本文選題：振動(dòng) + 曲柄滑塊機(jī)構(gòu)　； 參考：《西安工程大學(xué)》2012年碩士論文

【摘要】：針刺機(jī)是紡織行業(yè)中干法織布的重要設(shè)備，該機(jī)的核心部件為兩個(gè)對(duì)稱的曲柄滑塊機(jī)構(gòu)，當(dāng)機(jī)器工作時(shí)滑塊的縱向慣性力無法完全消除，導(dǎo)致針刺機(jī)有較大的振動(dòng)與噪聲現(xiàn)象出現(xiàn)，針刺機(jī)的壽命會(huì)大大減小，也會(huì)影響工人健康，而且故障出現(xiàn)頻率也會(huì)大幅度提升，更重要的是產(chǎn)品質(zhì)量也會(huì)有所降低。 為進(jìn)一步提高針刺機(jī)的針刺頻率亟須對(duì)曲柄滑塊機(jī)構(gòu)的振動(dòng)問題進(jìn)行研究，本文以針刺機(jī)的曲柄滑塊為研究對(duì)象對(duì)其進(jìn)行研究。從針梁部件運(yùn)動(dòng)規(guī)律、構(gòu)件受力、機(jī)構(gòu)計(jì)算機(jī)模態(tài)分析與諧響應(yīng)分析、主軸與針梁部件的振動(dòng)波形分析（主要是時(shí)間波形圖分析與頻譜圖分析）四大方面對(duì)其振動(dòng)現(xiàn)象進(jìn)行研究，找出可能造成振動(dòng)的原因。 首先，從曲柄滑塊機(jī)構(gòu)的運(yùn)動(dòng)特性著手，繪制出曲柄滑塊機(jī)構(gòu)主要部件的運(yùn)動(dòng)曲線圖。其次，利用ANSYS的強(qiáng)大分析功能計(jì)算出曲柄滑塊機(jī)構(gòu)主要部件如連桿、曲軸的變形量，并驗(yàn)正其需用應(yīng)力。再次，利用ANSYS軟件對(duì)曲柄滑塊機(jī)構(gòu)的重要部件如：曲軸、連桿、針梁進(jìn)行模態(tài)分析和諧響應(yīng)分析，，找出重要部件的固有頻率和振動(dòng)模型與共振時(shí)的振動(dòng)幅值和相位。最后，利用振動(dòng)測(cè)試設(shè)備現(xiàn)場對(duì)曲柄滑塊機(jī)構(gòu)進(jìn)行檢測(cè)，繪制出主要位置的振動(dòng)波形圖和頻譜圖。綜合分析理論運(yùn)動(dòng)曲線與計(jì)算機(jī)仿真的結(jié)果以及實(shí)際測(cè)出的振動(dòng)信號(hào)，得出了引起振動(dòng)的原因。 通過運(yùn)動(dòng)曲線理論分析及ADAMS動(dòng)力學(xué)仿真發(fā)現(xiàn)針刺機(jī)的曲柄滑塊機(jī)構(gòu)運(yùn)動(dòng)時(shí)存在比較大的沖擊力，可能引起設(shè)備的振動(dòng)從而影響產(chǎn)品質(zhì)量和減少機(jī)器壽命。適當(dāng)選擇平衡塊的質(zhì)量和質(zhì)心距就能最大限度地減少慣性力，但是曲柄滑塊機(jī)構(gòu)的慣性力不能完全消除，要減小該慣性力，需減小滑塊和連桿的重量，以及偏心距和連桿的長度。連桿變形量在Z向即長度方向最大，連桿所受應(yīng)力遠(yuǎn)小于其許用應(yīng)力；在曲軸許可變形范圍內(nèi)計(jì)算出了曲軸端面的最大變形量，并得曲軸出扭轉(zhuǎn)應(yīng)力遠(yuǎn)小于其扭轉(zhuǎn)許用應(yīng)力。借助于ANSYS軟件進(jìn)行的模態(tài)分析和諧響應(yīng)，得出連桿在頻率為40HZ時(shí)會(huì)發(fā)生共振現(xiàn)象，曲軸在30HZ時(shí)會(huì)發(fā)生共振現(xiàn)象，針梁的前十階固有頻率最大為2.1561HZ，但是，在針刺機(jī)啟動(dòng)過程中會(huì)很快越過針梁共振區(qū)，所以，以后改進(jìn)針刺機(jī)振動(dòng)特性時(shí)完全可以把針梁的因素作為次要因素來考慮，本針刺機(jī)的最大工作頻率為20HZ,不會(huì)引起曲柄滑塊機(jī)構(gòu)的共振現(xiàn)象。通過實(shí)地測(cè)試針刺機(jī)的曲柄滑塊機(jī)構(gòu)的振動(dòng)，對(duì)其濾波后的振動(dòng)信號(hào)的波形圖和頻譜圖進(jìn)行分析，得出引起曲柄滑塊機(jī)構(gòu)振動(dòng)的主要原因是轉(zhuǎn)子不平衡和碰磨。 最后,提了三個(gè)出不同的優(yōu)化方案，第一是通過繪制出滑塊的理論加速度曲線圖，改變加速度的相關(guān)參數(shù)從理論上使得加速度值得以大幅度減小。第二是通過變換不同的彈性模量、阻尼系數(shù)、磨擦系數(shù)即更換更優(yōu)的材質(zhì)后進(jìn)行ADMAS仿真,使得加速曲線變得比較光滑，避免沖擊力的產(chǎn)生。最后,通過在安裝了飛輪和配重塊并重新安裝曲軸和搖臂裝置,之后進(jìn)行實(shí)地的振動(dòng)測(cè)試，振動(dòng)幅值減小為原來的三到五倍。
[Abstract]:The needle punching machine is an important equipment for dry weaving in the textile industry. The core components of the machine are two symmetrical crank slider mechanisms. When the machine works, the longitudinal inertia force of the slider can not be completely eliminated. The needle punching machine has a large vibration and noise phenomenon, the life of the needle punching machine will be greatly reduced, and the workers' health will also be affected. Moreover, it will also affect the health of the workers, and therefore, the health of the workers will also be affected. The frequency of obstacles will also greatly improve, and more importantly, the quality of products will also be reduced.
In order to further improve the frequency of the needle punching frequency of the needle machine, the vibration of the crank slider mechanism must be studied. In this paper, the crank slider of the needle machine is studied. The motion law of the part of the needle beam, the force of the component, the modal analysis of the mechanism and the harmonic response of the mechanism, and the analysis of the vibration wave of the spindle and the part of the needle and beam (main body) If the time waveform analysis and spectrum analysis), four aspects of the vibration phenomenon are studied to find out the possible causes of vibration.
First, starting from the motion characteristics of the crank slider mechanism, the motion graph of the main parts of the crank slider mechanism is drawn. Secondly, the deformation of the crank slider mechanism, such as the connecting rod, the crankshaft deformation, and the required stress are calculated by the powerful analysis function of the ANSYS. Then, the important part of the crank slider mechanism is used by the ANSYS software. Parts such as crankshaft, connecting rod and needle beam are analyzed by modal analysis and harmonic response analysis, and the vibration amplitude and phase of the natural frequency and vibration model and resonance of important parts are found. Finally, the vibration waveform and spectrum of the main position are drawn by the vibration testing equipment, and the theoretical motion is analyzed. The results of the curve and computer simulation and the measured vibration signals show the cause of the vibration.
Through the theoretical analysis of motion curve and ADAMS dynamic simulation, it is found that the crank slider mechanism of the needle punching machine has a relatively large impact force, which may cause the vibration of the equipment to affect the quality of the product and reduce the life of the machine. The proper selection of the mass and the center distance of the balance block can minimize the inertia force, but the crank slider The inertia force of the structure can not be completely eliminated. To reduce the inertia force, the weight of the slider and the connecting rod, the eccentricity and the length of the connecting rod are reduced. The deformation of the connecting rod is the largest in the direction of Z to the length, and the stress of the connecting rod is far less than the allowable stress. The maximum deformation of the crankshaft end is calculated and the crankshaft is calculated in the range of the crankshaft permissible deformation. The torsion stress is far less than its torsional allowable stress. With the modal analysis of the ANSYS software, the resonance phenomenon occurs when the frequency is 40HZ, and the resonance phenomenon occurs when the crankshaft is at 30HZ. The maximum natural frequency of the first ten steps of the needle beam is 2.1561HZ, but the needle beam will quickly cross the needle beam during the starting process of the needle punching machine. Therefore, the factor of the needle beam can be considered as a secondary factor in the future improvement of the vibration characteristics of the needle punching machine. The maximum working frequency of the needle punching machine is 20HZ, and the resonance phenomenon of the crank slider mechanism will not be caused. The vibration of the vibration signal after the filter is measured by the vibration of the crank slider mechanism of the needle punching machine and the wave pattern of the vibration signal after the filter. The analysis of the spectrum shows that the main cause of the vibration of the crank slider mechanism is rotor imbalance and rubbing.
Finally, three different optimization schemes are proposed. First, by drawing the theoretical acceleration curve of the slider, the acceleration is changed in theory by changing the relative parameters of the acceleration. The second is to simulate the ADMAS by changing the different modulus of elasticity, damping coefficient, and the friction coefficient, that is, to replace the better material. In the end, the vibration amplitude was reduced to three to five times that of the original, after installing the flywheel and the counterweight block and reinstalling the crankshaft and rocker device.
【學(xué)位授予單位】：西安工程大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2012
【分類號(hào)】：TH112

