双钢轮振动压路机振幅不均匀性的试验研究
摘要
近年来,国产双钢轮振动压路机的产量大幅增长,但与国外同类机型的压实质量相比差异很大,在压实作业时,压实质量不高,路面不平整,有的压路机甚至出现跑偏现象,以至于我国的双钢轮振动压路机还不能在高等级公路中实现面层的压实作业。究其原因,振动轮(沿轮宽方向)左右两端振幅存在明显的差异是造成这一问题的主要原因之一。对国内一些双钢轮振动压路机的性能测试发现,我国的双钢轮振动压路机振动轮两端振幅存在较大的差异,有时超过20%,这必将严重影响双钢轮振动压路机的行驶性能和压实均匀性。
为解决这一问题,对双钢轮振动压路机的结构与性能进行了分析。双钢轮振动压路机振动轮的结构是不对称的,振动轮的滚动及安装于振动轮之上的车架的支撑,驱动侧依靠的是轮边减速机,振动侧依靠的是框架轴承。但在计算质量、减振效果、沿钢轮轴线振幅均匀度等参数时,往往是按照“对称”考虑的。这必然造成实际与理论计算差距的不符,引起双钢轮振动压路机沿钢轮轴线振幅不均匀性较大。
建立了钢轮的偏振模型,在模型中考虑了机架质心偏距、振动轮质心偏距、减振块刚度和阻尼对振动轮振幅不均性的影响。
基于该模型,运用MATLAB程序语言进行仿真计算,分析了引起振动轮振幅不均匀的单因素与多因素影响时的偏振情况。得出的结论是:振动轮质心偏距、机架质心偏距、减振块刚度和阻尼对振动轮振幅的均匀性影响程度是依次递减的,影响因素同时出现时,振动轮沿轴线方向的振幅偏差会更大。
为验证仿真分析的正确性,对国内某品牌11t级双钢轮振动压路机的振动效果进行了现场试验与分析,结果表明实测结果与仿真计算结果相近,证明了振动模型的正确性,为压路机的设计和使用提供了参考。
In recent years,the domestically produced Double-drum vibratory roller's output grows largely,but the domestic roller compaction quality worse than imports. When operating in the compaction,compaction quality is not high, pavement not formation, some even roller can not travel in a straight line, so China's Double-drum vibratory roller can not achieve high-grade highway in the surface layer of compacted operations. The reason is that vibration is round about the two ends of the amplitude of uneven. On some performance test of domestic Double-drum vibratory roller found that, China's Double-drum vibratory roller vibration amplitude round at both ends of the larger differences exist, sometimes more than 20%, this will seriously affect Double-drum vibratory roller on the performance and uniformity of compaction.
In order to solve this problem, we have carried on the analysis to the Double-drum vibratory roller's structure and the performance. Double-drum vibratory roller vibration round of the structure is asymmetric, vibration round with the support of body connection, driver-side rely on the round-reducer, vibration side rely on the framework of bearings. However, in the calculation of quality, the damping effect, the uniform amplitude and so on, often in accordance with the "symmetry" to consider about it. This will inevitably lead to the gap between actual and theoretical calculations of the discrepancies, from Double-drum vibratory roller drum along the axis of greater amplitude uneven.
The establishment of four degrees of freedom model, the model considered the rack in the center of mass from the side, vibration from the partial round of heart, stiffness and vibration damping block round of the amplitude of the vibration of the impact of inequality.
Based on this model, the use of MATLAB simulation programming language, the analysis of the vibration caused uneven round of the amplitude of the single-factor and multi-polarization factors affecting the situation. Come to the conclusion that: vibration round of partial from the heart, rack of heart from the side, block stiffness and vibration damping of vibration amplitude round of the uniformity of the impact of the decline is followed, the impact of factors at the same time, the vibration along the axis direction of the round Amplitude deviation will be greater.
To verify the accuracy of simulation analysis, a certain brand of domestic 11 t-Double-drum vibratory roller effect of vibration testing and analysis of the scene. The results showed that the measured results and simulation results similar to prove the correctness of the vibration model for the design and use of rollers to provide a reference.
