CN112487673B - Key host assembly structure optimization design method based on working state of machine tool - Google Patents
Key host assembly structure optimization design method based on working state of machine tool Download PDFInfo
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Abstract
The invention relates to a structural optimization design method of a machine tool assembly, in particular to a key host machine assembly structural optimization design method based on the working state of the machine tool, which comprises the following steps: A. optimizing based on multiplexing Kuang Tapu under the motion state of the machine tool; B. parameterizing and reconstructing by combining the optimized geometric model of the topological configuration; C. optimizing the shape and the size of the machine tool based on multiple working conditions in the motion state; D. based on the production state evaluation under the machine tool machining and assembly conditions. The invention aims at solving the problems that the invention is not limited to the component structure to be optimized, but comprehensively considers the whole machine installation structures such as the motion connecting piece, the supported piece and the like, fully considers each motion state and various working conditions of the machine tool, ensures that the optimized design index is closer to the actual working state of the machine tool, and ensures that the reliability of the optimized structure is higher.
Description
Technical Field
The invention relates to a structural optimization design method of a machine tool assembly, in particular to a key host machine assembly structural optimization design method based on the working state of a machine tool.
Background
With the development and upgrade of the manufacturing industry, higher and higher requirements are also put on a digital processing machine tool, so that the machine tool is required to have higher operation stability and processing effect, and also is required to have lower energy loss and manufacturing cost. Therefore, the dynamic and static rigidity of the machine tool structure needs to be fully considered to improve the stability of the machine tool structure during the design of the machine tool, and meanwhile, the light design is realized to reduce the energy loss of moving parts, improve the driving efficiency and reduce the manufacturing cost.
The traditional design method of the key main machine component structure of the machine tool is mostly concentrated on 'fool thick' type artificial model parameter modification and repeated calculation and check, and the design method is low in design efficiency and does not meet the design target of high rigidity and light weight of the traditional machine tool. Therefore, some research institutions have started to optimally design main machine tool supporting structures such as a machine tool body, a stand column and the like by means of technologies such as optimization algorithm, size optimization, topological optimization and the like, but the existing optimal design method is basically based on a certain static state of the machine tool, does not consider load change of a moving part or a rotating part caused by gravity center change or full stroke action, and cannot meet design requirements under the multi-movement working condition of the machine tool. Some optimization design methods consider the dynamic performance of a single structure, but neglect the influence of the mass distribution and the connection mode of the functional components connected with the dynamic performance of the whole machine, and in the state of the whole machine, the effect of optimizing the dynamic performance of the single structure is not obvious, and the reaction is possible. In addition, in the design of the main supporting structure, the conventional design method cannot take the key point displacement of the supported functional component as an optimization constraint condition, so that the dynamic and static rigidity of the main supporting structure can only be ensured, and the supporting rigidity of the main supporting structure cannot be ensured.
Disclosure of Invention
The invention aims to overcome the defects of the prior art and provide the structural optimization design method of the key host machine component of the machine tool, which not only considers the component structure, but also comprehensively considers the assembly and movement states of the component structure, the design index is closer to the real working state of the machine tool, and the reliability of the optimized structure is higher.
