雙節(jié)距變節(jié)距齒形輸送鏈的嚙合機(jī)理與試驗(yàn)研究
發(fā)布時(shí)間：2018-07-17 03:35
【摘要】：隨著汽車工業(yè)的發(fā)展，汽車裝配線上用的傳統(tǒng)鏈?zhǔn)捷斔蜋C(jī)的性能已經(jīng)無法滿足汽車裝配速度和裝配質(zhì)量提高�，F(xiàn)有的汽車裝配線上的鏈?zhǔn)捷斔蜋C(jī)均采用雙節(jié)距滾子輸送鏈作為牽引件和承載件。由于雙節(jié)距滾子輸送鏈系統(tǒng)自身結(jié)構(gòu)的限制，隨著裝配速度的提高，噪聲大、磨損劇烈、穩(wěn)定性差以及由于其內(nèi)節(jié)內(nèi)寬大于零件尺寸導(dǎo)致整線卡機(jī)等問題相繼出現(xiàn)，嚴(yán)重影響了裝配線的裝配速度和裝配質(zhì)量。齒形鏈傳動(dòng)系統(tǒng)具有高速、低噪聲、低磨損、高穩(wěn)定性等諸多優(yōu)點(diǎn)，被廣泛的應(yīng)用于傳動(dòng)領(lǐng)域，但是由于其自重過大，應(yīng)用于輸送機(jī)中時(shí)，會(huì)造成較大的沖擊、噪聲和振動(dòng)，影響輸送性能。因此，研究如何降低齒形鏈的自重，，使其可以應(yīng)用在鏈?zhǔn)捷斔蜋C(jī)上，以滿足鏈?zhǔn)捷斔蜋C(jī)對(duì)輸送速度、位置精度、穩(wěn)定性和環(huán)境友好性等方面的要求，具有重要的理論研究?jī)r(jià)值和工程應(yīng)用意義。 本文首先介紹了鏈傳動(dòng)技術(shù)與鏈?zhǔn)捷斔蜋C(jī)在各領(lǐng)域的應(yīng)用情況以及它們的國(guó)內(nèi)外發(fā)展現(xiàn)狀，突出強(qiáng)調(diào)了輸送鏈在鏈?zhǔn)捷斔蜋C(jī)中的重要作用，以及鏈?zhǔn)捷斔蜋C(jī)在國(guó)民經(jīng)濟(jì)中的重要作用，反映出本文對(duì)雙節(jié)距變節(jié)距齒形輸送鏈研究的學(xué)術(shù)價(jià)值和實(shí)際工程意義。通過分析齒形鏈無法應(yīng)用于鏈?zhǔn)捷斔蜋C(jī)中的原因，在國(guó)內(nèi)外學(xué)者對(duì)齒形鏈研究的基礎(chǔ)上，基于傳統(tǒng)齒形鏈的結(jié)構(gòu)，首次提出了適用于鏈?zhǔn)捷斔蜋C(jī)的雙節(jié)距變節(jié)距齒形輸送鏈的結(jié)構(gòu)。 本文首次提出了雙節(jié)距變節(jié)距齒形輸送鏈的結(jié)構(gòu)。該鏈條具有內(nèi)-外復(fù)合嚙合機(jī)制，采用對(duì)滾式鉸鏈，圍鏈節(jié)距是傳統(tǒng)齒形鏈的兩倍，工作鏈板具有三個(gè)齒，其中兩側(cè)齒為工作齒，中間齒為減磨齒；給出了工作鏈板、鉸鏈、邊板和導(dǎo)板的主要設(shè)計(jì)參數(shù)及其計(jì)算方法，且根據(jù)工程實(shí)際，設(shè)計(jì)了新型的齒形鏈連接接頭；根據(jù)嚙合和滾切原理，建立了雙節(jié)距變節(jié)距齒形輸送鏈—單節(jié)距齒形鏈—鏈輪滾刀—漸開線鏈輪的嚙合設(shè)計(jì)體系，研究了雙節(jié)距變節(jié)距齒形輸送鏈與漸開線鏈輪的主要設(shè)計(jì)參數(shù)之間的耦合關(guān)系。以節(jié)距P=25.4mm，鏈輪齒數(shù)z=38為例，利用CAD軟件繪制了二者的圖紙，二者圍嚙良好；制造樣鏈，進(jìn)行稱重試驗(yàn)和拉斷試驗(yàn)，對(duì)數(shù)據(jù)整理后發(fā)現(xiàn)，在等抗拉載荷條件下，雙節(jié)距變節(jié)距齒形輸送鏈與傳統(tǒng)齒形鏈相比，單位長(zhǎng)度質(zhì)量降低了30%以上。從而，驗(yàn)證了雙節(jié)距變節(jié)距齒形輸送鏈與鏈輪設(shè)計(jì)方法的合理性與正確性。 成功將內(nèi)-外復(fù)合嚙合機(jī)制引入到雙節(jié)距變節(jié)距齒形輸送鏈中，深入分析了雙節(jié)距變節(jié)距齒形輸送鏈與漸開線鏈輪的內(nèi)-外復(fù)合嚙合過程，得出了其嚙合周期為4z，且可以劃分五個(gè)階段：當(dāng)前鏈節(jié)的內(nèi)嚙合階段→前一鏈節(jié)的外嚙合定位階段→當(dāng)前鏈節(jié)懸浮階段→下一鏈節(jié)的內(nèi)嚙合階段→當(dāng)前鏈節(jié)的外嚙合定位階段；利用平面坐標(biāo)變換原理，建立了雙節(jié)距變節(jié)距齒形輸送鏈系統(tǒng)的嚙合數(shù)學(xué)模型，確定了雙節(jié)距變節(jié)距齒形輸送鏈與漸開線鏈輪的初始嚙合位置、交變位置以及定位位置。 在雙節(jié)距變節(jié)距齒形輸送鏈嚙合機(jī)理研究的基礎(chǔ)上，對(duì)其結(jié)構(gòu)特性、運(yùn)動(dòng)不均勻性和嚙合沖擊特性進(jìn)行了理論分析和仿真研究。結(jié)果表明：雙節(jié)距變節(jié)距齒形輸送鏈的內(nèi)-外復(fù)合嚙合機(jī)制、變節(jié)距特性和變節(jié)圓特性使其多邊形效應(yīng)、運(yùn)動(dòng)不均勻性和嚙合沖擊力與雙節(jié)距滾子輸送鏈相比均明顯降低。