大型雙質(zhì)體反共振振動篩的設(shè)計(jì)與動力學(xué)優(yōu)化
發(fā)布時間：2018-08-28 09:00
【摘要】：振動篩作為一種常見的工程機(jī)械,由于其操作簡單,運(yùn)行可靠,工作效率高等優(yōu)點(diǎn),在我國眾多的工業(yè)生產(chǎn)領(lǐng)域得到了廣泛的發(fā)展和應(yīng)用,振動機(jī)械的出現(xiàn)極大的促進(jìn)了工業(yè)生產(chǎn)的發(fā)展,提高了企業(yè)經(jīng)濟(jì)效益。在我國經(jīng)濟(jì)快速發(fā)展的同時,對于能源的需求量也在日益增長,能源消耗量大大增加,帶來的環(huán)境問題也愈加嚴(yán)峻,反過來制約著經(jīng)濟(jì)的發(fā)展。對于一些傳統(tǒng)的振動機(jī)械,由于其高耗能,低效率等特點(diǎn),已經(jīng)不符合我國當(dāng)前節(jié)能低碳的經(jīng)濟(jì)發(fā)展方向。相比之下,反共振振動機(jī)械的優(yōu)點(diǎn)更加突出,其具有壽命長、重量輕、噪聲低、節(jié)能環(huán)保等優(yōu)點(diǎn),符合我國當(dāng)前經(jīng)濟(jì)發(fā)展低碳節(jié)能的要求,因其廣闊的發(fā)展和應(yīng)用前景,反共振振動機(jī)械越來越受到人們的重視。將反共振理論應(yīng)用于一種新型雙質(zhì)體反共振振動篩的設(shè)計(jì),并對其進(jìn)行充分的理論研究和性能仿真,主要進(jìn)行了以下工作:首先,建立雙質(zhì)體反共振系統(tǒng)力學(xué)模型,對振動系統(tǒng)進(jìn)行動力學(xué)響應(yīng)分析,得到上、下質(zhì)體的位移公式。為了便于研究振動系統(tǒng)的振動機(jī)理,引入反共振系統(tǒng)參數(shù):固有頻率比,質(zhì)量比,阻尼比,反共振頻率比等。通過MATLAB軟件對振動系統(tǒng)進(jìn)行仿真,得到各反共振系統(tǒng)參數(shù)對于質(zhì)體位移的影響規(guī)律。分析了“工作點(diǎn)處工作振幅變化最小”和“工作點(diǎn)附近振幅變化最小”兩種情況下的參數(shù)選擇方法,在此基礎(chǔ)上,確定了參數(shù)優(yōu)選方法,為接下來振動篩結(jié)構(gòu)設(shè)計(jì)中的動力學(xué)參數(shù)選擇提供了理論指導(dǎo)和設(shè)計(jì)依據(jù)。其次,僅以懸臂篩網(wǎng)為上質(zhì)體,即在保留懸臂篩篩面結(jié)構(gòu)的基礎(chǔ)上,提出以懸臂篩網(wǎng)作為參振體的新型反共振振動篩,依據(jù)《振動篩設(shè)計(jì)規(guī)范》和《GBT 26506-2011懸臂篩網(wǎng)振動篩》等規(guī)范和標(biāo)準(zhǔn),對振動篩主體結(jié)構(gòu):懸臂篩網(wǎng)、篩箱、橫梁、機(jī)架等進(jìn)行結(jié)構(gòu)設(shè)計(jì),并基于反共振理論對一些運(yùn)動學(xué)參數(shù)和動力學(xué)參數(shù)的選擇進(jìn)行了詳細(xì)計(jì)算,用材料強(qiáng)度準(zhǔn)則對一些重要零部件做了強(qiáng)度校核。并基于反共振理論,依據(jù)前面所提出的參數(shù)選擇方法確定反共振系統(tǒng)參數(shù)。針對篩網(wǎng)和篩箱的彈簧連接問題,設(shè)計(jì)出兩種結(jié)構(gòu),分別以板彈簧和螺旋彈簧進(jìn)行連接�？紤]到板彈簧結(jié)構(gòu)簡單,承載能力強(qiáng),便于安裝;成本低,便于維修更換;同時板彈簧可以起到導(dǎo)向和傳遞激振力的作用,相比螺旋彈簧彈簧,不需要導(dǎo)桿和套筒,使結(jié)構(gòu)得到簡化。經(jīng)對比分析選用板彈簧作為主振彈簧,設(shè)計(jì)出以板彈簧為主振彈簧的懸臂篩網(wǎng)為參振體的新型反共振振動篩。第三,為了研究所設(shè)計(jì)雙質(zhì)體反共振振動篩的彈性動力學(xué)性能,將三維模型適當(dāng)簡化后導(dǎo)入ANSYS Workbench進(jìn)行有限元分析,包括靜強(qiáng)度分析,模態(tài)分析,諧響應(yīng)分析。靜力學(xué)分析得到振動篩結(jié)構(gòu)的靜應(yīng)力和靜變形,并依據(jù)材料許用靜強(qiáng)度準(zhