双节距分时啮合齿形输送链的啮合机理及试验研究
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摘要
我国工业发展迅速，汽车的生产与需求都大幅上升，一辆汽车的产出，往往需要经过上万道工序，组成的几百条流水线来完成的。链式输送机广泛用于汽车装配流水线的输送工作，现有输送机上的输送链均为滚子链，随着对输送机可靠性、同步性和环境友好性要求的提高，滚子输送链的自身特点制约着链式输送机的进一步发展，亟需研究新型输送链系统来提高几百条流水线上链式输送机的同步性、可靠性和环境友好性。本文通过分析输送链对输送机性能的影响和齿形链的性能，提出了双节距分时啮合齿形输送链，并开展了双节距分时啮合齿形输送链系统各部件参数的数学建模、啮合分析、可靠性和环境友好性的研究。
以应用齿形链在链式输送机上为目标，提出了双节距分时啮合齿形输送链，双节距分时啮合齿形输送链链板的设计特点，双倍节距是在啮合节圆上双倍节距，每个链板上分布三个齿，中间齿廓和一、三齿廓的外齿廓为直线齿廓，一、三齿廓的内齿廓为外凸的曲线齿廓。双节距分时啮合齿形输送链与单倍节距相同的外啮合齿形链相比，以单倍节距为15.875mm，链轮齿数45为例，每节相同片数的链条，每米自重降低了24.6%，根据双节距分时啮合齿形输送链链条—链轮—链轮加工刀具的相关耦合参数，设计了直线齿廓双节距分时啮合齿形输送链链轮和负变位渐开线齿廓双节距分时啮合齿形输送链链轮，建立了渐开线齿廓双节距分时啮合齿形输送链链轮负变位系数的数学模型，对与负变位渐开线齿廓双节距分时啮合齿形输送链链轮相啮合的双节距分时啮合齿形输送链链条进行了参数修正。针对工程实际，设计了适用于双节距分时啮合齿形输送链链式输送机的张紧装置。
对双节距分时啮合齿形输送链系统的啮合理论进行了系统的研究，双节距分时啮合齿形输送链紧边啮入过程在一个啮合周期内分为三个阶段：随着链轮的转动外凸的内齿廓与链轮接触啮合、转化为相邻链节的外齿廓啮合和中间齿廓啮合定位。对双节距分时啮合齿形链进行了假想坐标系的建立，利用坐标变换理论进行双节距分时啮合齿形输送链紧边啮入过程中一个啮合周期的数学建模。通过对双节距分时啮合齿形输送链系统的运动学和动力学分析，得出双节距分时啮合齿形输送链系统的速度、加速度的变化和双节距分时啮合齿形输送链链式输送机在不同输送方式下，链条承载的数学模型。把双节距分时啮合齿形输送链链条的紧边简化成无质量的弦线连接的一组离散质量系统，求出双节距分时啮合齿形输送链系统紧边的固有频率。
根据双节距分时啮合齿形输送链链条和直线齿廓双节距分时啮合齿形输送链链轮的设计参数进行实体建模，以单倍节距为15.875mm，链轮齿数45为例，建立了双节距分时啮合齿形输送链系统的运动学模型和啮合冲击模型，动态的模拟了双节距分时啮合齿形输送链系统的啮合过程，对双节距分时啮合齿形输送链和双节距滚子输送链进行对比仿真，仿真结果显示，双节距分时啮合齿形输送链系统的紧边链条波动降低59%、瞬间接触力最大值只是双节距滚子输送链系统的51.9%。
利用封闭力流链式试验台对双节距分时啮合齿形输送链系统和双节距滚子输送链系统进行噪声和磨损伸长的对比试验，以单倍节距为15.875mm，链轮齿数45为例。试验结果显示，与双节距滚子输送链系统相比，在转速为200rpm，载荷为2kN时，双节距分时啮合齿形输送链的噪声降低2dB，随着转速的增加，噪声差值明显增大；在转速为300rpm，载荷为2kN时，250小时的磨损伸长试验，试验结果显示磨损伸长率仅为双节距滚子输送链的46%，因此双节距分时啮合齿形输送链系统提高了链式输送机的可靠性和环境友好性。
根据研究成果申请了发明专利“双节距分时啮合齿形链链板”，专利号：201110233079.9；授权公告号：CN102287483B。
本文在总装备部“CDX01项目链传动系统降噪”的资助和支持下，对链式输送机进行研究，在深入分析双节距分时啮合齿形输送链的啮合理论的基础上，提出了双节距分时啮合齿形输送链系统的设计方法，并对单倍节距为15.875mm，链轮齿数为45的双节距分时啮合齿形输送链系统进行了设计计算、仿真分析及试验研究。
With the rapid industrial development of our country, the production and demand ofcar has greatly increased, and the output of one car is always completed by hundredsassembly lines through thousands working procedures. The chain conveyor is widelyapplied for the conveying of assembly line of car, and the conveying chain on currentconveyor is roller chain, with the increase of requirement for the reliability, synchronismand environmental friendliness of conveyor, the further development of chain conveyor islimited by the features of roller conveying chain, which requires to research new conveyorchain system urgently to improve the reliability, synchronism and environmentalfriendliness of chain conveyor on hundreds assembly lines. In this paper, double-pitchtime-sharing meshing silent conveyor chain is proposed by analyzing how the conveyorchain affects the performance of conveyor and the performance of silent chain, and theresearch on mathematical modeling of parameter of each part, meshing analysis, reliabilityand environmental friendliness of double-pitch time-sharing meshing silent conveyor chainsystem is carried out.