在相同的仿真條件下，與雙節(jié)距滾子輸送鏈相比，其緊邊橫向波動(dòng)量降低了24.18%，水平運(yùn)動(dòng)速度不均勻性降低了45.61%，從動(dòng)輪轉(zhuǎn)速不均勻性降低了23.13%，嚙合沖擊力降低了52.06%。可以推知：雙節(jié)距變節(jié)距齒形輸送鏈的輸送位置準(zhǔn)確度優(yōu)于雙節(jié)距滾子輸送鏈。 針對(duì)汽車裝配線用水平式輸送機(jī)，建立了雙節(jié)距變節(jié)距齒形輸送鏈的受力情況數(shù)學(xué)模型，對(duì)其運(yùn)動(dòng)過程中的靜載荷和附加動(dòng)載荷進(jìn)行了理論分析，并與雙節(jié)距滾子輸送鏈進(jìn)行了對(duì)比。結(jié)果顯示：雙節(jié)距變節(jié)距齒形輸送鏈的靜載荷除了包括傳統(tǒng)系統(tǒng)的齒形鏈系統(tǒng)的靜力，還包括鏈條與導(dǎo)軌之間的摩擦力；由于運(yùn)動(dòng)不均勻性引起的動(dòng)載荷明顯低于雙節(jié)距滾子輸送鏈�？梢酝浦弘p節(jié)距變節(jié)距齒形輸送鏈的受力情況優(yōu)于雙節(jié)距滾子輸送鏈。 利用封閉力流式試驗(yàn)臺(tái)對(duì)雙節(jié)距變節(jié)距齒形輸送鏈系統(tǒng)和雙節(jié)距滾子輸送鏈系統(tǒng)進(jìn)行臺(tái)架試驗(yàn)，對(duì)比分析了二者的噪聲性能和磨損性能。結(jié)果表明：在轉(zhuǎn)速為200r/min，加載2kN時(shí)，與雙節(jié)距滾子輸送鏈系統(tǒng)相比，雙節(jié)距變節(jié)距齒形輸送鏈系統(tǒng)的噪聲降低了3.5dB，且隨著轉(zhuǎn)速提高，噪聲降低量增大；相同轉(zhuǎn)速條件下，雙節(jié)距變節(jié)距齒形輸送鏈系統(tǒng)的噪聲波動(dòng)量為雙節(jié)距變節(jié)距齒形輸送鏈系統(tǒng)的33%左右；經(jīng)過250h的磨損試驗(yàn)后，雙節(jié)距變節(jié)距齒形輸送鏈的磨損伸長(zhǎng)量?jī)H為0.182%，與雙節(jié)距滾子輸送鏈相比，其磨損伸長(zhǎng)率降低了的45.5%�？梢姡号c雙節(jié)距滾子輸送鏈相比，雙節(jié)距變節(jié)距齒形輸送鏈的噪聲低、耐磨損以及具有高穩(wěn)定性和環(huán)境友好性。 將雙節(jié)距變節(jié)距齒形輸送鏈安裝在汽車裝配線用鏈?zhǔn)捷斔蜋C(jī)上，對(duì)其進(jìn)行了為期40周的現(xiàn)場(chǎng)磨損試驗(yàn)，結(jié)構(gòu)表明：雙節(jié)距變節(jié)距齒形輸送鏈在經(jīng)過40周的現(xiàn)場(chǎng)磨損后，磨損狀況良好，磨損伸長(zhǎng)率僅為0.13%，鏈?zhǔn)捷斔蜋C(jī)運(yùn)行良好。可以證明其結(jié)構(gòu)的合理性以及應(yīng)用于鏈?zhǔn)捷斔蜋C(jī)中的可行性。 綜上所述，本文研究的雙節(jié)距變節(jié)距齒形輸送鏈與傳統(tǒng)齒形鏈相比,單位長(zhǎng)度質(zhì)量明顯降低；與雙節(jié)距滾子輸送鏈相比,具有更高的位置精度、更高穩(wěn)定性和環(huán)境友好性，適合應(yīng)用在鏈?zhǔn)捷斔蜋C(jī)中。 本文得到了國(guó)家總裝部項(xiàng)目“CDX01項(xiàng)目鏈傳動(dòng)系統(tǒng)降噪”的支持。
[Abstract]:With the development of automobile industry , the performance of traditional chain conveyor used in automobile assembly line has been unable to meet the automobile assembling speed and assembly quality . The chain conveyor on the existing automobile assembly line has many advantages such as high speed , low noise , low wear , high stability and so on .
This paper first introduces the application of chain drive technology and chain conveyor in each field and their development status at home and abroad , highlights the important role of chain conveyor in chain conveyor and the important role of chain conveyor in national economy .