为解决这一问题,对双钢轮振动压路机的结构与性能进行了分析。双钢轮振动压路机振动轮的结构是不对称的,振动轮的滚动及安装于振动轮之上的车架的支撑,驱动侧依靠的是轮边减速机,振动侧依靠的是框架轴承。但在计算质量、减振效果、沿钢轮轴线振幅均匀度等参数时,往往是按照“对称”考虑的。这必然造成实际与理论计算差距的不符,引起双钢轮振动压路机沿钢轮轴线振幅不均匀性较大。
建立了钢轮的偏振模型,在模型中考虑了机架质心偏距、振动轮质心偏距、减振块刚度和阻尼对振动轮振幅不均性的影响。
基于该模型,运用MATLAB程序语言进行仿真计算,分析了引起振动轮振幅不均匀的单因素与多因素影响时的偏振情况。得出的结论是:振动轮质心偏距、机架质心偏距、减振块刚度和阻尼对振动轮振幅的均匀性影响程度是依次递减的,影响因素同时出现时,振动轮沿轴线方向的振幅偏差会更大。
为验证仿真分析的正确性,对国内某品牌11t级双钢轮振动压路机的振动效果进行了现场试验与分析,结果表明实测结果与仿真计算结果相近,证明了振动模型的正确性,为压路机的设计和使用提供了参考。
In recent years,the domestically produced Double-drum vibratory roller's output grows largely,but the domestic roller compaction quality worse than imports. When operating in the compaction,compaction quality is not high, pavement not formation, some even roller can not travel in a straight line, so China's Double-drum vibratory roller can not achieve high-grade highway in the surface layer of compacted operations. The reason is that vibration is round about the two ends of the amplitude of uneven. On some performance test of domestic Double-drum vibratory roller found that, China's Double-drum vibratory roller vibration amplitude round at both ends of the larger differences exist, sometimes more than 20%, this will seriously affect Double-drum vibratory roller on the performance and uniformity of compaction.
In order to solve this problem, we have carried on the analysis to the Double-drum vibratory roller's structure and the performance. Double-drum vibratory roller vibration round of the structure is asymmetric, vibration round with the support of body connection, driver-side rely on the round-reducer, vibration side rely on the framework of bearings. However, in the calculation of quality, the damping effect, the uniform amplitude and so on, often in accordance with the "symmetry" to consider about it. This will inevitably lead to the gap between actual and theoretical calculations of the discrepancies, from Double-drum vibratory roller drum along the axis of greater amplitude uneven.
The establishment of four degrees of freedom model, the model considered the rack in the center of mass from the side, vibration from the partial round of heart, stiffness and vibration damping block round of the amplitude of the vibration of the impact of inequality.
Based on this model, the use of MATLAB simulation programming language, the analysis of the vibration caused uneven round of the amplitude of the single-factor and multi-polarization factors affecting the situation. Come to the conclusion that: vibration round of partial from the heart, rack of heart from the side, block stiffness and vibration damping of vibration amplitude round of the uniformity of the impact of the decline is followed, the impact of factors at the same time, the vibration along the axis direction of the round Amplitude deviation will be greater.
To verify the accuracy of simulation analysis, a certain brand of domestic 11 t-Double-drum vibratory roller effect of vibration testing and analysis of the scene. The results showed that the measured results and simulation results similar to prove the correctness of the vibration model for the design and use of rollers to provide a reference.
