CN113127996A - Lightweight design method and structure of loader movable arm - Google Patents
Lightweight design method and structure of loader movable arm Download PDFInfo
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Abstract
The invention discloses a lightweight design method and a structure of a movable arm of a loader, which comprises the following steps: discretizing a geometric model; optimizing a transmission path based on the statics analysis of a structural finite element under multiple working conditions to obtain a lightweight design scheme meeting the requirements under the multiple working conditions; and (4) checking the size of the lightweight scheme in a rounding way and under multiple working conditions, calculating the rigidity and strength data of the comprehensive working conditions according to the weight coefficient of the working conditions, finishing result evaluation, and outputting the final lightweight scheme. The invention also discloses a structure form of the light movable arm of the loader, which comprises two movable arm plates which are symmetrically arranged, and a plurality of lightening holes are distributed on the movable arm plates. According to the invention, through optimizing, checking and evaluating the multi-working-condition force transmission path of the movable arm structure, reasonable layout of materials is realized, the structural weight is greatly reduced under the condition of ensuring the structural rigidity and the requirement of easy processing and manufacturing, the research and development period is shortened, the control flexibility of the whole machine is improved, and the labor intensity and the use cost of a user are reduced.
Description
Technical Field
The invention discloses a lightweight design method and a lightweight structure of a loader movable arm, and relates to the technical field of engineering machinery loaders.
Background
The loader is a shovel-loading transportation machine, is used for shoveling or transporting materials such as coal, ore, loose soil, corn and the like, and has the advantages of high operation speed, high efficiency, good maneuverability, light operation and the like, thereby becoming one of indispensable equipment in the existing mechanized engineering.
A typical loader operating device is mainly composed of a bucket, a boom, a link, a swing arm, a dump box cylinder, and a boom cylinder. The structure and performance of the working device directly affect the working size and performance parameters of the whole loader, so the rationality of the working device directly affects the production efficiency, the working load, the power and motion characteristics of the loader, the working effect under different working conditions, the working cycle time, the engine power and the like. The movable arm is used as a main structural support in the working device, and the performance of the movable arm directly influences the working device.
The research and development technology of the super-tonnage loader is mostly mastered in developed countries such as Europe and America, the loader in China still has a certain gap in the aspects of structure lightweight design, the design of a movable arm in the past is mostly realized by adopting an experience and analogy design method, the whole structure is generally widened and thickened in order to ensure the safety of the movable arm structure under the condition that proper strength and rigidity calculation and check are not taken as guide bases, and the direct consequence of the fact that the movable arm structure is heavy, the structural strength ratio is not coordinated, the weight of a working device is increased, the operation flexibility and the loading capacity of the loader are greatly influenced, the oil consumption is increased, the economic performance of the whole vehicle is reduced, and meanwhile, the environment is more polluted. Therefore, the design of boom structures, especially those of super-tonnage loaders, to reduce weight is imperative, and various manufacturers are constantly searching for ways to reduce weight.
In recent years, in order to meet increasingly severe global competition, foreign engineering machinery manufacturers further develop light weight, and mostly adopt high-strength wear-resistant materials to realize light weight of the structure, but the cost is greatly increased. The force transmission path optimization mainly comprises the steps of forming holes in the structure, removing unnecessary materials to optimize and configure the node connection relation, and achieving reasonable layout of the materials in a design area. The adjustment of the quantity and the position of the materials can ensure that the lightweight design is realized under the condition that the structural support position is subjected to applied load and the constraint conditions such as rigidity and strength are met, but the research on the lightweight design method under multiple working conditions is not common at present.
Disclosure of Invention
Aiming at the defects in the background technology, the invention provides a lightweight design method and a lightweight structure of a loader movable arm, which greatly reduce the weight of the structure and improve the control flexibility of the whole machine under the condition of ensuring the requirement of structural rigidity.