In this paper , the structure of double - pitch variable - pitch tooth - shaped conveying chain is proposed for the first time . The chain has internal - external composite meshing mechanism , which is double the traditional tooth chain , and the working link plate has three teeth , the two side teeth are working teeth , and the middle teeth are friction reducing teeth ;
The main design parameters and calculation methods of working link plate , hinge , side plate and guide plate are given , and a new type of tooth chain connecting joint is designed according to the engineering practice .
Based on the principle of meshing and hobbing , the meshing design system of double pitch variable pitch tooth chain - single pitch tooth chain - sprocket hob - involute sprocket is established , and the coupling relationship between the double pitch variable pitch profile conveyor chain and the main design parameters of the involute sprocket is studied .
After finishing the data , it is found that the quality of the unit length is reduced by more than 30 % compared with the traditional tooth chain , and the rationality and the correctness of the double - pitch variable - pitch tooth - shaped conveying chain and the sprocket design method are verified .
The internal - external composite meshing mechanism of the inner - outer composite meshing mechanism is successfully introduced into the double - pitch variable - pitch tooth - shaped conveying chain , and the internal - external composite meshing process of the double - pitch variable - pitch tooth - shaped conveying chain and the involute sprocket is deeply analyzed , and the meshing period is 4z , and the five stages can be divided into five stages : the inner engagement stage of the current link , the outer engagement positioning stage of the previous link , the inner engagement stage of the next link and the outer engagement positioning stage of the current link ;
Based on the principle of plane coordinate transformation , the meshing mathematical model of double pitch variable pitch tooth profile conveyor chain system is established , and the initial meshing position , alternating position and positioning position of the double pitch variable pitch tooth profile conveying chain and the involute sprocket are determined .