The design features of double-pitch time-sharing meshing silent conveyor chain andchain plate of double-pitch time-sharing meshing silent conveyor is proposed on the basisof applying tooth chain on chain conveyor, and double-pitch is the double-pitch onmeshing pitch circle, each chain plate has three teeth, and the external tooth profile of themiddle tooth profile, the first tooth profile and the third tooth profile is straight toothprofile, and the internal tooth profile of the first and third tooth profile is convex curvetooth profile. Compared with external meshing silent conveyor chain with the same singlepitch, the self-weight of chain with same number of plate of each pitch is reduced24.6%,according to the relevant coupling parameters of double-pitch time-sharing meshing silentconveyor chain—chain wheel—cutting tool of chain wheel, the chain wheel with straighttooth profile of double-pitch time-sharing meshing silent conveyor chain and the chainwheel with negative addendum modification involute tooth profile is designed, themathematical modeling of negative addendum modification factor of chain wheel withinvolute tooth profile of double-pitch time-sharing meshing silent conveyor chain isestablished, and the parameters of chain of double-pitch time-sharing meshing silentconveyor chain which meshes with the chain wheel with negative addendum modification involute tooth profile of double-pitch time-sharing meshing silent conveyor chain arerectified. For actual situation of project, the tension device, which is applied fordouble-pitch time-sharing meshing silent conveyor, is designed.
The meshing theory of double-pitch time-sharing meshing silent conveyor chainsystem is researched systematically, and the tension side meshing process of double-pitchtime-sharing meshing silent conveyor chain is divided into three stages: the mesh betweenconvex internal tooth profile and chain wheel as chain wheel rotates, the mesh externaltooth profile that is converted to adjacent chain link, and mesh positioning of middle toothprofile. The hypothetical coordinate system of double-pitch time-sharing meshing silentconveyor chain is established, which uses coordinate transformation theory to carry out themathematical modeling of one mesh cycle in the tension side meshing process ofdouble-pitch time-sharing meshing silent conveyor chain system. The change of speed andacceleration of double-pitch time-sharing meshing silent conveyor chain system andmathematical modeling of chain load of double-pitch time-sharing meshing silent conveyorunder different conveying mode through the analysis of kinematics and dynamics ofdouble-pitch time-sharing meshing silent conveyor chain system. The tension side ofdouble-pitch time-sharing meshing silent conveyor chain is simplified to a group ofdiscrete mass system connected by massless chord line to find the natural frequency oftension side of double-pitch time-sharing meshing silent conveyor chain system.