In order to achieve the purpose, the technical scheme adopted by the invention is as follows: a lightweight design method for a loader movable arm comprises the following steps:
the method comprises the following steps: discretizing a geometric model of the movable arm structure, and adopting hexahedral solid units to perform grid division on the movable arm structure to establish a finite element analysis model;
step two: carrying out finite element statics analysis on the initial structure of the movable arm structure under each working condition under the finite element analysis model, and acquiring the initial value of the stiffness index;
step three: iteration is carried out on the rigidity and the material volume ratio of the movable arm structure under each working condition on the basis of a finite element statics analysis result, a force transmission path is optimized, a light-weight design cloud picture of the movable arm structure meeting an optimization target is obtained, necessary materials on the force transmission path are reserved, unnecessary materials are removed, and a test light-weight movable arm structure is obtained;
step four: rounding and checking the test lightweight movable arm structure, performing finite element statics analysis again, calculating an optimized value of the stiffness strength index after lightweight, evaluating the optimized value and the initial value of the stiffness strength index, performing a fifth step if the stiffness strength index evaluation meets the requirement, and performing a third step if the stiffness strength index evaluation does not meet the requirement.
Step five: the lightweight boom structure of the output test is a final lightweight scheme.
Further, the finite element statics analysis specifically includes the following steps:
the equilibrium equation: KU ═ P
The geometric equation is as follows:
constitutive equation { σ } - [ D ] { epsilon }
The stress index of the movable arm structure is calculated by adopting an equivalent stress theory, and the principle is as follows:
wherein K is a stiffness matrix; u is a displacement matrix, and displacements x, y and z in 3 directions are respectively expressed by U, v and w; p is a load matrix; epsilon is structural strain, and 3 direction line strains are respectively epsilonx、εy、εzShear strain in three directions is tauxy、τxz、τyz(ii) a σ is structural stress, [ D ]]Is a matrix of elastic coefficients, the values of which are determined by the parameters of the material used, and the stress in the x, y and z directions is sigmax、σy、σz；
Maximum displacement of movable arm structure
Maximum stress s of movable arm structure is max { sigma }i}
Wherein i, j, k is 1,2 … … m, and m is the total number of structural nodes.
Further, the stiffness index includes: and the comprehensive rigidity is a summation value of the maximum displacement of the movable arm structure and the corresponding weight coefficient under the corresponding working condition, and the comprehensive strength is a summation value of the maximum stress of the movable arm structure and the corresponding weight coefficient under the corresponding working condition.
Further, a specific method for optimizing a force transmission path of the boom structure is as follows: the method comprises the steps that the material density of a movable arm plate is taken as a design variable, the structural strain energy of a movable arm structure is taken as a minimum objective function, a transmission path is optimized, and the movable arm structure material is removed under the conditions that the rigidity of the movable arm structure is the maximum and the displacement is the minimum;
the optimization equation is as follows:
lmin≤li≤1 i＝1,2,……，n
wherein a is a design variable vector and represents the relative density of the material of the solid unit of the movable arm plate; a isiIs the relative density of the ith physical unit;
n is the total number of the solid units of the movable arm plate;
c (a) is structural strain energy of the boom plate;
k0a cell stiffness matrix being a solid cell;
lidisplacement vector for ith entity unit;
li Ttranspose for displacement vector of ith entity unit;
(V0)iis the volume of the ith solid unit of material;
fVfor a given volume fraction ratio of material;
lmina positive real number much less than 1, representing the lower line of relative density of the unit material;
p is a penalty function.
Further, the working conditions include: a digging normal load working condition, a digging partial load working condition, a traction normal load working condition, a traction partial load working condition, a combined normal load working condition and a combined partial load working condition;
digging up a normal load working condition: when the loader works on the ground, the vertical external load is evenly distributed on the main cutting board,
digging unbalance loading working condition: when the loader works on the ground, the vertical external load is distributed on one side of the main cutter plate,
traction normal load working condition: when the loader works on the ground, the horizontal external load is uniformly distributed on the main cutting board,
traction unbalance loading working condition: when the loader works on the ground, the horizontal external load is distributed on one side of the main cutter plate,
the combined normal load working condition is as follows: when the loader works on the ground, the vertical external load and the horizontal external load are uniformly distributed on the main cutting board;
combined unbalance loading working condition: when the loader works on the ground, the vertical external load and the horizontal external load are distributed on one side of the main cutter plate.
Furthermore, the weight coefficients are set according to the application condition of the working condition, the sum of the weight coefficients is equal to 1, the weight coefficient of the excavation normal-load working condition is 0.05, the weight coefficient of the excavation unbalance-load working condition is 0.3, the weight coefficient of the traction normal-load working condition is 0.05, the weight coefficient of the traction unbalance-load working condition is 0.1, the weight coefficient of the combined normal-load working condition is 0.3, and the weight coefficient of the combined unbalance-load working condition is 0.2.
