本文選題：多繩摩擦式提升機(jī) + 首繩更換裝置�。� 參考：《太原理工大學(xué)》2015年碩士論文

【摘要】：隨著我國礦井提升技術(shù)的不斷進(jìn)步,多繩摩擦式提升機(jī)在立井提升系統(tǒng)中得到了廣泛使用。但其提升鋼絲繩更換工作較為頻繁,且需在井筒作業(yè),作業(yè)人員多,難度大,勞動(dòng)強(qiáng)度高�，F(xiàn)有換繩裝置大幅減少了換繩作業(yè)時(shí)間,提高了換繩的安全性和可靠性。但現(xiàn)有換繩裝置普遍存在整體性差,不能多繩同步更換,無法實(shí)現(xiàn)不同繩徑首繩更換等問題,甚至存在損繩、遛繩以及破壞提升系統(tǒng)等安全隱患,嚴(yán)重影響了礦井的安全高效生產(chǎn)。因此,研究設(shè)計(jì)一種新型首繩更換裝置具有重要意義。 本文分析了現(xiàn)有換繩工藝及換繩輔助裝置存在的不足與缺陷,提出了新型首繩更換裝置的設(shè)計(jì)目標(biāo),經(jīng)過方案論證確定了多繩同步連續(xù)快速更換裝置的設(shè)計(jì)方案,明確了各機(jī)械系統(tǒng)組成和工作原理,并針對(duì)換繩動(dòng)作要求設(shè)計(jì)了裝置液壓系統(tǒng),對(duì)液壓系統(tǒng)機(jī)能和油路運(yùn)行特性進(jìn)行了分析。 利用仿真軟件AMEsim對(duì)多繩同步連續(xù)快速更換裝置液壓系統(tǒng)建立了仿真模型,針對(duì)液壓系統(tǒng)動(dòng)態(tài)特性,分別對(duì)系統(tǒng)壓力以及電液換向閥額定流量等關(guān)鍵參數(shù)設(shè)置不同參數(shù)進(jìn)行仿真。通過對(duì)比仿真數(shù)據(jù),在滿足裝置設(shè)計(jì)要求的前提下,綜合考慮系統(tǒng)穩(wěn)定性及節(jié)能因素,合理選定系統(tǒng)壓力以及電液換向閥額定流量等參數(shù)并對(duì)其進(jìn)行優(yōu)化。 對(duì)首繩更換裝置核心機(jī)構(gòu)連續(xù)送繩裝置鏈傳動(dòng)進(jìn)行嚙合機(jī)理分析及ADAMS動(dòng)力學(xué)仿真,確定了鏈輪齒數(shù)為影響連續(xù)送繩裝置動(dòng)態(tài)特性及送繩穩(wěn)定的關(guān)鍵因素,發(fā)現(xiàn)隨著鏈輪輪齒數(shù)量的增加,鏈傳動(dòng)多邊形效應(yīng)降低,鏈節(jié)速度變化較小,從動(dòng)輪角速度變化逐漸平緩,單個(gè)鏈節(jié)受力降低,鏈傳動(dòng)穩(wěn)定性提高,送繩過程中鋼絲繩波動(dòng)減小,送繩穩(wěn)定性和安全性提高。 應(yīng)用ADAMS動(dòng)力學(xué)仿真軟件建立連續(xù)送繩裝置仿真模型,對(duì)不同換繩工況下鏈傳動(dòng)及鋼絲繩動(dòng)態(tài)特性進(jìn)行分析,連續(xù)送繩裝置與傳統(tǒng)送繩裝置相比送繩過程中沖擊較小,送繩速度快且運(yùn)行平穩(wěn),但當(dāng)送繩速度或送繩載荷增加時(shí),連續(xù)送繩裝置及鋼絲繩動(dòng)態(tài)特性波動(dòng)加劇,裝置送繩安全性和可靠性降低,在換繩過程中需根據(jù)實(shí)際換繩工況進(jìn)行送繩參數(shù)選擇。 對(duì)超速抓捕裝置進(jìn)行機(jī)液耦合仿真,驗(yàn)證了其機(jī)械系統(tǒng)和液壓系統(tǒng)能夠在不同工況下實(shí)現(xiàn)協(xié)調(diào)動(dòng)作對(duì)鋼絲繩進(jìn)行有效抓捕,保證了換繩裝置在首繩更換過程中的安全性。通過對(duì)比仿真數(shù)據(jù)發(fā)現(xiàn)當(dāng)鋼絲繩載荷一定時(shí),捕繩時(shí)間隨遛繩速度的增加而減小；遛繩速度一定時(shí),捕繩時(shí)間隨鋼絲繩載荷的增加而減小。
[Abstract]:With the development of mine hoisting technology in China, multi-rope friction hoist has been widely used in shaft hoisting system. But its lifting wire rope replacement work is more frequent, and needs to work in the wellbore, the operator is more difficult, the labor intensity is high. The existing rope changing device greatly reduces the rope changing operation time and improves the safety and reliability of rope changing. However, the existing rope changing devices generally have some problems, such as poor integrity, unable to replace multiple rope synchronously, unable to replace the first rope with different rope diameter, and even some safety hidden dangers such as damaged rope, rope walking and damage to the lifting system, etc. Has seriously affected the mine safe and efficient production. Therefore, it is of great significance to study and design a new type of head rope replacement device. In this paper, the shortcomings and defects of the existing rope changing technology and rope changing auxiliary device are analyzed, and the design goal of the new type of rope replacement device is put forward, and the design scheme of the multi-rope synchronous and continuous rapid replacement device is determined through the scheme demonstration. The composition and working principle of each mechanical system are clarified and the hydraulic system of the device is designed according to the requirements of rope changing operation. The function of the hydraulic system and the operating characteristics of the oil circuit are analyzed. The simulation model of hydraulic system of multi-rope synchronous and continuous rapid replacement device is established by using the simulation software AMEsim. According to the dynamic characteristics of hydraulic system, different parameters such as system pressure and the rated flow rate of electro-hydraulic directional valve are set up respectively. By comparing the simulation data and considering the system stability and energy saving factors, the parameters such as system pressure and the rated flow rate of the electro-hydraulic directional valve are selected and optimized under the premise of meeting the requirements of the device design. The meshing mechanism and ADAMS dynamics simulation of the chain drive of the continuous rope feeding device of the core mechanism of the head rope replacement device are analyzed. It is determined that the number of the sprocket teeth is the key factor affecting the dynamic characteristics of the continuous rope feeding device and the stability of the rope feeding device. It is found that with the increase of the number of sprocket teeth, the polygon effect of chain transmission decreases, and the change of chain speed is small. The change of angular velocity of driving wheel is gradually smooth, the force of single link decreases, and the stability of chain transmission is improved. In the process of rope feeding, the fluctuation of wire rope is reduced, and the stability and safety of wire rope are improved. The simulation model of continuous rope feeding device is established by using ADAMS dynamic simulation software. The dynamic characteristics of chain transmission and wire rope under different rope changing conditions are analyzed. Compared with the traditional rope feeding device, the continuous rope feeding device has less impact on the rope feeding process. The speed of rope feeding is fast and running smoothly, but when the speed or load increases, the fluctuation of dynamic characteristics of continuous rope feeding device and wire rope is increased, and the safety and reliability of the device are decreased. In the course of changing rope, the parameters of rope feeding should be selected according to the actual condition of changing rope. The mechanism and liquid coupling simulation of the overspeed capture device is carried out, which verifies that the mechanical system and hydraulic system can coordinate the action to catch the wire rope effectively under different working conditions, thus ensuring the safety of the wire rope changing device in the process of the first rope replacement. By comparing the simulation data, it is found that when the wire rope load is constant, the rope catching time decreases with the increase of the rope walking speed, and with the constant rope walking speed, the rope catching time decreases with the increase of the wire rope load.
【學(xué)位授予單位】：太原理工大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2015
【分類號(hào)】：TD534