Solid modeling is established according to the design parameters of chain ofdouble-pitch time-sharing meshing silent conveyor chain and the chain wheel with straighttooth profile of double-pitch time-sharing meshing silent conveyor chain, and kinematicalmodeling and meshing impact modeling of double-pitch time-sharing meshing silentconveyor chain system are established, which simulates the meshing process ofdouble-pitch time-sharing meshing silent conveyor chain system dynamically, andcompares the double-pitch time-sharing meshing silent conveyor chain with double-pitchroller conveyor chain, and the simulation result shows that the fluctuation of tension sidechain of double-pitch time-sharing meshing silent conveyor chain system is reduced59%,and the instant contact force is only51.9%of double-pitch roller conveyor chain system'sinstant contact force.
Comparison experiment is carried out to compare the noise and wear elongation ofdouble-pitch time-sharing meshing silent conveyor chain system and double-pitch rollerconveyor chain system by using closed force flow chain experiment table. The experimental result shows that compared with double-pitch roller conveyor chain system,when rotating speed is200rpm and load is2kN, the noise of double-pitch time-sharingmeshing silent conveyor chain is reduced2dB, with the increase of rotating speed, thevalue of noise is obviously increased, and when rotating speed is300rpm and load is2kNin250hours wear elongation experiment, the result shows that the is only46%ofdouble-pitch roller conveyor chain system, therefore, the reliability and environmentalfriendliness of chain conveyor is increased by the double-pitch time-sharing meshing silentconveyor chain system.
According to the research production to apply for a patent of invention,“double-pitchtime-sharing meshing silent chain”.patent No.:201110233079.9; notice of authorizationnumber: CN102287483B.
In this paper, the research on chain conveyor is carried out with the fund and supportfrom chain drive system for reducing the noise, which is the subproject of CDX01projectof National General Equipment Department, and the design method of double-pitchtime-sharing meshing silent conveyor chain system is proposed on the basis of furtherresearching the meshing theory of double-pitch time-sharing meshing silent conveyor chain,and design, calculation, emulation analysis and experimental research are carried out inregard to double-pitch time-sharing meshing silent conveyor chain system with15.875mmsingle pitch and45teeth.
以应用齿形链在链式输送机上为目标，提出了双节距分时啮合齿形输送链，双节距分时啮合齿形输送链链板的设计特点，双倍节距是在啮合节圆上双倍节距，每个链板上分布三个齿，中间齿廓和一、三齿廓的外齿廓为直线齿廓，一、三齿廓的内齿廓为外凸的曲线齿廓。双节距分时啮合齿形输送链与单倍节距相同的外啮合齿形链相比，以单倍节距为15.875mm，链轮齿数45为例，每节相同片数的链条，每米自重降低了24.6%，根据双节距分时啮合齿形输送链链条—链轮—链轮加工刀具的相关耦合参数，设计了直线齿廓双节距分时啮合齿形输送链链轮和负变位渐开线齿廓双节距分时啮合齿形输送链链轮，建立了渐开线齿廓双节距分时啮合齿形输送链链轮负变位系数的数学模型，对与负变位渐开线齿廓双节距分时啮合齿形输送链链轮相啮合的双节距分时啮合齿形输送链链条进行了参数修正。针对工程实际，设计了适用于双节距分时啮合齿形输送链链式输送机的张紧装置。
对双节距分时啮合齿形输送链系统的啮合理论进行了系统的研究，双节距分时啮合齿形输送链紧边啮入过程在一个啮合周期内分为三个阶段：随着链轮的转动外凸的内齿廓与链轮接触啮合、转化为相邻链节的外齿廓啮合和中间齿廓啮合定位。对双节距分时啮合齿形链进行了假想坐标系的建立，利用坐标变换理论进行双节距分时啮合齿形输送链紧边啮入过程中一个啮合周期的数学建模。通过对双节距分时啮合齿形输送链系统的运动学和动力学分析，得出双节距分时啮合齿形输送链系统的速度、加速度的变化和双节距分时啮合齿形输送链链式输送机在不同输送方式下，链条承载的数学模型。把双节距分时啮合齿形输送链链条的紧边简化成无质量的弦线连接的一组离散质量系统，求出双节距分时啮合齿形输送链系统紧边的固有频率。