Further, the optimized value of the evaluation stiffness index is increased or decreased by less than 8% compared with the initial value.
A lightweight design structure of a loader movable arm comprises two movable arm plates which are symmetrically arranged and a seat beam for connecting the two movable arm plates, wherein symmetrical rocker arm lug seats are welded on the seat beam, a first hinge hole and a third hinge hole are respectively formed in two ends of each movable arm plate, and a second hinge hole is formed in an oil cylinder flange on each arm plate; the third lightening hole is positioned in the center of the connecting position of the movable arm plate and the seat beam, the first lightening hole, the second lightening hole and the fourth lightening hole are distributed on the left side and the right side of the third lightening hole, and the fourth lightening hole is close to the flange side of the oil cylinder; the first lightening hole is close to the third hinge hole side, and the second lightening hole is close to the seat beam side.
Furthermore, the third lightening hole is oval and concentric with the cross section of the seat beam; the first lightening holes are circular; the second lightening hole and the fourth lightening hole are both trapezoidal, two intersected edges of the second lightening hole and the fourth lightening hole are both subjected to fillet treatment, and the bottom edges of the trapezoidal holes are both close to the third lightening hole side; all the lightening holes penetrate through the whole movable arm in the thickness direction.
Has the advantages that: the loader movable arm lightweight design method and structure based on multiple working conditions can quickly and accurately optimize a force transmission path of a movable arm structure under multiple working conditions, realize reasonable layout of materials, greatly reduce the weight of the structure under the requirement of ensuring structural rigidity, improve the control flexibility of the whole loader, reduce the labor intensity and use cost of a user, solve the problem of excessively heavy design of an ultra-large tonnage loader movable arm, reduce the gap with international products, and improve the product competitiveness.
Drawings
FIG. 1 is a flow chart of the present invention;
FIG. 2 is a structural view of a lightweight front arm according to the present invention;
FIG. 3 shows the intentions of the working conditions of the present invention (a is a digging normal loading working condition, b is a digging partial loading working condition, c is a traction normal loading working condition, d is a traction partial loading working condition, e is a combined normal loading working condition, and f is a combined partial loading working condition);
FIG. 4 is a view of the boom structure of the present invention after weight reduction;
fig. 5 is a view of the rounded boom structure of the present invention.
Detailed Description
The following describes the embodiments in further detail with reference to the accompanying drawings. The following examples are only for illustrating the technical solutions of the present invention more clearly, and the protection scope of the present invention is not limited thereby.
In the embodiment shown in fig. 1-3, the weight-reducing design method for the loader boom adopts a boom plate material as Q550D, the yield limit of the boom plate material is 550MPa, and the maximum stress of the boom is 420MPa after the weight reduction is evaluated in a single working condition; the method comprises the following steps:
the method comprises the following steps: discretizing a geometric model of the movable arm structure, and adopting hexahedral solid units to perform grid division on the movable arm structure to establish a finite element analysis model;
step two: carrying out finite element statics analysis on the initial structure of the movable arm structure under each working condition under the finite element analysis model, and acquiring the initial value of the stiffness index;
step three: based on the finite element statics analysis result, carrying out force transmission path optimization on the movable arm structure under each working condition to obtain a test lightweight movable arm structure;
step four: rounding and checking the test lightweight movable arm structure, performing finite element statics analysis again, calculating an optimized value of the stiffness strength index after lightweight, evaluating the optimized value and the initial value of the stiffness strength index, performing a fifth step if the stiffness strength index evaluation meets the requirement, and performing a third step if the stiffness strength index evaluation does not meet the requirement.
Step five: the lightweight boom structure of the output test is a final lightweight scheme.
Further, the finite element statics analysis specifically includes the following steps:
the equilibrium equation: KU ═ P
The geometric equation is as follows:
constitutive equation { σ } - [ D ] { epsilon }
The stress index of the movable arm structure is calculated by adopting an equivalent stress theory, and the principle is as follows:
wherein K is a stiffness matrix; u is a displacement matrix, and displacements x, y and z in 3 directions are respectively expressed by U, v and w; p is a load matrix; ε is the structural strain of 3 squaresStrain to the line is respectively epsilonx、εy、εzShear strain in three directions is tauxy、τxz、τyz(ii) a σ is structural stress, [ D ]]Is a matrix of elastic coefficients, the values of which are determined by the parameters of the material used, and the stress in the x, y and z directions is sigmax、σy、σz，
Maximum displacement of movable arm structure
Maximum stress s of movable arm structure is max { sigma }i}
Wherein i, j, k is 1,2 … … m, and m is the total number of structural nodes.