【參考文獻(xiàn)】

相關(guān)期刊論文 前10條

1 赫雄;ADAMS動(dòng)力學(xué)仿真算法及參數(shù)設(shè)置分析[J];傳動(dòng)技術(shù);2005年03期

2 馬建國;陳達(dá);;摩擦式提升機(jī)提升鋼絲繩更換工藝探析[J];硅谷;2013年18期

3 王曉光;;多繩摩擦式提升機(jī)單導(dǎo)互帶換繩法[J];礦業(yè)工程;2014年02期

4 趙亮;趙繼云;;礦井提升機(jī)步進(jìn)式自動(dòng)放繩裝置[J];機(jī)床與液壓;2008年09期

5 梁利華;寧繼鵬;史洪宇;;基于AMESim與ADAMS聯(lián)合仿真技術(shù)的減搖鰭液壓系統(tǒng)仿真研究[J];機(jī)床與液壓;2009年08期

6 劉海蓉;芮執(zhí)元;魯春朋;剡昌峰;;冷卻運(yùn)輸機(jī)滾子輸送鏈的接觸分析研究[J];計(jì)算機(jī)與數(shù)字工程;2007年03期

7 蒲明輝;吳江;;基于ADAMS的鏈傳動(dòng)多體動(dòng)力學(xué)模型研究[J];機(jī)械設(shè)計(jì)與研究;2008年02期

8 薛云娜,王勇,王憲倫;齒形鏈傳動(dòng)嚙合沖擊機(jī)理[J];機(jī)械設(shè)計(jì);2005年09期

9 許雷;丁武學(xué);;基于ADAMS的特氟龍輸送帶鏈傳動(dòng)多邊形效應(yīng)分析[J];機(jī)械制造;2011年07期

10 榮長(zhǎng)發(fā),王嚴(yán)興,寧興江;滾子鏈傳動(dòng)嚙合沖擊載荷特性分析[J];礦山機(jī)械;2003年07期

，

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