In order to solve the technical problems, the invention is realized by the following technical scheme: the key host machine component structure optimization design method based on the working state of the machine tool comprises the following steps:
A. optimizing based on multiplexing Kuang Tapu under the motion state of the machine tool;
B. parameterizing and reconstructing by combining the optimized geometric model of the topological configuration;
C. optimizing the shape and the size of the machine tool based on multiple working conditions in the motion state;
D. based on the production state evaluation under the machine tool machining and assembly conditions;
E. judging whether the evaluation result meets the design requirement, if so, completing the optimized design, otherwise, returning to the step C, and purposefully further optimizing the corresponding shape and size;
the step A comprises the following steps of:
A1. disassembling and simplifying the whole machine tool structure, extracting a target structure and a moving part structure unit supported by the target structure, and compressing small features and parts, which do not influence structural analysis results, but increase finite unit grid division time and calculation time, on the moving part structure unit, wherein the small features comprise but are not limited to threaded holes, chamfers and rounding;
A2. expanding the structural volume of the target structure according to the movement range and the non-interference space of the target structure, and completely filling solid materials into the target structure to define a design domain;
A3. the three-dimensional model of the design domain and the simplified moving part structural unit is imported into finite element software, and corresponding material parameters are respectively assigned, wherein the material parameters comprise but are not limited to elastic modulus, poisson ratio, density, thermal expansion coefficient and heat conductivity coefficient;
A4. carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
A5. carrying out multi-station integrated analysis considering pose change on the finite element model, and calculating related data of structural volume, key displacement, key stress, key natural frequency and comprehensive flexibility which need to be referred in the optimization process; wherein the multiple-working condition integrated analysis includes, but is not limited to: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; influence of cutting force on a target structure in a machining state; the overall structural mode analysis of the structural unit connection of the moving part is considered;
A6. establishing a topological optimization mathematical model, importing the data calculated in the step A5 into the topological optimization mathematical model, and optimizing by utilizing an optimization algorithm until the topological optimization mathematical model converges, and extracting a conceptual design diagram of a target structure;
b, carrying out model reconstruction of three-dimensional geometric modeling according to the conceptual design diagram extracted in the step A6 in combination with geometric model parameterization reconstruction of the optimized topological structure, and parameterizing specific detail features including, but not limited to, the position, shape and size of a lightening hole, the position and thickness of a structural reinforcement supporting plate, and the length and section size of a cantilever;
step C is based on the multi-working condition shape and size optimization of the machine tool in motion state, and is further optimized for local detail features, and comprises the following steps:
C1. defining materials for the reconstruction model, including but not limited to modulus of elasticity, poisson's ratio, density, coefficient of thermal expansion, and coefficient of thermal conductivity;
C2. performing finite element mesh division and boundary condition loading on the reconstruction model;
C3. carrying out multi-working condition integrated analysis considering pose change on the reconstruction model, and calculating related data of structural volume, key displacement, key stress, key natural frequency and comprehensive flexibility; wherein the multiple-working condition integrated analysis includes, but is not limited to: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; the overall structural mode analysis of the structural unit connection of the moving part is considered;
C4. establishing a shape and size optimization mathematical model, importing the data calculated in the step C3 into the shape and size optimization mathematical model, and optimizing by using an optimization algorithm until the shape and size optimization mathematical model converges to obtain final target size and shape data;
and D, evaluating the production state based on the machine tool machining and assembly conditions, namely evaluating the production state of the model subjected to shape and size optimization based on the machining and assembly process, and confirming whether the production can be realized through the existing production conditions.
Preferably, the three-dimensional model of the moving part unit in step A3 may be replaced by mass points, which are arranged on the center of gravity of the moving part unit, and which are given mass, mass moment of inertia related parameters along each axis, wherein the positions of the mass points change with the change of the position of the center of gravity of the moving part unit when the moving part unit moves.
Preferably, in step A6, three sets of optimization targets and constraint combinations are provided for the topology optimization mathematical model, respectively:
case1: minimizing integrated compliance, constraining volume, critical displacement, and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the total volume of the target structure; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency;
case2: maximizing first order natural frequency, constraining volume, critical displacement, and integrated compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the total volume of the target structure; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency;
case3: minimizing volume, constraining integrated compliance, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the total volume of the target structure; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency.
Preferably, the optimization algorithm in step A6 is sequentially performed according to the three sets of optimization targets and constraint combinations, that is, first, case1 is executed, if the model is converged, the optimization is finished, if the model is unable to be converged, case2 is executed, similarly, if the model is converged, the optimization is finished, and if the model is unable to be converged, case3 is executed.
Preferably, in the optimization algorithm in the step A6, three groups of optimization targets and constraint combinations are simultaneously calculated, and a group of data with the best convergence effect is selected as an optimization result.
