CN109766591B - Lightweight design method for crawler-type chariot movable cross beam - Google Patents
Lightweight design method for crawler-type chariot movable cross beam Download PDFInfo
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Abstract
The invention relates to a lightweight design method for a crawler-type war chariot movable cross beam, and belongs to the technical field of vehicle structure design. The invention provides a lightweight design method for a crawler-type war chariot movable cross beam, which can quickly realize lightweight design of the movable cross beam according to a design process, realize optimal matching of five design factors of cross beam mass, section size, cross beam material, strength and rigidity, and provide the most important reference for the movable cross beam in the stage of scheme design and engineering design.
Description
Technical Field
The invention belongs to the technical field of vehicle structure design, and particularly relates to a lightweight design method for a crawler-type war chariot movable cross beam.
Background
The movable cross beam is an important component of a crawler-type war chariot body structure and is one of main bearing parts of the whole vehicle structure. The crawler-type war chariot is divided into three parts, namely a power cabin, a fighting cabin and a passenger cabin. The power system, the transmission system, the auxiliary system and the like are loaded in the power cabin, and at present, the power transmission of most vehicles is integrated, so that a considerable space is occupied. Because of the requirements of installation, maintenance and repair of the power cabin, an opening needs to be reserved on the upper part of the power cabin, and the power transmission integrated hoisting is realized, so that the opening of the power cabin is very large. However, the power cabin cannot be designed with a cover plate as large as the opening, so that the weight of the chariot is increased, and the chariot is more inconvenient to disassemble, assemble and maintain at ordinary times. Therefore, in the design of the power compartment cover, the cover is usually divided into pieces so that the weight of each piece is within the range that can be borne by maintenance personnel. Therefore, a beam structure is required to be designed between each cover plate to support the weight of the cover plates. On the premise that the beam structure needs to meet the bearing requirement, the following conditions must be met: (1) Can be detached at any time so as to facilitate the hoisting of the power transmission device. (2) A sealing structure is required to be designed between the cross beam and the cover plate to prevent rainwater from permeating into the power cabin. (3) The crossbeam needs to satisfy the rigidity intensity requirement, prevents on the one hand to take place fatigue failure, and on the other hand prevents to take place plastic deformation under the dynamic load effect, makes to produce the clearance between apron and the crossbeam, influences the leakproofness of apron. (4) The design of the beam needs to meet the installation requirement of the whole vehicle, and the beam cannot occupy the space of other subsystems or parts. (5) The overall design places severe constraints on the weight of the mobile transverse beam. Therefore, the contradiction between high strength and light weight is a major problem in the structural design of the current movable cross beam.
The design method of the movable beam integrating the installation requirement, the strength design requirement and the sealing requirement is expected to solve the problem. The design method fully utilizes the strength characteristics of the beam structure in different bearing, different materials and different section sizes, and can greatly reduce the structure quality on the basis of not reducing the strength of the whole structure and not influencing the structure installation. The core technology of the structure design method is based on multi-objective multi-parameter optimization technology, and finally, the optimal matching of five factors including beam mass, section size, beam material, strength and rigidity is achieved.
Based on the requirements, the lightweight design of the movable beam structure of the existing crawler-type chariot has the following characteristics:
1. the movable beam structure is designed into an integrated structure as much as possible. Therefore, the rigidity and the strength of the whole structure can be increased, and a support upright post between the bottom of the power cabin and the cross beam is not required to be designed at the middle connecting part, so that the space in the cabin is occupied. The transitional connection structure between the cross beams is designed, and only the bolt fixing is carried out at the boundary point of the cross beam structure, so that the disassembly and the assembly are convenient, and the whole mass of the cross beam is reduced on the premise of meeting the rigidity and the strength.
2. The beam structure is made of the material which is produced in batches at present;
3. the beam structure adopts a finite element model when the rigidity and the strength are checked, the shell unit is mainly used as the finite element model, the node unit is reduced, the section size and the material property can be set as the design variables, and the multi-objective optimization is convenient to carry out subsequently.
4. Automatically completing optimization calculation by using professional and mature optimization software;
5. the whole design process has high modeling speed, convenient modification and low calculation time consumption.
Based on the characteristics, a lightweight design method for the crawler-type war chariot movable cross beam is required, the lightweight design of the movable cross beam can be quickly realized according to a design process, and the optimal matching of five design factors of the mass, the section size, the cross beam material, the strength and the rigidity of the cross beam is realized.
Disclosure of Invention
Technical problem to be solved
The technical problem to be solved by the invention is as follows: how to design a lightweight design method for a crawler-type war chariot movable cross beam, and the optimal matching of five design factors of the mass, the section size, the cross beam material, the strength and the rigidity of the cross beam is realized.
(II) technical scheme
In order to solve the technical problem, the invention provides a lightweight design method for a crawler-type chariot movable cross beam, which comprises the following steps:
(1) Establishing initial three-dimensional model of crawler-type chariot movable beam structure
According to the overall arrangement, an initial three-dimensional model of the movable cross beam structure is constructed according to the opening requirements and the thickness size of cover plates, the model comprises a basic structure model and a reinforcing structure model, bolt holes are reserved in the left side and the right side of the two ends of the basic model, and bolt holes are reserved in the top of the basic model and used for tightly installing the cover plates on the left side and the right side of a pressing plate;
(2) Establishing a shell unit finite element model of the movable beam according to the constructed beam structure initial three-dimensional model
The shell unit adopts a four-node midpoint-free mathematical model, represents the section size in a parameterization mode, adopts seven parameters of A, B, C, D, E, F and G to represent section size information and form a script file, wherein the seven parameters of A, B, C, D, E, F and G sequentially represent the middle thickness of a foundation structure, the height of two sides of the foundation structure, the thickness of two sides of the foundation structure, the width of two sides of the foundation structure, the internal width of a reinforced structure, the external height of the reinforced structure and the external width of the reinforced structure;
(3) Establishing solution model of movable cross beam
According to the established shell unit finite element model of the movable cross beam, load and constraint are applied according to actual working conditions, the positions of a plurality of fixed connecting bolts of the movable cross beam are constrained based on vertical impact working conditions, full constraint with 6 degrees of freedom is applied, meanwhile, 5 times of weight load of a cover plate is applied to act on the cross beam in a vertically and uniformly distributed mode, and the maximum equivalent stress value sigma is extracted max1 (ii) a Based on the working condition of braking impact load, the positions of a plurality of fixed connecting bolts of a movable cross beam are restrained, full restraint with 6 degrees of freedom is applied, meanwhile, 1.5 times of weight of horizontal load of a cover plate is applied to act on the cross beam in a concentrated mode, 1 time of weight of load acts on the cross beam in a vertically and uniformly distributed mode, and the maximum equivalent stress value sigma is extracted max2 (ii) a According to the fatigue stress limit test value of the movable beam, ensuring the two values sigma max1 、σ max2 Are all less than the fatigue yield limit, yield sigma, of the material used for the movable cross-member s A certain percentage of (A);
(4) Parametric sensitivity analysis
Sensitivity analysis is carried out on seven parameters of the sections A, B, C, D, E, F and G of the movable cross beam to obtain 7 parameters to the maximum equivalent stress sigma max1 And σ max2 The 7 parameters are sorted according to the sensitivity, the parameters with the sensitivity less than 5 percent are not listed as optimization variables, and the 7 parameters with the sensitivity more than or equal to 5 percent are set;
(5) Establishing a movable cross beam optimization model
Constructing an optimization model of the movable beam in the iSight software, taking the total mass m of the movable beam as an optimization target and seven parameters A, B, C, D, E, F and GNumber and four material parameter densities rho, elastic modulus E 'and Poisson's ratio gamma are used as optimization variables, and maximum stress sigma under vibration impact and braking impact is used max Maximum deformation S max Establishing an optimization model for constraint conditions, wherein the optimization model is as follows:
elements in the rho, E' and gamma four matrixes respectively represent the corresponding density, elastic modulus and Poisson ratio when the movable beam structure adopts four different materials;
(6) Optimization analysis
Carrying out optimization solution calculation according to the optimization model and initial input, screening three groups of suitable matching schemes by a vehicle body structure designer according to a multi-objective optimization result, then determining a group of optimal matching schemes, reestablishing a three-dimensional model of the movable cross beam based on the schemes, then carrying out finite element rigidity intensity check on the movable cross beam and the mounting bolts, and verifying the accuracy of optimization analysis; if the error exists, the initial values are endowed to the seven parameters of the movable cross beam again, the initial three-dimensional model is changed, and if the error does not exist, the engineering design of the movable cross beam is continued.
Preferably, the method further comprises the following steps after the optimization analysis: and (3) repeating the steps (1) to (6) for the movable cross beams with various cross-sectional shapes, then carrying out comprehensive comparison, and when the overall arrangement or the size change of the vehicle body is large, carrying out initial design on the movable cross beams again, and repeating the steps (1) to (6) as well.
