CN112487673A - Key host machine component structure optimization design method based on machine tool working state - Google Patents
Key host machine component structure optimization design method based on machine tool working state Download PDFInfo
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Abstract
The invention relates to a structure optimization design method of a machine tool component, in particular to a key host machine component structure optimization design method based on the working state of a machine tool, which comprises the following steps: A. based on the multi-working-condition topological optimization in the machine tool motion state; B. combining the optimized geometric model parameterization reconstruction of the topological configuration; C. optimizing the shape and size based on multiple working conditions under the motion state of the machine tool; D. and evaluating the production state based on the machining and assembling conditions of the machine tool. The invention aims to comprehensively consider the mounting structures of the whole machine, such as the motion connecting piece, the supported piece and the like, not the component structure needing to be optimized, and fully consider all motion states and various working conditions of the machine tool, so that the optimized design index is closer to the actual working state of the machine tool, and the optimized structure has higher reliability.
Description
Technical Field
The invention relates to a structure optimization design method of a machine tool component, in particular to a key host machine component structure 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 forward on the numerical control machine tool, so that the machine tool is required to have higher operation stability and processing effect, and lower energy loss and manufacturing cost. Therefore, when designing a machine tool, it is necessary to fully consider the dynamic and static stiffness of the machine tool structure to improve the stability thereof, and at the same time, to realize a lightweight design to reduce the energy loss of the moving parts, to improve the driving efficiency, and to reduce the manufacturing cost.
The traditional design method for the key main machine component structure of the machine tool mostly focuses on manual model parameter modification and repeated calculation and checking in a 'fool and stubborn' mode, and the design method is not only low in design efficiency, but also not in line with the design target of high rigidity and light weight of the existing machine tool. For this reason, some research organizations have started to optimize and design main machine tool support structures such as machine beds and columns by using optimization algorithms and techniques such as size optimization and topology optimization, but the current optimization design methods are basically based on the machine tool in a certain static state, and the load change of moving parts or rotating parts due to gravity center change or full-stroke motion is not considered, so that the design requirements of the machine tool under multiple motion conditions cannot be met. Although some optimization design methods consider the dynamic performance of a single structure, the influence of the mass distribution and the connection mode of the functional components connected to the optimization design methods on the dynamic performance of the whole machine is ignored, and the effect of optimizing the dynamic performance of the single structure is not obvious and possibly plays a role in reaction in the state of the whole machine. In addition, in the design of the main supporting structure, the existing design method cannot take the displacement of the key point 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 a structural optimization design method of a key main machine component of a machine tool, which not only considers the component structure, but also comprehensively considers the assembly and motion states of the component structure, so that the design index is closer to the real working state of the machine tool, and the optimized structure has higher reliability.
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 machine tool working state comprises the following steps:
A. based on the multi-working-condition topological optimization in the machine tool motion state;
B. combining the optimized geometric model parameterization reconstruction of the topological configuration;
C. optimizing the shape and size based on multiple working conditions under the motion state of the machine tool;
D. evaluating the production state based on the machining and assembling conditions of the machine tool;
E. judging whether the evaluation result meets the design requirement, if so, finishing the optimization design, otherwise, returning to the step C, and performing further optimization on the corresponding shape and size in a targeted manner;
the step A comprises the following steps of based on multi-working-condition topological optimization under the machine tool motion state:
A1. disassembling and simplifying the whole machine structure of the machine tool, extracting a target structure and a moving part structural unit supported by the target structure, and compressing all fine features and parts on the moving part structural unit, which do not influence the structural analysis result but increase the limited unit grid division time and the calculation time, wherein the fine features include but are not limited to threaded holes, chamfers and rounds;
A2. expanding the structure volume of the target structure according to the motion range and the non-interference space of the target structure, and filling all solid materials in the target structure to define the target structure as a design domain;
A3. importing the three-dimensional models of the design domain and the simplified moving part structure unit into finite element software, and respectively assigning corresponding material parameters, wherein the material parameters comprise but are not limited to elastic modulus, Poisson's ratio, density, thermal expansion coefficient and thermal conductivity coefficient;
A4. carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