Preferably, in step C4, for the shape and size optimization mathematical model, two sets of optimization targets and constraint combinations are provided, where Case4 is suitable for the design target of light weight and Case5 is suitable for the design target of increasing strength and reducing structural deformation, specifically as follows:
case4: minimizing target structure volume, constraining maximum stress, critical displacement, and critical frequency
Wherein x is a design variable, namely the shape parameter, the size and the position of the target feature; v is the total volume of the target structure; d, d j Refer to the j-th keypoint displacement; f (f) k Representing the k-th order natural frequency; sigma (sigma) max Maximum stress for structural stress;
case5: minimizing principal displacements, constraining structure volume, critical natural frequency and maximum stress
Wherein x is a design variable, namely the shape parameter, the size and the position of the target feature; v is the total volume of the target structure; d, d j Refer to the j-th keypoint displacement; f (f) k Representing the k-th order natural frequency; sigma (sigma) max Is the maximum stress to which the structure is subjected.
Compared with the prior art, the invention has the beneficial effects that: the invention is not limited to the optimized component structure, but fully considers the whole machine installation structures such as the motion connecting piece, the supported piece and the like, and the optimized component structure can fully meet the design requirements of the machine tool on structural rigidity and light weight, thereby realizing the optimal design of the whole machine tool. The invention is not based on optimization under static state, and fully considers the optimization of each motion state of the machine tool and various working conditions, so that the optimized design index is more in line with the actual working state of the machine tool. In addition, by adopting an optimization algorithm combining a plurality of groups of optimization targets and constraints, the optimal optimization result can be selected on the premise of ensuring optimization, the optimization compatibility is good, and the reliability of the optimized structure is high.
Drawings
FIG. 1 is a schematic flow chart of the method of the present invention.
Fig. 2 is a schematic diagram of the optimizing flow of the method based on multiplexing Kuang Tapu under the motion state of the machine tool.
FIG. 3 is a schematic diagram of the method of the present invention for performing multi-condition integrated analysis on a finite element model.
FIG. 4 is a schematic diagram of a multi-tool shape and size optimization flow based on machine tool motion.
Detailed Description
The invention is described in further detail below with reference to the drawings and the detailed description.
As shown in fig. 1, the key host assembly structure optimization design method based on the working state of the machine tool of the invention comprises the following steps:
step 100, optimizing based on multiplexing Kuang Tapu under the motion state of the machine tool: the method comprises the steps of disassembling and simplifying the whole machine structure of a machine tool, comprehensively considering a target structure and a motion connection structure thereof, carrying out multi-pose multi-station integrated analysis on a finite element model, optimizing a topological optimization mathematical model by means of an optimization algorithm, and extracting a conceptual design diagram of the target structure;
step 200, combining the geometric model parameterized reconstruction of the optimized topological configuration: model reconstruction of three-dimensional geometric modeling is performed according to the conceptual design diagram extracted in step 100, and specific detail features are parameterized for the purpose of changing the structure shape through size driving. Wherein the detail characteristics comprise the position, shape and size of a certain lightening hole, the position and thickness of a certain structural strengthening support plate, the length and section size of a certain cantilever and the like;
step 300, optimizing the shape and the size of the machine tool based on multiple working conditions in the motion state: the reconstruction model is subjected to multi-working condition integrated analysis based on pose change, and the local detail features are further optimized by means of an optimization algorithm, so that the purpose of light weight or structural strength increase is achieved;
step 400, production state evaluation based on machine tool machining and assembly conditions: evaluating the production state of the model with optimized shape and size based on the processing and assembly process, and determining whether the production can be realized by the existing production conditions;
and 500, judging whether the evaluation result meets the design requirement, if so, optimizing the design, otherwise, returning to the step 300, purposefully modifying the corresponding detail characteristics, and executing further optimization of the shape and the size again until the evaluation result meets the design requirement.
