram, when the point corresponding to the axial cutting depth and spindle speed selected for processing is above the lobe diagram curve of milling stability corresponding to the specified tool overhang length, the milling is in an unstable state. When it is below, the milling is in a stable state.

[0090] The present invention also provides a method for regulating and suppressing vibration in an anti-resonance region, which specifically includes:

[0091] Workpiece modal parameter identification step: receiving the thin-walled workpiece vibration signal input by the user, and analyzing the signal based on the modal parameter identification algorithm to obtain the modal parameters such as modal frequency, damping, residue, etc. of the first several modes of the system, and then sending the modal parameters to the anti-resonance zone frequency identification step.

[0092] The anti-resonance region frequency identification step receives modal parameter information of the thin-walled workpiece, and based on the experimental modal parameters of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database and the contact stiffness parameters of the two, obtains the frequency response curve of the thin-walled workpiece-pneumatic support coupling system, extracts the anti-resonance region frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the coupling system frequency response curve, and then sends the anti-resonance region frequency to the tool processing instruction generation step.

[0093] The tool processing instruction generation steps are as follows: receiving the anti-resonance zone frequency information of the thin-walled part-pneumatic support coupling system, and determining the tool pass frequency that matches it, and determining the tool speed in combination with the tool information such as the number of tool teeth given by the user, and combining the spindle tool milling stability lobe diagram under different tool overhang lengths in the database to determine the milling stability of the user-given tool length under specified processing conditions. If it is stable, output a processing instruction containing tool information and speed information; otherwise, output an instruction to remind the user to change the tool overhang length, number of teeth, or change the support ball material to meet the milling stability requirements.

[0094] The embodiments of the present invention provide a method, system, equipment and medium for regulating and suppressing vibration in the anti-resonance zone, and select a vibration suppression method for the spindle speed based on the anti-resonance zone characteristics of the coupling system; establish a lumped parameter model and a frequency response coupling model of the coupling system, explore the coupling mechanism between thin-walled parts and pneumatic supports, and propose an anti-resonance zone regulation method based on contact materials. The dynamic characteristics and processing performance of thin-walled parts supported by different ball materials are compared, providing a theoretical basis and practical methods for fully utilizing the support performance of the pneumatic support device.

[0095] The present invention measures the amplitude-frequency characteristic curve of a thin-walled part supported by a given ball material based on a modal experimental method, and identifies the modal parameters of the curve; based on the analyzed modal parameters of the thin-walled part, the modal parameters of the pneumatic support, and the contact stiffness parameters of the two, the anti-resonance zone frequency of the thin-walled part-pneumatic support coupling system is solved, and by reasonably selecting the tool speed to match the tool frequency with the anti-resonance frequency, the amplitude in the milling process is greatly reduced, thereby ensuring milling stability.

[0096] Those skilled in the art will appreciate that, in addition to implementing the system and its various devices, modules, and units provided by the present invention in purely computer-readable program code, it is entirely possible to implement the same functions of the system and its various devices, modules, and units provided by the present invention in the form of logic gates, switches, application-specific integrated circuits, programmable logic controllers, and embedded microcontrollers by logically programming the method steps. Therefore, the system and its various devices, modules, and units provided by the present invention can be considered a hardware component, and the devices, modules, and units included therein for implementing various functions can also be considered as structures within the hardware component; the devices, modules, and units for implementing various functions can also be considered as both software modules implementing the method and structures within the hardware component.

[0097] The above describes specific embodiments of the present invention. It should be understood that the present invention is not limited to the specific embodiments described above, and those skilled in the art may make various changes or modifications within the scope of the claims, which do not affect the essence of the present invention. The embodiments of this application and the features in the embodiments may be combined with each other in any manner unless there is a conflict.