引文
[1]冯忠绪.工程机械理论[M].北京:人民交通出版社,2003:201-203
[2]陈振春.压路机构造与技术运用[M].北京:人民交通出版社, 1991:72-80
[3]孙祖望.压实技术与压实机械的发展与展望[J].筑路机械与施工机械化,2004(05):4-7
[4]马捷.我国液压振动压路机的发展机遇与挑战[J].公路与汽运,2006(10):101-103
[5]张启君,张忠海,张宏,王华君.国外双钢轮振动压路机的探讨[J].压实机械与施工技术,2004(04):47-48
[6]李冰.振动压路机与振动压实技术[M].北京:人民交通出版社,2001:2-4
[7]程耀东.机械振动学[M].杭州:浙江大学出版社, 1988:43-46
[8]赵铁栓,陈新轩.压路机运用技术[M].陕西:陕西科学技术出版社:2005:1-2
[9]郇庆祥,刘军,刘翠菊.振动压路机激振机构的改进设计[J].建设机械技术与管理,2007(10):102-103
[10]刘洪海,吴少鹏,玄东兴.沥青路面碾压离析的试验研究[J].武汉理工大学学报(交通科学与工程版),2004(12):899-901
[11]沙庆林.高速公路沥青路面早期破坏现象及预防[M].北京:人民交通出版社,2001:89-95
[12]沈金安关于沥青混合料的均匀性和离析问题[J].公路交通科技,2001(12):32-34
[13]周承德.振动压路机名义振幅求解方法研究[J].建筑机械,2002(6):12-14
[14]冯忠绪,朱伟敏,姚运仕,岳建平.振动压路机名义振幅的探讨[J].压实机械与施工技术,2005(10):49-51
[15] Chang, Chieh-Min (Alfred Benesch and Company); Baladi, Gilbert Y.; Wolff, Thomas F Detecting segregation in bituminous pavements Transportation Research Record, n 1813, 02-2634, 2002, p 77-86
[16] Selig,E.T., T.S.Yoo. Dynamics of vibratory roller compaction[J]. Journal of the Geotechnical Eng.Division,1979:55-58
[17] Machet.J.M, More.L.G. Vibratory compaction of bituminous mixes in France[J]. Pavement Constraction and Field Contral.1977:326-333
[18] D.Pietzsch, Wolfgang Poppy. Simulation of soil compaction with vibratory rollers[J].Journal of Terramechanics, 1992, 29(6): 585-597
[19]严世榕,闻邦椿.考虑塑性变形的振动压路机非线性动力学仿真[J].筑路机械与施工机械化,1999,16(4):13-16
[20]王聪玲.混沌振动在压实作业中应用的仿真研究[D].北京:中国农业大学博士学位论文, 1999
[21] Windisch SJ, Yong RN. The determination of soil strain-rate behaviour beneath a moving wheel[J]. Journal of Terramechanics, 1970, 7(1): 55-67
[22] Yong RN, Fattah EA, Boonsisuk P. Analysis and prediction of tire-soil interaction and performance using finite elements[J]. Journal of Terramechanics, 1978, 15(1): 43-63
[23] Aubel T.[A]. The interaction between the rolling type and the soft soil. Sixth European ISTVS Conference[C]. Wien, 1994: 169-88
[24] J. Maciejewski, A. Jarzebowski. Experimental analysis of soil deformation below a rolling rigid cylinder[J]. Journal of Terramechanics, 2004, (41): 223-241
[25] Onafeko O, Reece AR. Soil stresses and deformations beneath rigid wheel[J]. Journal of Terra-mechanics, 1967, 4(1): 59-80
[26] Abebe AT, Tanaka T, Yamazaki M. Soil compaction by multiple passes of a rigid wheel relevant for optimization of traffic[J]. Journal of Terramechanics, 1989, 26(2): 139-148
[27] R.L. Raper, C.E. Johnson, A.C. Bailey. Prediction of Soil Stresses Beneath a Rigid Wheel[J]. J.agric.Engng Res, 1995 (61): 57-62
[28] I. Shmulevich, U. Mussel, D. Wolf. The effect of velocity on rigid wheel performance[J]. Journal of Terramechanics, 1998 (35): 189-207