Fig. 2 shows a multi-task topology optimization process based on machine tool motion at step 100, comprising the steps of:
step 101, disassembling and simplifying the whole machine structure of the machine tool, extracting a target structure and a moving part structure unit supported by the target structure, and compressing small features and parts which do not influence structural analysis results but increase finite unit grid division time and calculation time on the moving part structure unit, wherein the small features comprise threaded holes, chamfers, rounding and the like;
step 102, expanding the structural volume of the target structure according to the movement range and the non-interference space of the target structure, and completely filling solid materials into the target structure to define a design domain;
and 103, importing the design domain and the three-dimensional model of the simplified moving part structural unit into finite element software, and respectively assigning material parameters such as elastic modulus, poisson's ratio, density, thermal expansion coefficient, thermal conductivity coefficient and the like. If the moving part structure unit is complex, mass points can be used for replacing the moving part structure unit for simplifying the model, the mass points are arranged on the gravity centers of the moving part structure unit, parameters such as mass, mass moment of inertia along each axis and the like are given to the mass points, and when the moving part structure unit moves, the positions of the mass points change along with the change of the gravity center positions of the moving part structure unit.
104, carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
step 105. Carrying out multi-task integrated analysis considering pose change on the finite element model, and calculating the structural volume vol, the key displacement disp1 to dispN and the key stress sigma which need to be referred in the optimization process max Critical natural frequency f 1 To f N Comprehensive compliance C (w) 1 ,w 2 ,…,w N ) The multi-working condition integrated analysis includes, as shown in fig. 3: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; the influence of cutting force on a target structure in a machining state, the overall structure modal analysis considering the connection of a moving part structural unit and the like;
step 106, establishing a topological optimization mathematical model, importing the data calculated in the step 1055 into the topological optimization mathematical model, and optimizing by utilizing an optimization algorithm until the topological optimization mathematical model converges, and extracting a conceptual design diagram of a target structure;
for the topology optimization mathematical model, three sets of optimization targets and constraint combinations are preferred, respectively:
case1: minimizing integrated compliance, constraining volume, critical displacement, and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the target knotConstructing the total volume; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency;
case2: maximizing first order natural frequency, constraining volume, critical displacement, and integrated compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the total volume of the target structure; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency;
case3: minimizing volume, constraining integrated compliance, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; c (C) w For the comprehensive compliance, represent the comprehensive compliance of the target structure overall considering each working condition, where k j The weight of the j working condition is occupied; v is the total volume of the target structure; d, d k Refers to the kth keypoint displacement; f (f) l Representing the first order natural frequency.
Two optimization algorithms are provided for the three sets of optimization objectives and constraint combinations described above: one is sequentially executed according to the sequence from Case1 to Case3, namely, firstly, case1 is executed, if the model is converged, the optimization is finished, if the model is not converged, case2 is executed, similarly, if the model is converged, the optimization is finished, and if the model is not converged, case3 is executed; the other method is to calculate three groups of optimization targets and constraint combinations simultaneously, and select a group of data with the best convergence effect as an optimization result; one of the two methods can be selected at will for optimization calculation, so that not only can the optimization with a solution be ensured, but also the optimal optimization result can be selected, the optimization compatibility is good, and the reliability of the optimized structure is high.
Fig. 4 shows a schematic diagram of a multi-task shape and size optimization process based on machine tool motion in step 300, comprising the steps of:
step 301, material definition is carried out on the reconstruction model, namely, material parameters such as elastic modulus, poisson ratio, density, thermal expansion coefficient, heat conduction coefficient and the like are assigned;
step 302, carrying out finite element mesh division and boundary condition loading on the reconstruction model;
step 303, carrying out multi-task integrated analysis considering pose change on the reconstruction model, and calculating related data of structural volume, key displacement, key stress, key natural frequency and comprehensive flexibility; the multi-working condition integrated analysis comprises the following steps: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; complete machine structural modal analysis considering the connection of the structural units of the moving parts, and the like;
step 304, establishing a shape and size optimization mathematical model, importing the data calculated in the step C3 into the shape and size optimization mathematical model, and optimizing by using an optimization algorithm until the shape and size optimization mathematical model converges to obtain final target size and shape data;
for the shape and size optimization mathematical model, two groups of optimization targets and constraint combinations of Case4 and Case5 are provided, wherein Case4 is suitable for a lightweight design target, case5 is suitable for a design target for increasing strength and reducing structural deformation, and one group of optimization targets can be selected to be executed according to different design requirements, and the two groups of optimization targets and constraint combinations are specifically as follows:
case4: minimizing target structure volume, constraining maximum stress, critical displacement, and critical frequency
Where x is a design variable, i.e. a target featureShape parameters and dimensions, and location; v is the total volume of the target structure; d, d j Refer to the j-th keypoint displacement; f (f) k Representing the k-th order natural frequency; sigma (sigma) max Maximum stress for structural stress;
case5: minimizing principal displacements, constraining structure volume, critical natural frequency and maximum stress
Wherein x is a design variable, namely the shape parameter, the size and the position of the target feature; v is the total volume of the target structure; d, d j Refer to the j-th keypoint displacement; f (f) k Representing the k-th order natural frequency; sigma (sigma) max Is the maximum stress to which the structure is subjected.