【參考文獻(xiàn)】

相關(guān)期刊論文 前9條

1 汪之光;淺談針刺機(jī)的設(shè)計(jì)[J];北京紡織;2005年04期

2 王慧彩,趙德有;粘彈性阻尼夾層板動(dòng)力特性分析及其試驗(yàn)研究[J];船舶力學(xué);2005年04期

3 鞠永農(nóng);;淺談國產(chǎn)針刺機(jī)的開發(fā)現(xiàn)狀及發(fā)展趨勢(shì)[J];產(chǎn)業(yè)用紡織品;2010年01期

4 王淑貞;楊建成;;針刺機(jī)偏心機(jī)構(gòu)的平衡分析[J];紡織機(jī)械;2009年06期

5 王淑貞;藺軍;;針刺機(jī)機(jī)構(gòu)設(shè)計(jì)的改進(jìn)[J];紡織機(jī)械;2011年02期

6 趙寧濤;孫榮祿;;針刺機(jī)振動(dòng)問題研究[J];非織造布;2009年06期

7 賈民平;楊建文;;滾動(dòng)軸承振動(dòng)的周期平穩(wěn)性分析及故障診斷[J];機(jī)械工程學(xué)報(bào);2007年01期

8 童小燕;王德俊;;40CrNiMo材料循環(huán)滯回環(huán)的分析與計(jì)算[J];試驗(yàn)技術(shù)與試驗(yàn)機(jī);1988年01期

9 趙德勝;李彩琴;張雪;;間隙對(duì)曲柄滑塊機(jī)構(gòu)靈敏度的影響研究[J];西安郵電學(xué)院學(xué)報(bào);2011年05期

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