A5. performing multi-working condition integrated analysis considering pose change on the finite element model, and calculating relevant data of structure volume, key displacement, key stress, key natural frequency and comprehensive compliance which need to be referred to in the optimization process; wherein, the multi-condition integrated analysis includes but is not limited to: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; influence of cutting force on a target structure in a machining state; the modal analysis of the whole structure of the connection of the structural units of the moving parts is considered;
A6. establishing a topological optimization mathematical model, importing the data calculated in the step A5 into the topological optimization mathematical model, optimizing by using an optimization algorithm until the topological optimization mathematical model is converged, and extracting a conceptual design diagram of a target structure;
step B, combining the optimized geometric model parameterization reconstruction of the topological structure, namely performing three-dimensional geometric model reconstruction according to the conceptual design diagram extracted in the step A6, and parameterizing specific detail characteristics, wherein the detail characteristics comprise but are not limited to the position, the shape and the size of a lightening hole, the position and the thickness of a structure strengthening support plate, and the length and the section size of a cantilever;
step C is based on the optimization of the shape and the size of the multiple working conditions under the motion state of the machine tool, is further optimized aiming at local detailed characteristics, and comprises the following steps:
C1. defining materials for the reconstructed model, including but not limited to elastic modulus, poisson's ratio, density, thermal expansion coefficient and thermal conductivity coefficient;
C2. carrying out finite element mesh division and boundary condition loading on the reconstruction model;
C3. performing multi-working-condition integrated analysis considering pose change on the reconstructed model, and calculating relevant data of structure volume, key displacement, key stress, key natural frequency and comprehensive compliance; wherein, the multi-condition integrated analysis includes but is not limited to: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; the modal analysis of the whole structure of the connection of the structural units of the moving parts 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 machining and assembling conditions of the machine tool, namely evaluating the production state of the model subjected to shape and size optimization based on the machining and assembling processes, and determining whether the production can be realized through the existing production conditions.
Preferably, the three-dimensional model of the moving part unit described in step a3 is replaced with a mass point which is located at the center of gravity of the moving part unit and which is assigned with mass and mass-moment-of-inertia parameters along each axis, wherein the position of the mass point changes with 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 objectives and constraint combinations are provided for the topology optimization mathematical model, which are respectively:
case 1: minimizing integrated compliance, constrained volume, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflRepresents the natural frequency of the l order;
case 2: maximizing first order natural frequency, constraining volume, critical displacement and comprehensive compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflRepresents the natural frequency of the l order;
case 3: minimizing volume, constraining complex compliance, critical displacements and critical frequencies
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflIndicating the ith order natural frequency.
Preferably, the optimization algorithm in step a6 is performed sequentially according to the three sets of optimization targets and constraint combinations, that is, Case1 is performed first, if the model converges, the optimization ends, if the model fails to converge, Case2 is performed, and similarly, if the model converges, the optimization ends, and if the model fails to converge, Case3 is performed.
Preferably, the optimization algorithm in step a6 is to calculate three sets of optimization objectives and constraint combinations simultaneously, and select a set of data with the best convergence effect as the optimization result.
Preferably, in step C4, for the shape and size optimization mathematical model, two sets of optimization objectives and constraint combinations are provided, wherein Case4 is suitable for the design objective of light weight, and Case5 is suitable for the design objective of increasing strength and reducing structural deformation, specifically as follows:
case 4: 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; djRefers to the jth keypoint displacement; f. ofkRepresents the k-th order natural frequency; sigmamaxThe maximum stress to which the structure is stressed;
case 5: minimizing dominant displacements, constraining structure volume, critical natural frequencies 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; djRefers to the jth keypoint displacement; f. ofkRepresents the k-th order natural frequency; sigmamaxThe maximum stress to which the structure is subjected.
Compared with the prior art, the invention has the beneficial effects that: the invention aims to fully consider the mounting structures of the whole machine, such as the motion connecting piece, the supported piece and the like, rather than the component structure which needs to be optimized, so that the optimized component structure can fully meet the design requirements of the machine tool on structural rigidity and light weight, and the optimal design of the whole machine tool is realized. The invention is not based on optimization under static state, and fully considers the optimization of each motion state and various working conditions of the machine tool, so that the optimized design index is more in line with the actual working state of the machine tool. In addition, an optimization algorithm of a plurality of groups of optimization targets and constraint combinations is adopted, an optimal optimization result can be selected on the premise of ensuring optimization, optimization compatibility is good, and the optimized structure is high in reliability.