The stiffness index includes: and the comprehensive rigidity is a summation value of the maximum displacement of the movable arm structure and the corresponding weight coefficient under the corresponding working condition, and the comprehensive strength is a summation value of the maximum stress of the movable arm structure and the corresponding weight coefficient under the corresponding working condition.
The specific method for optimizing the force transmission path of the movable arm structure comprises the following steps: the method comprises the steps that the material density of a movable arm plate is taken as a design variable, the structural strain energy of a movable arm structure is taken as a minimum objective function, a transmission path is optimized, and the movable arm structure material is removed under the conditions that the rigidity of the movable arm structure is the maximum and the displacement is the minimum;
the optimization equation is as follows:
lmin≤li≤1 i＝1,2,……，n
wherein a is a design variable vector and represents the relative density of the material of the solid unit of the movable arm plate, and aiIs the relative density of the ith physical unit;
n is the total number of the solid units of the movable arm plate;
c is the structural strain energy of the movable arm plate;
k0a cell stiffness matrix being a solid cell;
lidisplacement vector for ith entity unit;
li Ttranspose for displacement vector of ith entity unit;
V0)iis the volume of the ith solid unit of material;
fVfor a given volume fraction ratio of material;
lmina positive real number much less than 1, representing the lower line of relative density of the unit material;
p is a penalty function.
As shown in fig. 3, the working conditions include: a digging normal load working condition, a digging partial load working condition, a traction normal load working condition, a traction partial load working condition, a combined normal load working condition and a combined partial load working condition;
digging up a normal load working condition: when the loader works on the ground, the vertical external load is evenly distributed on the main cutting board,
digging unbalance loading working condition: when the loader works on the ground, the vertical external load is distributed on one side of the main cutter plate,
traction normal load working condition: when the loader works on the ground, the horizontal external load is uniformly distributed on the main cutting board,
traction unbalance loading working condition: when the loader works on the ground, the horizontal external load is distributed on one side of the main cutter plate,
the combined normal load working condition is as follows: when the loader works on the ground, the vertical external load and the horizontal external load are uniformly distributed on the main cutting board;
combined unbalance loading working condition: when the loader works on the ground, the vertical external load and the horizontal external load are distributed on one side of the main cutter plate. The weight coefficients are set according to the application condition of the working condition, the sum of the weight coefficients is equal to 1, and the weight coefficient w of the positive loading working condition is excavated1Is 0.05, and the weight coefficient w of the digging partial load working condition2Is 0.3, and the weight coefficient w of the traction normal load working condition3Is 0.05, and the weight coefficient w of the traction unbalance loading working condition4Is 0.1, and is combined with the weight coefficient w of the normal load working condition5Is 0.3, and is combined with the weight coefficient w of the unbalance loading working condition6Is 0.2.
Calculating the rigidity and strength index data of the steel plate,
combined stiffness D ═ w1 d1+w2 d2+w3 d3+w4 d4+w5 d5+w6 d6，
Combined strength S ═ w1 s1+w2 s2+w3 s3+w4 s4+w5 s5+w6 s6，
The maximum displacement of the movable arm structure under the corresponding working condition is taken from d 1-d 6, and the maximum stress of the movable arm structure under the corresponding working condition is taken from s 1-s 6;
the initial finite element statics analysis data are shown in table 1:
TABLE 1
Assuming initial structural material volume fraction ratio fVSetting the volume distribution ratio of the optimized material to be 0.4-0.5, selectively removing the part with lower material density shown in figure 4, rounding and checking to obtain a lightweight model structure shown in figure 5, and realizing the weight reduction of the structure by 10%;
the data of the finite element statics analysis is again shown in table 2:
TABLE 2
The results of the comprehensive rigidity and strength indexes of the lightweight forward and backward moving arm plate are compared and shown in the table 3:
| initial structure | Lightweight structure | Comparison of | |
| Combined stiffness | 44.25mm | 46.46mm | Increase by 5% |
| Combined strength | 277.75 | 271.9 | The reduction is 2 percent |
TABLE 3
As shown in Table 3, the comprehensive strength of the structure is reduced by 2% after the weight is reduced, the comprehensive rigidity of the structure is increased by 5%, and the weight of the structure is reduced by 10% while the structural strength and the structural rigidity are ensured.