Preferably, in a first step, a sealing strip is applied between the cover plate and the cross-member.
Preferably, the cross-sectional dimension information of the movable beam obtained in the second step is as follows:
TABLE 1
Preferably, in the fifth step, elements in the ρ, E', and γ four matrices respectively represent density, elastic modulus, and poisson ratio corresponding to the movable beam structure made of four different materials, i.e., high-strength steel, aluminum alloy, titanium alloy, and magnesium alloy.
Preferably, the fatigue yield limit is the yield limit σ s 75% of the total.
(III) advantageous effects
The invention provides a lightweight design method for a crawler-type war chariot movable cross beam, which can quickly realize lightweight design of the movable cross beam according to a design process, realize optimal matching of five design factors of cross beam mass, section size, cross beam material, strength and rigidity, and provide the most important reference for the movable cross beam in the stage of scheme design and engineering design.
Drawings
FIG. 1 is a flow chart of a lightweight design of a crawler vehicle power compartment movable cross beam of the present invention;
FIG. 2 is a schematic view of the initial three-dimensional model of the movable beam of the present invention.
Detailed Description
In order to make the objects, contents, and advantages of the present invention clearer, the following detailed description of the embodiments of the present invention will be made in conjunction with the accompanying drawings and examples.
As shown in figure 1, the invention provides a lightweight design method for a crawler-type war chariot movable cross beam, which comprises the following steps:
(1) Establishing initial three-dimensional model of crawler-type chariot movable beam structure
According to the overall arrangement, an initial three-dimensional model of the movable cross beam structure is constructed according to the opening requirement and the thickness size of the cover plate, the movable cross beam model comprises a basic structure model and a reinforcing structure model, bolt holes are reserved in the left side and the right side of the two ends of the basic structure model as shown in figure 2, and the mounting and fixing requirements of the cross beam are met. Bolt holes are reserved in the top of the basic model and used for installing cover plates on the left side and the right side of the tight installation pressing plate, sealing rubber strips are pasted between the cover plates and the cross beams, rainwater infiltration is prevented, and meanwhile fatigue damage and plastic deformation of the cross beams are prevented due to vibration generated in gaps.
(2) Constructing a finite element model of a movable beam with shell units as main parts
And establishing a shell unit finite element model of the movable cross beam according to the established initial movable cross beam three-dimensional model. In order to improve the calculation efficiency, the shell unit adopts a four-node midpoint-free mathematical model, the section size is represented in a parameterization mode, as shown in fig. 2, seven parameters A, B, C, D, E, F and G are adopted to represent section size information, a script file is formed, and subsequent design optimization is facilitated, wherein the seven parameters A, B, C, D, E, F and G sequentially represent the middle thickness of a foundation structure, the heights of two sides of the foundation structure, the thicknesses of two sides of the foundation structure, the widths of two sides of the foundation structure, the inner width of a reinforcing structure, the outer height of the reinforcing structure and the outer width of the reinforcing structure. As shown in table 1.
TABLE 1 Movable Cross-Beam section dimension information
(3) Establishing solution model of movable cross beam
According to the established finite element initial model of the movable cross beam, applying load and constraint according to actual working conditions, based on vertical impact working conditions, constraining the positions of a plurality of fixed connecting bolts of the movable cross beam, applying full constraint with 6 degrees of freedom, simultaneously applying 5 times of weight load of a cover plate to vertically and uniformly act on the cross beam, and extracting a maximum equivalent stress value sigma max1 . Based on the working condition of braking impact load, the positions of a plurality of fixed connecting bolts of a movable cross beam are restrained, full restraint with 6 degrees of freedom is applied, meanwhile, 1.5 times of weight of horizontal load of a cover plate is applied to be intensively acted on the cross beam, 1 time of weight of load is vertically and uniformly acted on the cross beam, and the maximum equivalent stress value sigma is extracted max2 . According to the fatigue stress limit test value of the movable beam, ensuring the two values sigma max1 、σ max2 Are all less than the fatigue yield limit (i.e., yield limit σ) of the material used for the movable cross member s 75% of).
(4) Parametric sensitivity analysis
Sensitivity analysis is carried out on seven parameters of the sections A, B, C, D, E, F and G of the movable cross beam to obtain 7 parameters to the maximum equivalent stress sigma max1 And σ max2 The 7 parameters are sorted according to the sensitivity.