Although the present invention has been described in detail hereinabove, the present invention is not limited thereto and various modifications may be made by those skilled in the art in accordance with the principles of the present invention. Therefore, all modifications made in accordance with the principles of the present invention should be understood as falling within the scope of the present invention.
Claims (6)
1. The key host machine component structure optimization design method based on the working state of the machine tool is characterized by comprising the following steps:
A. optimizing based on multiplexing Kuang Tapu under the motion state of the machine tool;
B. parameterizing and reconstructing by combining the optimized geometric model of the topological configuration;
C. optimizing the shape and the size of the machine tool based on multiple working conditions in the motion state;
D. based on the production state evaluation under the machine tool machining and assembly conditions;
E. judging whether the evaluation result meets the design requirement, if so, completing the optimized design, otherwise, returning to the step C, and purposefully further optimizing the corresponding shape and size;
the step A comprises the following steps of:
A1. disassembling and simplifying the whole machine tool structure, extracting a target structure and a moving part structure unit supported by the target structure, and compressing small features and parts, which do not influence structural analysis results, but increase finite unit grid division time and calculation time, on the moving part structure unit, wherein the small features comprise but are not limited to threaded holes, chamfers and rounding;
A2. expanding the structural volume of the target structure according to the movement range and the non-interference space of the target structure, and completely filling solid materials into the target structure to define a design domain;
A3. the three-dimensional model of the design domain and the simplified moving part structural unit is imported into finite element software, and corresponding material parameters are respectively assigned, wherein the material parameters comprise but are not limited to elastic modulus, poisson ratio, density, thermal expansion coefficient and heat conductivity coefficient;
A4. carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
A5. carrying out multi-station integrated analysis considering pose change on the finite element model, and calculating related data of structural volume, key displacement, key stress, key natural frequency and comprehensive flexibility which need to be referred in the optimization process; wherein the multiple-working condition integrated analysis includes, but is not limited to: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; the overall structural mode analysis of the structural unit connection of the moving part is considered;
A6. establishing a topological optimization mathematical model, importing the data calculated in the step A5 into the topological optimization mathematical model, and optimizing by utilizing an optimization algorithm until the topological optimization mathematical model converges, and extracting a conceptual design diagram of a target structure;
b, carrying out model reconstruction of three-dimensional geometric modeling according to the conceptual design diagram extracted in the step A6 in combination with geometric model parameterization reconstruction of the optimized topological structure, and parameterizing specific detail features including, but not limited to, the position, shape and size of a lightening hole, the position and thickness of a structural reinforcement supporting plate, and the length and section size of a cantilever;
step C is based on the multi-working condition shape and size optimization of the machine tool in motion state, and is further optimized for local detail features, and comprises the following steps:
C1. defining materials for the reconstruction model, including but not limited to modulus of elasticity, poisson's ratio, density, coefficient of thermal expansion, and coefficient of thermal conductivity;
C2. performing finite element mesh division and boundary condition loading on the reconstruction model;
C3. carrying out multi-working condition integrated analysis considering pose change on the reconstruction model, and calculating related data of structural volume, key displacement, key stress, key natural frequency and comprehensive flexibility; wherein the multiple-working condition integrated analysis includes, but is not limited to: dynamic and static analysis of a target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under inertia force when the moving part structure unit is in an acceleration and deceleration state; thermodynamic coupling analysis of a target structure under the distribution of a complete machine temperature field; influence of cutting force on a target structure in a machining state; the overall structural mode analysis of the structural unit connection of the moving part is considered;
C4. establishing a shape and size optimization mathematical model, importing the data calculated in the step C3 into the shape and size optimization mathematical model, and optimizing by using an optimization algorithm until the shape and size optimization mathematical model converges to obtain final target size and shape data;
and D, evaluating the production state based on the machine tool machining and assembly conditions, namely evaluating the production state of the model subjected to shape and size optimization based on the machining and assembly process, and confirming whether the production can be realized through the existing production conditions.