On the basis of the study of the meshing mechanism of the double - pitch variable - pitch tooth - shaped conveying chain , the structural characteristics , the non - uniformity of the motion and the meshing impact are analyzed and simulated . The results show that the cross - section fluctuation of the double - pitch - pitch - pitch tooth - shaped conveying chain is reduced by 24.18 % , the non - uniformity of the moving speed and the meshing impact force are reduced by 24.18 % , the non - uniformity of the moving speed is reduced by 23.13 % , and the meshing impact force is reduced by 52.06 % . It can be concluded that the accuracy of the transmission position of the double - pitch variable - pitch tooth - shaped conveying chain is better than that of the double - pitch roller conveying chain .
Aiming at the horizontal conveyor for automobile assembly line , a mathematical model of the stress condition of double - pitch variable - pitch tooth - shaped conveying chain is established , and the static load and the additional dynamic load in the motion process are analyzed theoretically and compared with the double - pitch roller conveying chain . The results show that the static load of the double - pitch variable - pitch tooth - shaped conveying chain comprises the static force of the tooth - shaped chain system of the traditional system , and also the friction force between the chain and the guide rail ;
Because the dynamic load caused by the non - uniformity of motion is obviously lower than that of the double - pitch roller conveying chain , it can be concluded that the stress condition of the double - pitch variable - pitch tooth - shaped conveying chain is better than that of the double - pitch roller conveying chain .
The results show that the noise of the double - pitch variable - pitch tooth - shaped conveyor chain system is reduced by 3.5dB when the rotating speed is 200r / min , and the noise reduction is increased with the increase of the rotating speed .
Under the same rotating speed condition , the noise fluctuation quantity of the double - pitch variable - pitch tooth - shaped conveying chain system is about 33 % of the double - pitch variable - pitch tooth - shaped conveying chain system ;
After 250h of wear test , the wear elongation of the double pitch variable pitch profile conveyor chain is only 0.182 % , and its wear elongation is reduced by 44.5 % compared with the double pitch roller conveyor chain . It can be seen that the double pitch variable pitch profile conveyor chain has low noise , abrasion resistance and high stability and environmental friendliness as compared with the double pitch roller conveyor chain .
A 40 - week field wear test is carried out to install the double - pitch variable - pitch toothed conveyor chain on the chain conveyor for automobile assembly line . The structure shows that after 40 weeks of field wear , the wear condition is good , the wear elongation is only 0.13 % , the running of the chain conveyor is good . The rationality of its structure and the feasibility of applying it in chain conveyor can be proved .
In conclusion , compared with the traditional tooth - shaped chain , the double - pitch - pitch - pitch - pitch tooth - shaped conveying chain is obviously lower than that of the traditional tooth chain .
Compared with the double - pitch roller conveying chain , the double - pitch roller conveying chain has higher position precision , higher stability and environmental friendliness , and is suitable for being applied in a chain conveyor .
This paper gives the support of " noise reduction of CDX01 project chain drive system " of the project " CDX01 " .
【學(xué)位授予單位】：吉林大學(xué)
【學(xué)位級(jí)別】：博士
【學(xué)位授予年份】：2014
【分類號(hào)】：TH233;TH132.45
本文編號(hào)：2128825
[Abstract]:With the development of automobile industry , the performance of traditional chain conveyor used in automobile assembly line has been unable to meet the automobile assembling speed and assembly quality . The chain conveyor on the existing automobile assembly line has many advantages such as high speed , low noise , low wear , high stability and so on .
This paper first introduces the application of chain drive technology and chain conveyor in each field and their development status at home and abroad , highlights the important role of chain conveyor in chain conveyor and the important role of chain conveyor in national economy .
In this paper , the structure of double - pitch variable - pitch tooth - shaped conveying chain is proposed for the first time . The chain has internal - external composite meshing mechanism , which is double the traditional tooth chain , and the working link plate has three teeth , the two side teeth are working teeth , and the middle teeth are friction reducing teeth ;
The main design parameters and calculation methods of working link plate , hinge , side plate and guide plate are given , and a new type of tooth chain connecting joint is designed according to the engineering practice .
Based on the principle of meshing and hobbing , the meshing design system of double pitch variable pitch tooth chain - single pitch tooth chain - sprocket hob - involute sprocket is established , and the coupling relationship between the double pitch variable pitch profile conveyor chain and the main design parameters of the involute sprocket is studied .