(5) Establishing movable cross beam optimization model
Constructing an optimization model of the movable beam in iSight software, taking the total mass m of the movable beam as an optimization target, taking seven parameters of A, B, C, D, E, F and G and four material parameters including density rho, elastic modulus E' and Poisson ratio gamma as optimization variables, and taking the maximum stress sigma under vibration impact and braking impact as well as max Maximum deformation S max For constraint conditions, an optimization model is established, which is shown as the following formula.
Elements in the rho, E' and gamma matrixes in the above formula respectively represent the corresponding density, elastic modulus and Poisson ratio when the movable beam structure adopts four different materials, namely high-strength steel, aluminum alloy, titanium alloy and magnesium alloy.
(6) Optimization analysis
And performing optimization solution calculation according to the optimization model and the initial input, wherein the optimization model of the movable cross beam can properly reduce optimization targets and optimization parameters so as to accelerate the optimization speed. And finally, according to a multi-objective optimization result, a vehicle body structure designer screens out three groups of suitable matching schemes, then synthesizes other factors such as overall vehicle requirements, overall arrangement, process realization, economic cost and the like, determines a group of optimal matching schemes, reestablishes a three-dimensional model of the movable cross beam based on the schemes, and then checks the finite element rigidity strength of the movable cross beam and the mounting bolts, and verifies the accuracy of optimization analysis. If the error exists, the initial values are endowed to the seven parameters of the movable cross beam again, the initial three-dimensional model is changed, and if the error does not exist, the engineering design of the movable cross beam can be continued.
(7) Preference of the protocol
And (3) for the movable cross beam with various cross section shapes, repeating the steps (1) to (6), and then carrying out comprehensive comparison and weighing analysis. If the overall arrangement or the size of the vehicle body is greatly changed, the movable cross beam needs to be designed again, and the steps (1) to (6) are repeated.
The implementation steps of the method are briefly described below for the movable cross beam of the power compartment of a certain tracked vehicle.
(1) An initial three-dimensional model of the movable beam is designed, and the section size adopts the past design parameters, as shown in figure 2.
(2) Then, a finite element model with shell elements as main parts is established, and three variables of the cross section size, the thickness and the material property of the beam are parameterized.
(3) And establishing two analysis working conditions of vertical impact and braking impact, analyzing, and storing a result file.
(4) And carrying out sensitivity analysis on the parameterized variables according to the result, and sequencing according to the size.
(5) And establishing an optimization model in the iSight software, establishing the optimization model by taking the minimum mass and minimum deformation of the vehicle body as targets, section parameters and material parameters as design variables and the maximum stress in the impact and brake analysis working conditions as constraints, and solving and calculating.
(6) Three schemes which accord with design and constraint are selected, and other factors are integrated to carry out balance analysis and decision.
(7) And carrying out rigidity and strength verification on the selected matching scheme.
And if the requirements are met, carrying out engineering design according to the scheme.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, it is possible to make various improvements and modifications without departing from the technical principle of the present invention, and those improvements and modifications should be considered as the protection scope of the present invention.
Claims (6)
1. A lightweight design method for a crawler-type war chariot movable cross beam is characterized by comprising the following steps:
(1) Establishing initial three-dimensional model of crawler-type chariot movable beam structure
According to the overall arrangement, an initial three-dimensional model of the movable cross beam structure is constructed according to the opening requirements and the thickness size of cover plates, the model comprises a basic structure model and a reinforcing structure model, bolt holes are reserved in the left side and the right side of the two ends of the basic model, and bolt holes are reserved in the top of the basic model and used for tightly installing the cover plates on the left side and the right side of a pressing plate;
(2) Establishing a shell unit finite element model of the movable beam according to the constructed beam structure initial three-dimensional model
The shell unit adopts a four-node midpoint-free mathematical model, represents the section size in a parameterization mode, adopts seven parameters of A, B, C, D, E, F and G to represent section size information and form a script file, wherein the seven parameters of A, B, C, D, E, F and G sequentially represent the middle thickness of a foundation structure, the height of two sides of the foundation structure, the thickness of two sides of the foundation structure, the width of two sides of the foundation structure, the internal width of a reinforced structure, the external height of the reinforced structure and the external width of the reinforced structure;