[29] T. Hiroma, S. Wanjii, T. Kataoka. Stress analysis using FEM on stress distribution under a wheel considering friction with adhesion between a wheel and soil[J]. Journal of Terramechanics, 1997, 34(4): 225-233
[30] T. Shikanai, K. Hashiguchi, Y. Nohse. Precise measurement of soil deformation and fluctuation in drawbar pull for steel and rubber-coated rigid wheel[J]. Journal of Terramechanics, 2000, 37(1): 21-39
[31] Hiroma T, Ohta Y, Suyama K. Analysis of the soil deformation beneath a wheel by the finite element method[J]. J Jpn Soc Agric Mach, 1984, 46(2): 163-70
[32] Wong JY. Behavior of soil beneath rigid wheels[J]. J Jpn Soc Agric Mach, 1967, 12 (4):257-269
[33] Nakashima H, Tanaka T. Interaction in soil-lug system[J]. J Jpn Soc Agric Mach, 1989, 51(2): 47-55
[34]杨士敏,张铁.工程机械地面力学与行驶理论[M].西安:陕西科学技术出版社, 2000
[35]倪振华.振动力学[M].西安:西安交通大学出版社, 1989:99-104
[36]薛定宇,陈阳泉.高等应用数学问题的MATLAB求解[M].北京:清华大学出版社,2004:203-257
[37]徐灏.机械设计手册[Z].北京:机械工业出版社,1995:256-272
[38]何挺继.筑路机械手册[Z].北京:机械工业出版社,1988:349-360
[39]楼顺天,陈生潭,雷虎民. MATLAB5.X程序设计语言[M].西安:西安电子科技大学出版社,2004:203-257
[40]王济,胡晓. MATLAB在振动信号处理中的应用[M].北京:知识产权出版社,中国水利水电出版社,2006:83-96
[41]中华人民共和国国家标准《振动压路机》(GB/T8511-2005)[S].北京:中华人民共和国国家质量监督检验检疫总局,2005:10
[42]数据采集系统[EB/OL]. http://www.xahuance.com/cpfl.asp?id=100
[2]陈振春.压路机构造与技术运用[M].北京:人民交通出版社, 1991:72-80
[3]孙祖望.压实技术与压实机械的发展与展望[J].筑路机械与施工机械化,2004(05):4-7
[4]马捷.我国液压振动压路机的发展机遇与挑战[J].公路与汽运,2006(10):101-103
[5]张启君,张忠海,张宏,王华君.国外双钢轮振动压路机的探讨[J].压实机械与施工技术,2004(04):47-48
[6]李冰.振动压路机与振动压实技术[M].北京:人民交通出版社,2001:2-4
[7]程耀东.机械振动学[M].杭州:浙江大学出版社, 1988:43-46
[8]赵铁栓,陈新轩.压路机运用技术[M].陕西:陕西科学技术出版社:2005:1-2
[9]郇庆祥,刘军,刘翠菊.振动压路机激振机构的改进设计[J].建设机械技术与管理,2007(10):102-103
[10]刘洪海,吴少鹏,玄东兴.沥青路面碾压离析的试验研究[J].武汉理工大学学报(交通科学与工程版),2004(12):899-901
[11]沙庆林.高速公路沥青路面早期破坏现象及预防[M].北京:人民交通出版社,2001:89-95
[12]沈金安关于沥青混合料的均匀性和离析问题[J].公路交通科技,2001(12):32-34
[13]周承德.振动压路机名义振幅求解方法研究[J].建筑机械,2002(6):12-14
[14]冯忠绪,朱伟敏,姚运仕,岳建平.振动压路机名义振幅的探讨[J].压实机械与施工技术,2005(10):49-51
[15] Chang, Chieh-Min (Alfred Benesch and Company); Baladi, Gilbert Y.; Wolff, Thomas F Detecting segregation in bituminous pavements Transportation Research Record, n 1813, 02-2634, 2002, p 77-86
[16] Selig,E.T., T.S.Yoo. Dynamics of vibratory roller compaction[J]. Journal of the Geotechnical Eng.Division,1979:55-58
[17] Machet.J.M, More.L.G. Vibratory compaction of bituminous mixes in France[J]. Pavement Constraction and Field Contral.1977:326-333
[18] D.Pietzsch, Wolfgang Poppy. Simulation of soil compaction with vibratory rollers[J].Journal of Terramechanics, 1992, 29(6): 585-597