Claims

1. A method for regulating and suppressing vibration in an anti-resonance region, characterized in that: include: Workpiece modal parameter identification step: receiving and analyzing the thin-walled workpiece vibration signal input by the user, and sending the modal parameter information of the thin-walled workpiece obtained after analysis to the anti-resonance region frequency identification step; Anti-resonance region frequency identification step: receiving modal parameter information of the thin-walled part, calculating a frequency response curve of the thin-walled part-pneumatic support coupling system, extracting the anti-resonance region frequency and sending it to the tool processing instruction generation step; Tool processing instruction generation step: receiving the anti-resonance zone frequency, determining milling stability in combination with relevant tool information, and determining whether to output tool processing instructions based on the milling stability; The anti-resonance zone frequency identification step specifically includes: receiving modal parameter information of the thin-walled workpiece, solving the frequency response curve of the thin-walled workpiece-pneumatic support coupling system based on the modal parameter information of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database, and the contact stiffness parameters of the two, extracting the anti-resonance zone frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the frequency response curve, and then sending the anti-resonance zone frequency to the tool processing instruction generation step.

2. The anti-resonance region control and vibration suppression method according to claim 1, characterized in that: The frequency response curve of the thin-walled component-pneumatic support coupling system is solved as follows: The overall pneumatic support device is regarded as substructure B, the thin-walled component is regarded as substructure A, and the thin-walled component pneumatic support coupling system is regarded as a combination C of the two after flexible connection. Point 1 is the coupling point, point 1a is the center of the thin-walled component, and point 1b is the equivalent action point of the support device. The two points are coupled together through a flexible connection. The frequency response of the thin-walled component pneumatic support combination is obtained by calculating the substructure frequency response. The specific process is as follows: Assume external force Acting on point 1a of the thin-walled part in the assembly, since the action point is at the connection point, the load balance condition satisfies formula (1): in, represents the external force on substructure A at 1a; represents the external force on substructure B at 1b; according to the viscous damping model, the degree of freedom coordination conditions of the flexible connection satisfy equations (2) and (3), where the contact stiffness coefficient is: K c =k c +ic c ω, Among them, K c represents the stiffness coefficient; k c represents the contact stiffness; c c represents contact damping; represents the displacement of point 1a in the assembly C; represents the displacement of point 1a in substructure A; represents the displacement of point 1b in the assembly C; represents the displacement of point 1b in substructure B; Substitute equation (3) into equation (2), and then according to the definition of transfer function Formula (2) Written in the form of formula (4): Substituting formula (4) into formula (1), we get and The relationship equation (5): Sequentially transform formula (3), Substitute the transfer function into equation (5) In the definition of It is expressed as formula (6): According to formula (6), the frequency response of the thin-walled pneumatic support assembly is Through the frequency response of the thin-walled part itself Pneumatic support frequency response and the connection stiffness K c The pneumatic support frequency response can be obtained by the design parameters of the support device, which satisfies the form of formula (7): in, represents the equivalent modal mass; represents the equivalent viscous damping; represents the equivalent modal stiffness.

3. The anti-resonance region control and vibration suppression method according to claim 1, characterized in that: The tool processing instruction generation step specifically includes: receiving anti-resonance zone frequency information of the thin-walled workpiece-pneumatic support coupling system, determining a tool pass frequency that matches the anti-resonance zone frequency, and determining a tool rotation speed based on relevant tool information including the number of tool teeth specified by the user, and then determining the milling stability of the spindle tool under specified processing conditions based on a spindle tool milling stability lobe diagram for different tool overhang lengths in a database; If the milling is stable, a processing instruction containing tool information and speed information is output; otherwise, an instruction is output to remind the user to change the tool overhang length, number of teeth, or change the support ball material to meet the milling stability requirements.