根据双节距分时啮合齿形输送链链条和直线齿廓双节距分时啮合齿形输送链链轮的设计参数进行实体建模，以单倍节距为15.875mm，链轮齿数45为例，建立了双节距分时啮合齿形输送链系统的运动学模型和啮合冲击模型，动态的模拟了双节距分时啮合齿形输送链系统的啮合过程，对双节距分时啮合齿形输送链和双节距滚子输送链进行对比仿真，仿真结果显示，双节距分时啮合齿形输送链系统的紧边链条波动降低59%、瞬间接触力最大值只是双节距滚子输送链系统的51.9%。
利用封闭力流链式试验台对双节距分时啮合齿形输送链系统和双节距滚子输送链系统进行噪声和磨损伸长的对比试验，以单倍节距为15.875mm，链轮齿数45为例。试验结果显示，与双节距滚子输送链系统相比，在转速为200rpm，载荷为2kN时，双节距分时啮合齿形输送链的噪声降低2dB，随着转速的增加，噪声差值明显增大；在转速为300rpm，载荷为2kN时，250小时的磨损伸长试验，试验结果显示磨损伸长率仅为双节距滚子输送链的46%，因此双节距分时啮合齿形输送链系统提高了链式输送机的可靠性和环境友好性。
根据研究成果申请了发明专利“双节距分时啮合齿形链链板”，专利号：201110233079.9；授权公告号：CN102287483B。
本文在总装备部“CDX01项目链传动系统降噪”的资助和支持下，对链式输送机进行研究，在深入分析双节距分时啮合齿形输送链的啮合理论的基础上，提出了双节距分时啮合齿形输送链系统的设计方法，并对单倍节距为15.875mm，链轮齿数为45的双节距分时啮合齿形输送链系统进行了设计计算、仿真分析及试验研究。
With the rapid industrial development of our country, the production and demand ofcar has greatly increased, and the output of one car is always completed by hundredsassembly lines through thousands working procedures. The chain conveyor is widelyapplied for the conveying of assembly line of car, and the conveying chain on currentconveyor is roller chain, with the increase of requirement for the reliability, synchronismand environmental friendliness of conveyor, the further development of chain conveyor islimited by the features of roller conveying chain, which requires to research new conveyorchain system urgently to improve the reliability, synchronism and environmentalfriendliness of chain conveyor on hundreds assembly lines. In this paper, double-pitchtime-sharing meshing silent conveyor chain is proposed by analyzing how the conveyorchain affects the performance of conveyor and the performance of silent chain, and theresearch on mathematical modeling of parameter of each part, meshing analysis, reliabilityand environmental friendliness of double-pitch time-sharing meshing silent conveyor chainsystem is carried out.
The design features of double-pitch time-sharing meshing silent conveyor chain andchain plate of double-pitch time-sharing meshing silent conveyor is proposed on the basisof applying tooth chain on chain conveyor, and double-pitch is the double-pitch onmeshing pitch circle, each chain plate has three teeth, and the external tooth profile of themiddle tooth profile, the first tooth profile and the third tooth profile is straight toothprofile, and the internal tooth profile of the first and third tooth profile is convex curvetooth profile. Compared with external meshing silent conveyor chain with the same singlepitch, the self-weight of chain with same number of plate of each pitch is reduced24.6%,according to the relevant coupling parameters of double-pitch time-sharing meshing silentconveyor chain—chain wheel—cutting tool of chain wheel, the chain wheel with straighttooth profile of double-pitch time-sharing meshing silent conveyor chain and the chainwheel with negative addendum modification involute tooth profile is designed, themathematical modeling of negative addendum modification factor of chain wheel withinvolute tooth profile of double-pitch time-sharing meshing silent conveyor chain isestablished, and the parameters of chain of double-pitch time-sharing meshing silentconveyor chain which meshes with the chain wheel with negative addendum modification involute tooth profile of double-pitch time-sharing meshing silent conveyor chain arerectified. For actual situation of project, the tension device, which is applied fordouble-pitch time-sharing meshing silent conveyor, is designed.