2. The method according to claim 1, wherein the three-dimensional model of the moving component structure unit in step A3 is replaced by mass points, the mass points are disposed on the center of gravity of the moving component structure unit, and mass moment of inertia related parameters along each axis are given to the mass points, wherein the positions of the mass points change with the change of the center of gravity of the moving component structure unit when the moving component structure unit moves.
3. The method for optimizing the design of a key host component structure based on the working state of a machine tool according to claim 1 or 2, wherein in step A6, three sets of optimization targets and constraint combinations are provided for the topology optimization mathematical model, respectively:
case1: minimizing integrated compliance, constraining volume, critical displacement, and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; cw is the comprehensive compliance and represents the comprehensive compliance of the target structure comprehensively considering all working conditions, wherein kj is the weight occupied by the j-th working condition; v is the total volume of the target structure; dk refers to the kth keypoint displacement; fl represents the first order natural frequency;
case2: maximizing first order natural frequency, constraining volume, critical displacement, and integrated compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; cw is the comprehensive compliance and represents the comprehensive compliance of the target structure comprehensively considering all working conditions, wherein kj is the weight occupied by the j-th working condition; v is the total volume of the target structure; dk refers to the kth keypoint displacement; fl represents the first order natural frequency;
case3: minimizing volume, constraining integrated compliance, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in the design domain; cw is the comprehensive compliance and represents the comprehensive compliance of the target structure comprehensively considering all working conditions, wherein kj is the weight occupied by the j-th working condition; v is the total volume of the target structure; dk refers to the kth keypoint displacement; fl represents the first order natural frequency.
4. The method for optimizing the structure of a key host component based on the working state of a machine tool according to claim 3, wherein in the step A6, the optimization algorithm is sequentially performed according to the three sets of optimization targets and constraint combinations, namely, firstly, case1 is executed, if the model is converged, the optimization is finished, if the model is not converged, case2 is executed, and similarly, if the model is converged, the optimization is finished, and if the model is not converged, case3 is executed.
5. The method for optimizing the design of the key host component structure based on the working state of the machine tool according to claim 3, wherein the optimization algorithm in the step A6 is to calculate three groups of optimization targets and constraint combinations simultaneously, and a group of data with the best convergence effect is selected as an optimization result.
6. The method for optimizing design of a critical host component structure based on a working state of a machine tool according to claim 1, wherein in step C4, for a shape and size optimizing mathematical model, two sets of optimization targets and constraint combinations are provided, wherein Case4 is suitable for a lightweight design target, and Case5 is suitable for a design target for increasing strength and reducing structural deformation, specifically as follows:
case4: minimizing target structure volume, constraining maximum stress, critical displacement, and critical frequency
Wherein x is a design variable, namely the shape parameter, the size and the position of the target feature; v is the total volume of the target structure; dj refers to the j-th keypoint displacement; fk represents the kth order natural frequency; sigma max is the maximum stress of the structural stress;
case5: minimizing principal displacements, constraining structure volume, critical natural frequency and maximum stress
Wherein x is a design variable, namely the shape parameter, the size and the position of the target feature; v is the total volume of the target structure; dj refers to the j-th keypoint displacement; fk represents the kth order natural frequency; σmax is the maximum stress to which the structure is subjected.
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