4. An anti-resonance region control and vibration suppression system, characterized in that: include: Workpiece modal parameter identification module: receives and analyzes the thin-walled workpiece vibration signal input by the user, and sends the modal parameter information of the thin-walled workpiece obtained after analysis to the anti-resonance region frequency identification module; Anti-resonance region frequency identification module: receives the modal parameter information of the thin-walled part, calculates the frequency response curve of the thin-walled part-pneumatic support coupling system, extracts the anti-resonance region frequency and sends it to the tool processing instruction generation module; Tool processing instruction generation module: receives the anti-resonance zone frequency, determines the milling stability in combination with relevant tool information, and determines whether to output the tool processing instruction according to the milling stability; The anti-resonance zone frequency identification module specifically includes: receiving modal parameter information of the thin-walled workpiece, solving the frequency response curve of the thin-walled workpiece-pneumatic support coupling system based on the modal parameter information of the thin-walled workpiece and the modal parameters of the pneumatic support already in the database, and the contact stiffness parameters of the two, extracting the anti-resonance zone frequency corresponding to the minimum frequency response amplitude between the first two modal frequencies of the frequency response curve, and then sending the anti-resonance zone frequency to the tool processing instruction generation module.

5. The anti-resonance region control and vibration suppression system according to claim 4, characterized in that: The frequency response curve of the thin-walled component-pneumatic support coupling system is solved as follows: The overall pneumatic support device is regarded as substructure B, the thin-walled component is regarded as substructure A, and the thin-walled component pneumatic support coupling system is regarded as a combination C of the two after flexible connection. Point 1 is the coupling point, point 1a is the center of the thin-walled component, and point 1b is the equivalent action point of the support device. The two points are coupled together through a flexible connection. The frequency response of the thin-walled component pneumatic support combination is obtained by calculating the substructure frequency response. The specific process is as follows: Assume external force Acting on point 1a of the thin-walled part in the assembly, since the action point is at the connection point, the load balance condition satisfies formula (1): in, represents the external force on substructure A at 1a; represents the external force on substructure B at 1b; according to the viscous damping model, the degree of freedom coordination conditions of the flexible connection satisfy equations (2) and (3), where the contact stiffness coefficient is: K c =k c +ic c ω, Among them, K c represents the stiffness coefficient; k c represents the contact stiffness; c c represents contact damping; represents the displacement of point 1a in the assembly C; represents the displacement of point 1a in substructure A; represents the displacement of point 1b in the assembly C; represents the displacement of point 1b in substructure B; Substitute equation (3) into equation (2), and then according to the definition of transfer function and , formula (2) Written in the form of formula (4): Substituting formula (4) into formula (1), we get and The relationship equation (5): Sequentially transform formula (3), Substitute the transfer function into equation (5) In the definition of It is expressed as formula (6): According to formula (6), the frequency response of the thin-walled pneumatic support assembly is Through the frequency response of the thin-walled part itself Pneumatic support frequency response and the connection stiffness K c The pneumatic support frequency response can be obtained by the design parameters of the support device, which satisfies the form of formula (7): in, represents the equivalent modal mass; represents the equivalent viscous damping; represents the equivalent modal stiffness.

6. The anti-resonance region control and vibration suppression system according to claim 4, characterized in that: The tool processing instruction generation module specifically includes: receiving anti-resonance zone frequency information of the thin-walled workpiece-pneumatic support coupling system, determining a tool pass frequency that matches the anti-resonance zone frequency, and determining a tool rotation speed based on relevant tool information including the number of tool teeth specified by the user, and then determining the milling stability of the spindle tool under specified processing conditions based on a spindle tool milling stability lobe diagram for different tool overhang lengths in a database; If the milling is stable, a processing instruction containing tool information and speed information is output; otherwise, an instruction is output to remind the user to change the tool overhang length, number of teeth, or change the support ball material to meet the milling stability requirements.

7. A device, characterized in that The device comprises: one or more processors; a storage device for storing one or more programs, When the one or more programs are executed by the one or more processors, the one or more processors implement the steps of the method according to any one of claims 1 to 3.

8. A computer-readable storage medium storing a computer program, characterized in that: When the computer program is executed by a processor, the steps of the method according to any one of claims 1 to 3 are implemented.

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