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FIG. 1 is a schematic flow diagram of the process of the present invention.
FIG. 2 is a schematic view of the multi-condition topology optimization process based on the machine tool motion state.
FIG. 3 is a schematic diagram of a multi-condition integrated analysis of a finite element model according to the method of the present invention.
FIG. 4 is a schematic flow chart of the optimization of the shape and size of the machine tool based on multiple working conditions in the motion state.
Detailed Description
The present invention will be described in further detail with reference to the accompanying drawings and specific embodiments.
As shown in fig. 1, the method for optimally designing the structure of the key host component based on the working state of the machine tool comprises the following steps:
200, combining the optimized geometric model parameterization reconstruction of the topological configuration: and (5) carrying out model reconstruction of three-dimensional geometric modeling according to the conceptual design diagram extracted in the step 100, and carrying out parameterization on specific detail characteristics so as to achieve the purpose of changing the structural shape through size driving. The detailed characteristics comprise the position, the shape and the size of a certain lightening hole, the position and the thickness of a certain structural reinforcing support plate, the length and the section size of a certain cantilever and the like;
and 500, judging whether the evaluation result meets the design requirement, if so, finishing the optimization design, otherwise, returning to the step 300, pertinently modifying the corresponding detail characteristics, and performing further optimization of the shape and the size again until the evaluation result meets the design requirement.
Fig. 2 shows a multi-condition topology optimization process based on the motion state of the machine tool in step 100, which includes the following steps:
and 103, importing the three-dimensional models of the design domain and the simplified structural unit of the moving part 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 structural unit is complicated, mass points can be used instead of simplifying the model, the mass points are arranged on the gravity center of the moving part structural unit, parameters such as mass, mass inertia moment along each axis and the like are given to the mass points, and when the moving part structural unit moves, the position of the mass points changes along with the change of the position of the gravity center.
104, carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
105, carrying out multi-working-condition integrated analysis considering pose change on the finite element model, and calculating the structural volume vol, the key displacement disp 1-dispN and the key stress sigma which need to be referred to in the optimization processmaxCritical natural frequency f1To fNComprehensive softness C (w)1,w2,…,wN) And waiting for data, as shown in fig. 3, the multi-condition integrated analysis comprises: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; influence of cutting force on a target structure in a machining state, overall structure modal analysis considering connection of structural units of moving parts and the like;
for the topological optimization mathematical model, three groups of optimization targets and constraint combinations are optimized, which are respectively:
case 1: minimizing integrated compliance, constrained volume, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflRepresents the natural frequency of the l order;
case 2: maximizing first order natural frequency, constraining volume, critical displacement and comprehensive compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflRepresents the natural frequency of the l order;
case 3: minimizing volume, constraining complex compliance, critical displacements and critical frequencies
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cwFor comprehensive flexibility, comprehensively considering comprehensive flexibility of each working condition on behalf of a target structure, wherein kjThe weight of the jth working condition is taken up; v is the total volume of the target structure; dkRefers to the kth keypoint displacement; f. oflRepresents the ith orderThe natural frequency.
Aiming at the three groups of optimization targets and constraint combinations, two optimization algorithms are provided: one is to perform the operations in the order of Case1 to Case3, namely, first perform Case1, if the model converges, the optimization ends, if the model fails to converge, perform Case2, and similarly, if the model converges, the optimization ends, if the model fails to converge, perform Case 3; 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; the two methods can be used for carrying out optimization calculation by randomly selecting one method, not only can the solution of optimization be guaranteed, but also the optimal optimization result can be selected, the optimization compatibility is good, and the structure reliability after optimization is high.