After finishing the data , it is found that the quality of the unit length is reduced by more than 30 % compared with the traditional tooth chain , and the rationality and the correctness of the double - pitch variable - pitch tooth - shaped conveying chain and the sprocket design method are verified .
The internal - external composite meshing mechanism of the inner - outer composite meshing mechanism is successfully introduced into the double - pitch variable - pitch tooth - shaped conveying chain , and the internal - external composite meshing process of the double - pitch variable - pitch tooth - shaped conveying chain and the involute sprocket is deeply analyzed , and the meshing period is 4z , and the five stages can be divided into five stages : the inner engagement stage of the current link , the outer engagement positioning stage of the previous link , the inner engagement stage of the next link and the outer engagement positioning stage of the current link ;
Based on the principle of plane coordinate transformation , the meshing mathematical model of double pitch variable pitch tooth profile conveyor chain system is established , and the initial meshing position , alternating position and positioning position of the double pitch variable pitch tooth profile conveying chain and the involute sprocket are determined .
On the basis of the study of the meshing mechanism of the double - pitch variable - pitch tooth - shaped conveying chain , the structural characteristics , the non - uniformity of the motion and the meshing impact are analyzed and simulated . The results show that the cross - section fluctuation of the double - pitch - pitch - pitch tooth - shaped conveying chain is reduced by 24.18 % , the non - uniformity of the moving speed and the meshing impact force are reduced by 24.18 % , the non - uniformity of the moving speed is reduced by 23.13 % , and the meshing impact force is reduced by 52.06 % . It can be concluded that the accuracy of the transmission position of the double - pitch variable - pitch tooth - shaped conveying chain is better than that of the double - pitch roller conveying chain .
Aiming at the horizontal conveyor for automobile assembly line , a mathematical model of the stress condition of double - pitch variable - pitch tooth - shaped conveying chain is established , and the static load and the additional dynamic load in the motion process are analyzed theoretically and compared with the double - pitch roller conveying chain . The results show that the static load of the double - pitch variable - pitch tooth - shaped conveying chain comprises the static force of the tooth - shaped chain system of the traditional system , and also the friction force between the chain and the guide rail ;
Because the dynamic load caused by the non - uniformity of motion is obviously lower than that of the double - pitch roller conveying chain , it can be concluded that the stress condition of the double - pitch variable - pitch tooth - shaped conveying chain is better than that of the double - pitch roller conveying chain .
The results show that the noise of the double - pitch variable - pitch tooth - shaped conveyor chain system is reduced by 3.5dB when the rotating speed is 200r / min , and the noise reduction is increased with the increase of the rotating speed .
Under the same rotating speed condition , the noise fluctuation quantity of the double - pitch variable - pitch tooth - shaped conveying chain system is about 33 % of the double - pitch variable - pitch tooth - shaped conveying chain system ;
After 250h of wear test , the wear elongation of the double pitch variable pitch profile conveyor chain is only 0.182 % , and its wear elongation is reduced by 44.5 % compared with the double pitch roller conveyor chain . It can be seen that the double pitch variable pitch profile conveyor chain has low noise , abrasion resistance and high stability and environmental friendliness as compared with the double pitch roller conveyor chain .
A 40 - week field wear test is carried out to install the double - pitch variable - pitch toothed conveyor chain on the chain conveyor for automobile assembly line . The structure shows that after 40 weeks of field wear , the wear condition is good , the wear elongation is only 0.13 % , the running of the chain conveyor is good . The rationality of its structure and the feasibility of applying it in chain conveyor can be proved .
In conclusion , compared with the traditional tooth - shaped chain , the double - pitch - pitch - pitch - pitch tooth - shaped conveying chain is obviously lower than that of the traditional tooth chain .
Compared with the double - pitch roller conveying chain , the double - pitch roller conveying chain has higher position precision , higher stability and environmental friendliness , and is suitable for being applied in a chain conveyor .
This paper gives the support of " noise reduction of CDX01 project chain drive system " of the project " CDX01 " .
【學(xué)位授予單位】：吉林大學(xué)
【學(xué)位級(jí)別】：博士
【學(xué)位授予年份】：2014
【分類號(hào)】：TH233;TH132.45
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