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Parametric analysis of bolted flange connections of circular monopoles.

机译:圆形单极螺栓法兰连接的参数分析。

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摘要

The present study involved the parametric analysis of bolted flange connections of eighteen different circular monopoles. The parameters considered were the number of bolts (8, 6, and 4) and thickness of flange plate [25.4 mm (1.0 in.), 19.05 mm (0.75 in.) and 12.7 mm (0.50 in.)]. These were analyzed under stiffened and unstiffened conditions. Four, two and four stiffeners, 12.7 mm (0.50 in.) thick, were used with 8-, 6- and 4-bolt arrangements. Each finite element model is made up of a small diameter (171.5 mm) circular pipe and a large diameter (327 mm) circular pipe both welded to circular flanges. The outer and inner diameters of the flange plates were 327 mm and 171.5 mm respectively. Each bolt was 25.4 mm (1 in.) diameter and was pretensioned to 227 kN (51 kips); and an external load of 45 kN (10 kips) was applied at the free end of the monopole, 1804 mm (71 in.) from the bolted joint, in the Riks analysis load step of ABAQUS (version 6.3) computer program. From the finite element analysis, it was found that monopoles (8 bolts, 6 bolts and 4 bolts) with unstiffened 12.7 mm (0.50 in.) thick flange plates experienced a large deformation because of the thin flange plate. Optimum solutions to stiffened and unstiffened connections were found to be among those monopoles with minimal gap, deflection and deformation, i.e., 25.4 mm (1 in.) thick flanges with 4 bolts or 19.05 mm (0.75 in.) thick flanges with 6 bolts for unstiffened case; and 12.7 mm (0.50 in.) thick flanges with 8 bolts, 25.4 mm (1 in.) thick flanges with 4 bolts or 19.05 mm (0.75 in.) thick flanges with 6 bolts for stiffened case.; In addition to the parametric study, T-Stub and yield line analytical procedures were also presented with examples; and it was found that the analytical methods provide good preliminary guidance regarding connection parameters when designing bolted flange connections for circular monopoles.
机译:本研究涉及十八种不同圆形单极子的螺栓法兰连接的参数分析。考虑的参数是螺栓的数量(8、6和4)和法兰板的厚度[25.4毫米(1.0英寸),19.05毫米(0.75英寸)和12.7毫米(0.50英寸)]。在加劲和不加劲的条件下对它们进行了分析。分别使用厚度为12.7毫米(0.50英寸)的四个,两个和四个加劲肋,并带有8、6和4螺栓布置。每个有限元模型均由小直径(171.5 mm)圆形管和大直径(327 mm)圆形管组成,两者均焊接到圆形法兰上。法兰盘的外径和内径分别为327 mm和171.5 mm。每个螺栓的直径为25.4毫米(1英寸),并预拉伸至227 kN(51 kips);在ABAQUS(6.3版)计算机程序的Riks分析载荷步骤中,在距螺栓连接接头1804毫米(71英寸)的单极自由端施加45 kN(10 kips)的外部载荷。通过有限元分析,发现具有未加劲的12.7毫米(0.50英寸)厚法兰板的单极子(8个螺栓,6个螺栓和4个螺栓)由于法兰薄而变形大。发现在那些间隙,挠度和变形最小的单极子中,对加劲和不加劲的连接的最佳解决方案,即25.4毫米(1英寸)厚的法兰(4个螺栓)或19.05毫米(0.75英寸)厚的法兰(6个螺栓)。未加严的情况;用于加固外壳的12.7毫米(0.50英寸)厚法兰,带4个螺栓的25.4毫米(1英寸)厚法兰,或带6个螺栓的19.05毫米(0.75英寸)厚法兰,用于加硬外壳。除了参数研究之外,还提供了T-Stub和屈服线分析程序的示例。结果发现,在设计圆形单极螺栓法兰连接时,该分析方法为连接参数提供了良好的初步指导。

著录项

  • 作者

    Olusanya, Olumadunwa.;

  • 作者单位

    University of Windsor (Canada).;

  • 授予单位 University of Windsor (Canada).;
  • 学科 Engineering Civil.
  • 学位 M.A.Sc.
  • 年度 2005
  • 页码 152 p.
  • 总页数 152
  • 原文格式 PDF
  • 正文语种 eng
  • 中图分类 建筑科学;
  • 关键词

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