The meshing theory of double-pitch time-sharing meshing silent conveyor chainsystem is researched systematically, and the tension side meshing process of double-pitchtime-sharing meshing silent conveyor chain is divided into three stages: the mesh betweenconvex internal tooth profile and chain wheel as chain wheel rotates, the mesh externaltooth profile that is converted to adjacent chain link, and mesh positioning of middle toothprofile. The hypothetical coordinate system of double-pitch time-sharing meshing silentconveyor chain is established, which uses coordinate transformation theory to carry out themathematical modeling of one mesh cycle in the tension side meshing process ofdouble-pitch time-sharing meshing silent conveyor chain system. The change of speed andacceleration of double-pitch time-sharing meshing silent conveyor chain system andmathematical modeling of chain load of double-pitch time-sharing meshing silent conveyorunder different conveying mode through the analysis of kinematics and dynamics ofdouble-pitch time-sharing meshing silent conveyor chain system. The tension side ofdouble-pitch time-sharing meshing silent conveyor chain is simplified to a group ofdiscrete mass system connected by massless chord line to find the natural frequency oftension side of double-pitch time-sharing meshing silent conveyor chain system.
Solid modeling is established according to the design parameters of chain ofdouble-pitch time-sharing meshing silent conveyor chain and the chain wheel with straighttooth profile of double-pitch time-sharing meshing silent conveyor chain, and kinematicalmodeling and meshing impact modeling of double-pitch time-sharing meshing silentconveyor chain system are established, which simulates the meshing process ofdouble-pitch time-sharing meshing silent conveyor chain system dynamically, andcompares the double-pitch time-sharing meshing silent conveyor chain with double-pitchroller conveyor chain, and the simulation result shows that the fluctuation of tension sidechain of double-pitch time-sharing meshing silent conveyor chain system is reduced59%,and the instant contact force is only51.9%of double-pitch roller conveyor chain system'sinstant contact force.
Comparison experiment is carried out to compare the noise and wear elongation ofdouble-pitch time-sharing meshing silent conveyor chain system and double-pitch rollerconveyor chain system by using closed force flow chain experiment table. The experimental result shows that compared with double-pitch roller conveyor chain system,when rotating speed is200rpm and load is2kN, the noise of double-pitch time-sharingmeshing silent conveyor chain is reduced2dB, with the increase of rotating speed, thevalue of noise is obviously increased, and when rotating speed is300rpm and load is2kNin250hours wear elongation experiment, the result shows that the is only46%ofdouble-pitch roller conveyor chain system, therefore, the reliability and environmentalfriendliness of chain conveyor is increased by the double-pitch time-sharing meshing silentconveyor chain system.
According to the research production to apply for a patent of invention,“double-pitchtime-sharing meshing silent chain”.patent No.:201110233079.9; notice of authorizationnumber: CN102287483B.
In this paper, the research on chain conveyor is carried out with the fund and supportfrom chain drive system for reducing the noise, which is the subproject of CDX01projectof National General Equipment Department, and the design method of double-pitchtime-sharing meshing silent conveyor chain system is proposed on the basis of furtherresearching the meshing theory of double-pitch time-sharing meshing silent conveyor chain,and design, calculation, emulation analysis and experimental research are carried out inregard to double-pitch time-sharing meshing silent conveyor chain system with15.875mmsingle pitch and45teeth.
引文
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