Fig. 4 shows a schematic diagram of the optimization process 300 based on the multi-condition shape and size under the machine tool motion state, which includes the following steps:
303, carrying out multi-working-condition integrated analysis on the reconstruction model by considering pose change, and calculating relevant data of structure volume, key displacement, key stress, key natural frequency and comprehensive compliance; the multi-working-condition integrated analysis comprises the following steps: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; the analysis of the whole structure mode of the connection of the structure units of the moving parts is considered;
for the shape and size optimization mathematical model, two sets of optimization targets and constraint combinations of Case4 and Case5 are provided, wherein Case4 is suitable for the design target of light weight, Case5 is suitable for the design target of increasing strength and reducing structural deformation, and one set can be selected according to different design requirements for implementation, and the specific steps are as follows:
case 4: 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; djRefers to the jth keypoint displacement; f. ofkRepresents the k-th order natural frequency; sigmamaxThe maximum stress to which the structure is stressed;
case 5: minimizing dominant displacements, constraining structure volume, critical natural frequencies 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; djRefers to the jth keypoint displacement; f. ofkRepresents the k-th order natural frequency; sigmamaxThe 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 those skilled in the art can make various modifications in accordance with the principle of the present invention. Thus, modifications made in accordance with the principles of the present invention should be understood to fall within the scope of the present invention.
Claims (6)
1. The method for optimally designing the structure of the key host machine component based on the working state of the machine tool is characterized by comprising the following steps of:
A. based on the multi-working-condition topological optimization in the machine tool motion state;
B. combining the optimized geometric model parameterization reconstruction of the topological configuration;
C. optimizing the shape and size based on multiple working conditions under the motion state of the machine tool;
D. evaluating the production state based on the machining and assembling conditions of the machine tool;
E. judging whether the evaluation result meets the design requirement, if so, finishing the optimization design, otherwise, returning to the step C, and performing further optimization on the corresponding shape and size in a targeted manner;
the step A comprises the following steps of based on multi-working-condition topological optimization under the machine tool motion state:
A1. disassembling and simplifying the whole machine structure of the machine tool, extracting a target structure and a moving part structural unit supported by the target structure, and compressing all fine features and parts on the moving part structural unit, which do not influence the structural analysis result but increase the limited unit grid division time and the calculation time, wherein the fine features include but are not limited to threaded holes, chamfers and rounds;
A2. expanding the structure volume of the target structure according to the motion range and the non-interference space of the target structure, and filling all solid materials in the target structure to define the target structure as a design domain;
A3. importing the three-dimensional models of the design domain and the simplified moving part structure unit into finite element software, and respectively assigning corresponding material parameters, wherein the material parameters comprise but are not limited to elastic modulus, Poisson's ratio, density, thermal expansion coefficient and thermal conductivity coefficient;
A4. carrying out finite element mesh division and boundary condition loading on each three-dimensional model;
A5. performing multi-working condition integrated analysis considering pose change on the finite element model, and calculating relevant data of structure volume, key displacement, key stress, key natural frequency and comprehensive compliance which need to be referred to in the optimization process; wherein, the multi-condition integrated analysis includes but is not limited to: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; the modal analysis of the whole structure of the connection of the structural units of the moving parts is considered;
A6. establishing a topological optimization mathematical model, importing the data calculated in the step A5 into the topological optimization mathematical model, optimizing by using an optimization algorithm until the topological optimization mathematical model is converged, and extracting a conceptual design diagram of a target structure;
step B, combining the optimized geometric model parameterization reconstruction of the topological structure, namely performing three-dimensional geometric model reconstruction according to the conceptual design diagram extracted in the step A6, and parameterizing specific detail characteristics, wherein the detail characteristics comprise but are not limited to the position, the shape and the size of a lightening hole, the position and the thickness of a structure strengthening support plate, and the length and the section size of a cantilever;
step C is based on the optimization of the shape and the size of the multiple working conditions under the motion state of the machine tool, is further optimized aiming at local detailed characteristics, and comprises the following steps:
C1. defining materials for the reconstructed model, including but not limited to elastic modulus, poisson's ratio, density, thermal expansion coefficient and thermal conductivity coefficient;
C2. carrying out finite element mesh division and boundary condition loading on the reconstruction model;
C3. performing multi-working-condition integrated analysis considering pose change on the reconstructed model, and calculating relevant data of structure volume, key displacement, key stress, key natural frequency and comprehensive compliance; wherein, the multi-condition integrated analysis includes but is not limited to: dynamic and static analysis of the target structure when the moving part structural unit is in different poses; deformation analysis of the target structure under the inertia force when the moving part structural unit is in an acceleration and deceleration state; analyzing the thermal coupling of the target structure under the distribution of the temperature field of the whole machine; influence of cutting force on a target structure in a machining state; the modal analysis of the whole structure of the connection of the structural units of the moving parts 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 machining and assembling conditions of the machine tool, namely evaluating the production state of the model subjected to shape and size optimization based on the machining and assembling processes, and determining 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 structural unit of the moving part in step a3 is replaced by mass points disposed at the center of gravity of the structural unit of the moving part, and the mass points are assigned mass and parameters related to mass moment of inertia along each axis, and wherein the positions of the mass points vary with the positions of the center of gravity of the structural unit of the moving part when the structural unit of the moving part moves.
