【摘要】：本文針對(duì)D型打結(jié)器在打結(jié)嘴鉸扭繩扣過(guò)程中出現(xiàn)的捆繩纏死在打結(jié)嘴凸臺(tái)上導(dǎo)致的成結(jié)失敗和鉤鉗扭轉(zhuǎn)變形問(wèn)題,以非均勻三次B樣條曲線造型方法和基于累積損傷理論的可靠性設(shè)計(jì)方法對(duì)打結(jié)器繞扣機(jī)構(gòu)進(jìn)行改進(jìn)設(shè)計(jì),運(yùn)用基于剛?cè)峤佑|動(dòng)力學(xué)的打結(jié)器虛擬打結(jié)方法,對(duì)改進(jìn)前后的繞扣機(jī)構(gòu)進(jìn)行成結(jié)對(duì)比試驗(yàn),驗(yàn)證了繞扣機(jī)構(gòu)改進(jìn)設(shè)計(jì)的有效性,并利用打結(jié)器性能檢測(cè)與可靠性試驗(yàn)臺(tái)對(duì)改進(jìn)后的繞扣機(jī)構(gòu)進(jìn)行打結(jié)正交試驗(yàn)。本文的主要研究工作如下:(1)打結(jié)嘴的曲面造型設(shè)計(jì):提出利用非均勻三次B樣條曲線造型方法表征打結(jié)嘴縱向截面輪廓曲線,對(duì)比分析構(gòu)造的打結(jié)嘴縱向截面輪廓曲線與三維掃描的打結(jié)嘴模型對(duì)應(yīng)截面曲線,二者的弧度變化率相差0.05,表明此方法可行。建立了打結(jié)嘴表面的非均勻三次B樣條曲面函數(shù),利用C++的OPENGL可視化模塊構(gòu)造打結(jié)嘴曲面。通過(guò)對(duì)打結(jié)嘴繞扣過(guò)程的受力分析,得出捆繩不發(fā)生纏死在打結(jié)嘴凸臺(tái)上的曲面曲率要求,利用非均勻三次B樣條曲線造型方法對(duì)打結(jié)嘴側(cè)向曲面進(jìn)行改進(jìn)設(shè)計(jì)。(2)基于累積損傷理論的鉤鉗可靠性設(shè)計(jì):以實(shí)測(cè)的繞扣機(jī)構(gòu)在成結(jié)過(guò)程中所受捆繩拉力為鉤鉗載荷,利用ANSYS有限元軟件建立鉤鉗的靜力學(xué)分析模型,通過(guò)加載與求解計(jì)算得出鉤鉗危險(xiǎn)點(diǎn)位置。再利用ANSYS的疲勞分析模塊對(duì)危險(xiǎn)點(diǎn)進(jìn)行疲勞分析,結(jié)果顯示:經(jīng)過(guò)10萬(wàn)次循環(huán)加載,鉤鉗的疲勞耗損系數(shù)達(dá)到1.87476,發(fā)生疲勞失效。采用強(qiáng)度-應(yīng)力干涉理論,以鉤鉗危險(xiǎn)截面積最小為優(yōu)化目標(biāo)函數(shù),約束鉤鉗剛度和強(qiáng)度條件,建立鉤鉗模糊可靠性優(yōu)化設(shè)計(jì)模型,得出6×6圓角矩形截面的20CrMnTi為最優(yōu)解,且ANSYS的疲勞分析結(jié)果顯示,經(jīng)過(guò)10萬(wàn)次循環(huán)加載,鉤鉗的疲勞耗損系數(shù)達(dá)到0.79256,鉤鉗沒(méi)有發(fā)生疲勞失效。(3)雙齒盤驅(qū)動(dòng)打結(jié)器繞扣機(jī)構(gòu)動(dòng)力學(xué)仿真:利用ADAMS動(dòng)力學(xué)仿真軟件建立改進(jìn)前后的繞扣機(jī)構(gòu)與捆繩剛?cè)峤佑|的動(dòng)力學(xué)模型,對(duì)比分析了改進(jìn)前后的繞扣機(jī)構(gòu)動(dòng)作過(guò)程,表明改進(jìn)后的繞扣機(jī)構(gòu)成結(jié)更加可靠。利用打結(jié)器性能檢測(cè)與可靠性試驗(yàn)臺(tái)對(duì)改進(jìn)后的繞扣機(jī)構(gòu)進(jìn)行打結(jié)試驗(yàn),16000次打結(jié)試驗(yàn)結(jié)果表明:改進(jìn)后的打結(jié)嘴曲面可約束捆繩纏繞在打結(jié)嘴凸臺(tái)下方表面,未發(fā)生捆繩纏死在打結(jié)嘴凸臺(tái)上導(dǎo)致的成結(jié)失敗現(xiàn)象。(4)繞扣機(jī)構(gòu)正交疲勞試驗(yàn):以捆繩拉力、打結(jié)器主軸轉(zhuǎn)速和捆繩直徑為因素,對(duì)改進(jìn)后的繞扣機(jī)構(gòu)進(jìn)行打結(jié)正交試驗(yàn),同時(shí)利用測(cè)量鉤鉗截面與打結(jié)嘴安裝截面間距變化,以此分析鉤鉗是否發(fā)生變形,試驗(yàn)結(jié)果表明:在經(jīng)過(guò)16000次的打結(jié)正交試驗(yàn)后,繞扣機(jī)構(gòu)成結(jié)率達(dá)到100%,鉤鉗截面與打結(jié)嘴安裝面的間距保持初始值0.52mm,并未發(fā)生變形,與ANSYS的疲勞分析結(jié)果一致。
[Abstract]:In this paper, the problems of knot forming failure and torsion deformation of hook pliers caused by bundles wrapped on the knotted protruding platform in the process of knot joint hinges and twisting rope buckling of D type knots are discussed in this paper. The nonuniform cubic B-spline curve modeling method and the reliability design method based on cumulative damage theory are used to improve the design of knot winding mechanism, and the virtual knotting method based on rigid and flexible contact dynamics is used. The effect of the improved design on the improved mechanism is verified by the comparison test of the improved winding mechanism, and the orthogonal test of the improved winding mechanism is carried out by using the performance test and reliability test bench of the knotting device. The main work of this paper is as follows: (1) Surface modeling design of knots: a non-uniform cubic B-spline curve modeling method is proposed to characterize the profile curve of longitudinal section of knots. The curve of longitudinal section profile constructed by comparison with that of the model of 3D scanning is compared with the curve of section, and the