[19]严世榕,闻邦椿.考虑塑性变形的振动压路机非线性动力学仿真[J].筑路机械与施工机械化,1999,16(4):13-16
[20]王聪玲.混沌振动在压实作业中应用的仿真研究[D].北京:中国农业大学博士学位论文, 1999
[21] Windisch SJ, Yong RN. The determination of soil strain-rate behaviour beneath a moving wheel[J]. Journal of Terramechanics, 1970, 7(1): 55-67
[22] Yong RN, Fattah EA, Boonsisuk P. Analysis and prediction of tire-soil interaction and performance using finite elements[J]. Journal of Terramechanics, 1978, 15(1): 43-63
[23] Aubel T.[A]. The interaction between the rolling type and the soft soil. Sixth European ISTVS Conference[C]. Wien, 1994: 169-88
[24] J. Maciejewski, A. Jarzebowski. Experimental analysis of soil deformation below a rolling rigid cylinder[J]. Journal of Terramechanics, 2004, (41): 223-241
[25] Onafeko O, Reece AR. Soil stresses and deformations beneath rigid wheel[J]. Journal of Terra-mechanics, 1967, 4(1): 59-80
[26] Abebe AT, Tanaka T, Yamazaki M. Soil compaction by multiple passes of a rigid wheel relevant for optimization of traffic[J]. Journal of Terramechanics, 1989, 26(2): 139-148
[27] R.L. Raper, C.E. Johnson, A.C. Bailey. Prediction of Soil Stresses Beneath a Rigid Wheel[J]. J.agric.Engng Res, 1995 (61): 57-62
[28] I. Shmulevich, U. Mussel, D. Wolf. The effect of velocity on rigid wheel performance[J]. Journal of Terramechanics, 1998 (35): 189-207
[29] T. Hiroma, S. Wanjii, T. Kataoka. Stress analysis using FEM on stress distribution under a wheel considering friction with adhesion between a wheel and soil[J]. Journal of Terramechanics, 1997, 34(4): 225-233
[30] T. Shikanai, K. Hashiguchi, Y. Nohse. Precise measurement of soil deformation and fluctuation in drawbar pull for steel and rubber-coated rigid wheel[J]. Journal of Terramechanics, 2000, 37(1): 21-39
[31] Hiroma T, Ohta Y, Suyama K. Analysis of the soil deformation beneath a wheel by the finite element method[J]. J Jpn Soc Agric Mach, 1984, 46(2): 163-70
[32] Wong JY. Behavior of soil beneath rigid wheels[J]. J Jpn Soc Agric Mach, 1967, 12 (4):257-269
[33] Nakashima H, Tanaka T. Interaction in soil-lug system[J]. J Jpn Soc Agric Mach, 1989, 51(2): 47-55
[34]杨士敏,张铁.工程机械地面力学与行驶理论[M].西安:陕西科学技术出版社, 2000
[35]倪振华.振动力学[M].西安:西安交通大学出版社, 1989:99-104
[36]薛定宇,陈阳泉.高等应用数学问题的MATLAB求解[M].北京:清华大学出版社,2004:203-257
[37]徐灏.机械设计手册[Z].北京:机械工业出版社,1995:256-272
[38]何挺继.筑路机械手册[Z].北京:机械工业出版社,1988:349-360
[39]楼顺天,陈生潭,雷虎民. MATLAB5.X程序设计语言[M].西安:西安电子科技大学出版社,2004:203-257
[40]王济,胡晓. MATLAB在振动信号处理中的应用[M].北京:知识产权出版社,中国水利水电出版社,2006:83-96
[41]中华人民共和国国家标准《振动压路机》(GB/T8511-2005)[S].北京:中华人民共和国国家质量监督检验检疫总局,2005:10
[42]数据采集系统[EB/OL]. http://www.xahuance.com/cpfl.asp?id=100