3. The method for optimally designing the structure of the key host computer component based on the working state of the machine tool as claimed in the claim 1 or 2, wherein in the step A6, three groups of optimization objectives and constraint combinations are provided for the topological optimization mathematical model, which are respectively:
case 1: minimizing integrated compliance, constrained volume, critical displacement and critical frequency
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cw is comprehensive flexibility, represents the comprehensive flexibility of the target structure under all working conditions, and kj is the weight occupied by the jth working condition; v is the total volume of the target structure; dk denotes the kth keypoint displacement; fl denotes the l-th order natural frequency;
case 2: maximizing first order natural frequency, constraining volume, critical displacement and comprehensive compliance
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cw is comprehensive flexibility, represents the comprehensive flexibility of the target structure under all working conditions, and kj is the weight occupied by the jth working condition; v is the total volume of the target structure; dk denotes the kth keypoint displacement; fl denotes the l-th order natural frequency;
case 3: minimizing volume, constraining complex compliance, critical displacements and critical frequencies
Wherein x is a design variable, namely the pseudo density of each analysis unit in a design domain; cw is comprehensive flexibility, represents the comprehensive flexibility of the target structure under all working conditions, and kj is the weight occupied by the jth working condition; v is the total volume of the target structure; dk denotes the kth keypoint displacement; fl denotes the l-th order natural frequency.
4. The method of claim 3, wherein the optimization algorithm in step A6 is performed according to the three sets of optimization objectives and constraint combinations in sequence, that is, Case1 is performed first, if the model converges, the optimization ends, if the model fails to converge, Case2 is performed, and similarly, if the model converges, the optimization ends, if the model fails to converge, Case3 is performed.
5. The method according to claim 3, wherein the optimization algorithm in step A6 is to calculate three sets of optimization objectives and constraint combinations simultaneously, and select a set of data with the best convergence as the optimization result.
6. The method of claim 1, wherein in step C4, two sets of optimization objectives and constraint combinations are provided for the shape and size optimization mathematical model, wherein Case4 is suitable for the design objective of light weight and Case5 is suitable for the design objective of increasing strength and reducing structural deformation, specifically as follows:
case 4: 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 denotes the jth keypoint displacement; fk denotes a kth order natural frequency; σ max is the maximum stress of the structure;
case 5: minimizing dominant displacements, constraining structure volume, critical natural frequencies 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 denotes the jth keypoint displacement; fk denotes a kth order natural frequency; σ max is the maximum stress to which the structure is subjected.