As shown in fig. 5, the lightweight design structure of the loader movable arm comprises two movable arm plates 3 which are symmetrically arranged and a seat beam 4 for connecting the two movable arm plates 3, wherein symmetrical rocker arm ear seats 5 are welded on the seat beam 4, a first hinge hole 1 and a third hinge hole 6 are respectively arranged at two ends of each movable arm plate 3, a second hinge hole 11 is arranged on an oil cylinder flange 2 on each arm plate, and the first hinge hole 1, the second hinge hole 11 and the third hinge hole 6 are used for being connected with other structures to complete force transmission; four groups of symmetrical lightening holes, namely a first lightening hole 7, a second lightening hole 8, a third lightening hole 9 and a fourth lightening hole 20, are distributed on the movable armplate 3; the third lightening hole 9 is positioned at the center of the connecting position of the movable arm plate 3 and the seat beam 4, the first lightening hole 7, the second lightening hole 8 and the fourth lightening hole 10 are distributed on the left side and the right side of the third lightening hole 9, and the fourth lightening hole 10 is close to the side of the oil cylinder flange 2; the first lightening hole 7 is close to the third hinge hole 6 side, and the second lightening hole 8 is close to the seat beam 4 side.
Further, the third lightening holes 9 are oval and concentric with the section of the seat beam 4; the first lightening holes 7 are circular; the second lightening hole 8 and the fourth lightening hole 10 are both trapezoidal, two intersected edges of the second lightening hole and the fourth lightening hole are both subjected to fillet treatment, and the bottom edges of the trapezoidal shapes are both close to the third lightening hole 9 side; all the lightening holes penetrate through the whole movable arm in the thickness direction.
The loader movable arm lightweight design method and structure based on multiple working conditions can quickly and accurately optimize a force transmission path of a movable arm structure under multiple working conditions, realize reasonable layout of materials, greatly reduce the weight of the structure under the requirement of ensuring structural rigidity, improve the control flexibility of the whole loader, reduce the labor intensity and use cost of a user, solve the problem of excessively heavy design of an ultra-large tonnage loader movable arm, reduce the gap with international products, and improve the product competitiveness.
The above description is only a preferred embodiment of the present invention, and it should be noted that, for those skilled in the art, several modifications and variations can be made without departing from the technical principle of the present invention, and these modifications and variations should also be regarded as the protection scope of the present invention.
Claims (9)
1. A lightweight design method for a loader movable arm is characterized by comprising the following steps:
the method comprises the following steps: discretizing a geometric model of the movable arm structure, and adopting hexahedral solid units to perform grid division on the movable arm structure to establish a finite element analysis model;
step two: carrying out finite element statics analysis on the initial structure of the movable arm structure under each working condition under the finite element analysis model, and acquiring the initial value of the stiffness index;
step three: based on the finite element statics analysis result, carrying out force transmission path optimization on the movable arm structure under each working condition to obtain a test lightweight movable arm structure;
step four: rounding and checking the test lightweight movable arm structure, performing finite element statics analysis again, calculating an optimized value of the stiffness strength index after lightweight, evaluating the optimized value and the initial value of the stiffness strength index, performing a fifth step if the stiffness strength index evaluation meets the requirement, and performing a third step if the stiffness strength index evaluation does not meet the requirement.
Step five: the lightweight boom structure of the output test is a final lightweight scheme.
2. The method for designing the loader arm for lightening the weight of the loader arm as claimed in claim 1, wherein the finite element statics analysis comprises the following steps:
the equilibrium equation: KU ═ P
The geometric equation is as follows:
constitutive equation { σ } - [ D ] { epsilon }
The stress index of the movable arm structure is calculated by adopting an equivalent stress theory, and the principle is as follows:
wherein K is a stiffness matrix; u is a displacement matrix, and displacements x, y and z in 3 directions are respectively expressed by U, v and w; p is a load matrix; epsilon is structural strain, and 3 direction line strains are respectively epsilonx、εy、εzShear strain in three directions is tauxy、τxz、τyz(ii) a σ is structural stress, [ D ]]A matrix of elastic coefficients whose values depend on the material parameters used; stress in x, y and z directions is sigmax、σy、σz；
Maximum displacement of movable arm structure
Maximum stress s of movable arm structure is max { sigma }i}，
Wherein i, j, k is 1,2 … … m, and m is the total number of structural nodes.