(3) Establishing solution model of movable cross beam
According to the established shell unit finite element model of the movable cross beam, load and constraint are applied according to actual working conditions, the positions of a plurality of fixed connecting bolts of the movable cross beam are constrained based on vertical impact working conditions, full constraint with 6 degrees of freedom is applied, meanwhile, 5 times of weight load of a cover plate is applied to act on the cross beam in a vertically and uniformly distributed mode, and the maximum equivalent stress value sigma is extracted max1 (ii) a Based on the working condition of braking impact load, the positions of a plurality of fixed connecting bolts of a movable cross beam are restrained, full restraint with 6 degrees of freedom is applied, meanwhile, 1.5 times of weight of horizontal load of a cover plate is applied to be intensively acted on the cross beam, 1 time of weight of load is vertically and uniformly acted on the cross beam, and the maximum equivalent stress value sigma is extracted max2 (ii) a According to the fatigue stress limit test value of the movable beam, ensuring the two values sigma max1 、σ max2 Are all less than the fatigue yield limit, yield sigma, of the material used for the movable cross-member s A certain percentage of (A);
(4) Parametric sensitivity analysis
Seven parameters of the cross sections A, B, C, D, E, F and G of the movable cross beam are subjected to sensitivity analysis to obtain 7 parameters to the maximum equivalent stress sigma max1 And σ max2 The 7 parameters are sorted according to the sensitivity, forThe parameters with the sensitivity less than 5 percent are not listed as optimization variables, and the sensitivity of 7 parameters is set to be more than or equal to 5 percent;
(5) Establishing movable cross beam optimization model
Constructing an optimization model of the movable beam in iSight software, taking the total mass m of the movable beam as an optimization target, taking seven parameters of A, B, C, D, E, F and G and four material parameters including density rho, elastic modulus E' and Poisson ratio gamma as optimization variables, and taking the maximum stress sigma under vibration impact and braking impact as well as max Maximum deformation S max Establishing an optimization model for constraint conditions, wherein the optimization model is as follows:
elements in the rho, E' and gamma four matrixes respectively represent the corresponding density, elastic modulus and Poisson ratio when the movable beam structure adopts four different materials;
(6) Optimization analysis
Carrying out optimization solution calculation according to the optimization model and initial input, screening out three groups of suitable matching schemes by a vehicle body structure designer according to a multi-objective optimization result, then determining a group of optimal matching schemes, reestablishing a three-dimensional model of the movable cross beam based on the schemes, then carrying out finite element rigidity strength check on the movable cross beam and the mounting bolts, and verifying the accuracy of optimization analysis; if the error exists, the initial values are endowed to the seven parameters of the movable cross beam again, the initial three-dimensional model is changed, and if the error does not exist, the engineering design of the movable cross beam is continued.
2. The method of claim 1, further comprising, after the optimization analysis, the steps of: and (3) repeating the steps (1) to (6) for the movable cross beams with various cross-sectional shapes, then carrying out comprehensive comparison, and when the overall arrangement or the size change of the vehicle body is large, carrying out initial design on the movable cross beams again, and repeating the steps (1) to (6) as well.
3. A method according to claim 1, characterized in that in a first step a sealing strip is applied between the cover and the cross-member.
4. The method according to claim 1, wherein the information on the cross-sectional size of the movable beam obtained in the second step is as follows:
TABLE 1
5. The method of claim 4, wherein in the fifth step, the elements in the four matrixes ρ, E' and γ represent the density, the elastic modulus and the Poisson ratio of the movable beam structure respectively when four different materials, namely high-strength steel, aluminum alloy, titanium alloy and magnesium alloy, are adopted.
6. The method of claim 1, wherein the fatigue yield limit is yield limit σ s 75% of the total weight.
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| CN1342578A (en) * | 2000-08-15 | 2002-04-03 | 株式会社小松制作所 | Endless-track type building machinery vehicle frame structure |
| JP2004017922A (en) * | 2002-06-20 | 2004-01-22 | Yanmar Agricult Equip Co Ltd | Travel vehicle |
| JP2004017923A (en) * | 2002-06-20 | 2004-01-22 | Yanmar Agricult Equip Co Ltd | Travel vehicle |
| CN101252995A (en) * | 2005-08-29 | 2008-08-27 | 株式会社小松制作所 | Jaw crusher and self-traveling crusher |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| CN1342578A (en) * | 2000-08-15 | 2002-04-03 | 株式会社小松制作所 | Endless-track type building machinery vehicle frame structure |
| JP2004017922A (en) * | 2002-06-20 | 2004-01-22 | Yanmar Agricult Equip Co Ltd | Travel vehicle |
| JP2004017923A (en) * | 2002-06-20 | 2004-01-22 | Yanmar Agricult Equip Co Ltd | Travel vehicle |
| CN101252995A (en) * | 2005-08-29 | 2008-08-27 | 株式会社小松制作所 | Jaw crusher and self-traveling crusher |
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