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| CN115270585A (en) * | 2022-09-28 | 2022-11-01 | 西北工业大学 | Collaborative optimization design method for machine tool body and ground feet and related product |
Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080281839A1 (en) * | 2007-05-08 | 2008-11-13 | Laser-Scan, Inc. | Three-Dimensional Topology Building Method and System |
| CN101537567A (en) * | 2009-04-28 | 2009-09-23 | 同济大学 | Modulization-based method for designing reconfigurable machine tool |
| CN102063548A (en) * | 2011-01-07 | 2011-05-18 | 西安交通大学 | Method for optimally designing dynamic property of complete machine tool |
| CN103390082A (en) * | 2013-07-22 | 2013-11-13 | 北京工业大学 | Steady optimal distributing method for geometric accuracy of multi-shaft machine tool |
| CN105243215A (en) * | 2015-10-12 | 2016-01-13 | 西安交通大学 | Motorized spindle structure optimization method based on parametric finite element model |
| CN106624845A (en) * | 2016-12-08 | 2017-05-10 | 廊坊精雕数控机床制造有限公司 | Numerically-controlled machine tool with translation interaction working tables |
| CN106844917A (en) * | 2017-01-10 | 2017-06-13 | 西北工业大学 | A kind of lathe base method of topological optimization design based on support reaction Variance Constraints |
| CN107145663A (en) * | 2017-05-04 | 2017-09-08 | 吉林大学 | Wheel multi-objective optimization design of power method |
| WO2018032668A1 (en) * | 2016-08-16 | 2018-02-22 | 北京新能源汽车股份有限公司 | Method and device for determining the position where structural adhesive is applied in automobile and method and device for applying structural adhesive in automobile |
| US20180210983A1 (en) * | 2016-06-16 | 2018-07-26 | South China University Of Technology | Design method of topology optimization for flexible hinge |
| CN108416158A (en) * | 2018-03-21 | 2018-08-17 | 江苏龙胜机床制造有限公司 | A kind of composite material lathe lathe bed optimization of inside structure design method |
| CN109359353A (en) * | 2018-09-29 | 2019-02-19 | 共享智能铸造产业创新中心有限公司 | A kind of machine pillar optimum structure design method based on topological optimization |
-
2019
- 2019-09-10 CN CN201910850880.4A patent/CN112487673B/en active Active
Patent Citations (12)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US20080281839A1 (en) * | 2007-05-08 | 2008-11-13 | Laser-Scan, Inc. | Three-Dimensional Topology Building Method and System |
| CN101537567A (en) * | 2009-04-28 | 2009-09-23 | 同济大学 | Modulization-based method for designing reconfigurable machine tool |
| CN102063548A (en) * | 2011-01-07 | 2011-05-18 | 西安交通大学 | Method for optimally designing dynamic property of complete machine tool |
| CN103390082A (en) * | 2013-07-22 | 2013-11-13 | 北京工业大学 | Steady optimal distributing method for geometric accuracy of multi-shaft machine tool |
| CN105243215A (en) * | 2015-10-12 | 2016-01-13 | 西安交通大学 | Motorized spindle structure optimization method based on parametric finite element model |
| US20180210983A1 (en) * | 2016-06-16 | 2018-07-26 | South China University Of Technology | Design method of topology optimization for flexible hinge |
| WO2018032668A1 (en) * | 2016-08-16 | 2018-02-22 | 北京新能源汽车股份有限公司 | Method and device for determining the position where structural adhesive is applied in automobile and method and device for applying structural adhesive in automobile |
| CN106624845A (en) * | 2016-12-08 | 2017-05-10 | 廊坊精雕数控机床制造有限公司 | Numerically-controlled machine tool with translation interaction working tables |
| CN106844917A (en) * | 2017-01-10 | 2017-06-13 | 西北工业大学 | A kind of lathe base method of topological optimization design based on support reaction Variance Constraints |
| CN107145663A (en) * | 2017-05-04 | 2017-09-08 | 吉林大学 | Wheel multi-objective optimization design of power method |
| CN108416158A (en) * | 2018-03-21 | 2018-08-17 | 江苏龙胜机床制造有限公司 | A kind of composite material lathe lathe bed optimization of inside structure design method |
| CN109359353A (en) * | 2018-09-29 | 2019-02-19 | 共享智能铸造产业创新中心有限公司 | A kind of machine pillar optimum structure design method based on topological optimization |
Non-Patent Citations (1)
| Title |
|---|
| 赵海鸣等: "基于拓扑优化与多目标优化的机床底座结构设置", 机械设计与研究, vol. 34, no. 4, pages 101 - 105 * |
Cited By (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN114880816A (en) * | 2022-07-11 | 2022-08-09 | 北京精雕科技集团有限公司 | Machine tool dynamics analysis model modeling method and device and electronic equipment |
| CN114880816B (en) * | 2022-07-11 | 2022-09-20 | 北京精雕科技集团有限公司 | Machine tool dynamics analysis model modeling method and device and electronic equipment |
| CN115270585A (en) * | 2022-09-28 | 2022-11-01 | 西北工业大学 | Collaborative optimization design method for machine tool body and ground feet and related product |
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