# 6m圓盤造球機機架輕量化設計Lightweight Design of 6m Disc Pelletizer Frame

DOI: 10.12677/MET.2020.93025, PDF, HTML, XML, 下載: 22  瀏覽: 68

Abstract: In order to reduce the weight of the disc pelletizer and save the manufacturing cost, this paper puts forward an idea of lightweight design of the frame. In this paper, the stress of the whole and the frame (bracket and base) of the pelletizer is analyzed by using ANSYS workbench as the platform. It is concluded that the large redundancy in the frame design of the pelletizer is the main reason for the increase of the weight of the equipment. Therefore, with the goal of reducing the weight of the rack, the lightweight design of the rack is carried out, and the optimized frame structure is compared. the results show that the maximum equivalent stress is reduced by 10%, the static stiff-ness of weak parts is increased by 10%, and the equipment mass is reduced by 1000 kg at the same time, which not only achieves the goal of lightweight, but also improves its static stiffness and strength, effectively reduces the weight of equipment and manufacturing cost, and improves performance. It provides theoretical support and design reference for the design of the frame base in the future.

1. 引言

2. 造球機整體及主要部件剛度強度分析

Figure 2. Overall strain and population stress diagram

$\left[\sigma \right]=\frac{{\sigma }_{s}}{n}$

$\left[\sigma \right]=\frac{{\sigma }_{s}}{n}=\frac{235\text{MPa}}{1.5}=156.7\text{MPa}$

1) 支架強度和剛度分析

Figure 3. Overall deformation and strain diagram of the stent

2) 底座強度和剛度分析

Figure 4. Base strain and stress

3. 造球機機架結構的輕量化設計

3.1. 優化數學模型及方法

1) 設計變量

$X=\left[P1,P2,P3,P4,P5\right]$

2) 約束條件

$P6\le {S}_{MAX}\le \left[\sigma \right]=156.7$

3) 目標函數

$P7=M=f\left[P1,P2,P3,P4,P5\right]$

$X=\left[P1,P2,P3,P4,P5\right]$

${S}_{MAX}\le \left[\sigma \right]=195.84$

$M=\mathrm{min}f\left[P1,P2,P3,P4,P5\right]$

3.2. 優化設計方法

3.3. 優化結果分析

Figure 5. The broken line diagram of input and output parameters at each design point and sensitive response of design variables to mass

Figure 6. Sensitive response of design variables to maximum deformation

Figure 7. Relationship between maximum deformation quantity and quality

Figure 8. Optimizing the optimal result

Table 1. Parameters of four different types of I-beam

Figure 9. Deformation and stress of I-beam No. 3

Figure 10. Strength stiffness after optimization

Table 2. Parameter changes before and after optimization

4. 結論

1) 得出優化后造球機最大應力集中處還是在圓盤的支撐橫軸處，優化前最大應力為187.22 Mp，安全系數較低，優化后最大應力為147.81 MPa，與優化前強度提高了21%，小于許用應力156.7 MPa，說明優化結果對支撐橫軸進行了加強，提高了它的剛度強度；

2) 經過優化前后參數對比，在滿足安全應力范圍下，得到優化之后機架的質量減小了1429 kg，占整個機架質量的13.6%，減輕質量提高經濟性的效果還是顯著的；

3) 本文中的機架優化結果能夠滿足圓盤造球機的工作要求，能夠快速的得到機架的輕量化的目標，為以后機架底座的設計提供了理論支持；對圓盤造球機的設計開發、制造和使用具有現實意義。

NOTES

*通訊作者。

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