difference of radians between them is 0.05, which shows that this method is feasible. The nonuniform cubic B-spline surface function of the knotted surface is established, and the knotted surface is constructed by using C's OPENGL visualization module. Through the analysis of the force on the winding process of the knots, it is concluded that the curvature requirements of the curved surface of the bundles do not occur when they are wrapped on the knotted protruding table. The non-uniform cubic B-spline curve modeling method is used to improve the design of the lateral surface of knot nozzles. (2) the reliability design of hook and clamp based on cumulative damage theory. The statics analysis model of hook forceps was established by using ANSYS finite element software, and the dangerous point position of hook pliers was obtained by loading and solving calculation. The fatigue analysis of the dangerous point is carried out by using the fatigue analysis module of ANSYS. The results show that after 100000 cycles, the fatigue wear coefficient of the hook clamp reaches 1.87476, and the fatigue failure occurs. Using the theory of strength and stress interference, taking the minimum dangerous cross section of hook clamp as the optimization objective function, and restricting the stiffness and strength condition of hook clamp, the fuzzy reliability optimization design model of hook clamp is established, and the optimal solution of 6 脳 6 corner rectangular section 20CrMnTi is obtained. The fatigue analysis results of ANSYS show that, after 100000 cyclic loading, The fatigue wear coefficient of hook pliers reaches 0.79256, and there is no fatigue failure of hook pliers. (3) dynamic simulation of winding mechanism of double-toothed disc driven knotting device: the dynamic model of rigid and flexible contact between winding mechanism and bundle rope before and after improvement is established by using ADAMS dynamic simulation software. The operation process of the improved winding mechanism is compared and analyzed, which shows that the improved winding mechanism is more reliable. Using the knotter performance test and reliability test bench, the results of 16000 knotting tests on the improved winding mechanism show that the improved knotted curved surface can constrain the binding rope winding on the surface of the knotted protruding table. (4) orthogonal fatigue test of the winding mechanism: taking the tension of the rope, the rotation speed of the main shaft and the diameter of the tie rope as the factors, the improved winding mechanism was tested by orthogonal knotting test. At the same time, by measuring the distance between the cross section of hook pliers and the installation section of knot nozzles, the deformation of hook pliers is analyzed. The results show that: after 16000 times of knotting orthogonal test, The connection rate of the winding mechanism is 100 and the distance between the hook and clamp section and the mounting surface of the knot nozzle keeps the initial value of 0.52 mm, and no deformation occurs, which is consistent with the fatigue analysis results of ANSYS.
【學(xué)位授予單位】：江蘇大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2017
【分類號(hào)】：S225

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本文編號(hào)：2177201