3. The method for designing a loader arm with reduced weight according to claim 2, wherein the stiffness index includes: and the comprehensive rigidity is a summation value of the maximum displacement of the movable arm structure and the corresponding weight coefficient under the corresponding working condition, and the comprehensive strength is a summation value of the maximum stress of the movable arm structure and the corresponding weight coefficient under the corresponding working condition.
4. The lightweight design method for the movable arm of the loader as claimed in claim 1, wherein the specific method for optimizing the force transmission path of the movable arm structure is as follows: the method comprises the steps that the material density of a movable arm plate is taken as a design variable, the structural strain energy of a movable arm structure is taken as a minimum objective function, a transmission path is optimized, and the movable arm structure material is removed under the conditions that the rigidity of the movable arm structure is the maximum and the displacement is the minimum;
the optimization equation is as follows:
lmin≤li≤1 i＝1,2,……，n
wherein a is a design variable vector and represents the relative density of the material of the solid unit of the movable arm plate; a isiIs the relative density of the ith physical unit;
n is the total number of the solid units of the movable arm plate;
c (a) is structural strain energy of the boom plate;
k0a cell stiffness matrix being a solid cell;
lidisplacement vector for ith entity unit;
li Ttranspose for displacement vector of ith entity unit;
(V0)iis the volume of the ith solid unit of material;
fVfor a given volume fraction ratio of material;
lmina positive real number much less than 1, representing the lower line of relative density of the unit material;
p is a penalty function.
5. The lightweight design method for the loader moving arm as claimed in claim 1, wherein the working conditions include: a digging normal load working condition, a digging partial load working condition, a traction normal load working condition, a traction partial load working condition, a combined normal load working condition and a combined partial load working condition;
digging up a normal load working condition: when the loader works on the ground, the vertical external load is evenly distributed on the main cutting board,
digging unbalance loading working condition: when the loader works on the ground, the vertical external load is distributed on one side of the main cutter plate,
traction normal load working condition: when the loader works on the ground, the horizontal external load is uniformly distributed on the main cutting board,
traction unbalance loading working condition: when the loader works on the ground, the horizontal external load is distributed on one side of the main cutter plate,
the combined normal load working condition is as follows: when the loader works on the ground, the vertical external load and the horizontal external load are uniformly distributed on the main cutting board;
combined unbalance loading working condition: when the loader works on the ground, the vertical external load and the horizontal external load are distributed on one side of the main cutter plate.
6. The lightweight design method for the loader moving arm as recited in claim 3, wherein the weighting factors are set according to the operating conditions, the sum of the weighting factors is equal to 1, the weighting factor for the excavation normal load condition is 0.05, the weighting factor for the excavation unbalance loading condition is 0.3, the weighting factor for the traction normal load condition is 0.05, the weighting factor for the traction unbalance loading condition is 0.1, the weighting factor for the combined normal load condition is 0.3, and the weighting factor for the combined unbalance loading condition is 0.2.
7. The method of claim 1, wherein the ratio of increase or decrease of the optimized value of the estimated stiffness index from the initial value is less than 8%.
8. A lightweight design structure of a loader arm based on the lightweight design method of the loader arm in claims 1-7 comprises two movable arm plates which are symmetrically arranged and a seat beam which is connected with the two movable arm plates, wherein symmetrical rocker arm lug seats are welded on the seat beam, a first hinge hole and a third hinge hole are respectively arranged at two ends of each movable arm plate, and a second hinge hole is arranged on an oil cylinder flange on each arm plate; the third lightening hole is positioned in the center of the connecting position of the movable arm plate and the seat beam, the first lightening hole, the second lightening hole and the fourth lightening hole are distributed on the left side and the right side of the third lightening hole, and the fourth lightening hole is close to the flange side of the oil cylinder; the first lightening hole is close to the third hinge hole side, and the second lightening hole is close to the seat beam side.
9. The loader arm lightweight design structure of claim 8, characterized in that: the third lightening hole is oval and concentric with the section of the seat beam; the first lightening holes are circular; the second lightening hole and the fourth lightening hole are both trapezoidal, two intersected edges of the second lightening hole and the fourth lightening hole are both subjected to fillet treatment, and the bottom edges of the trapezoidal holes are both close to the third lightening hole side.
Priority Applications (1)
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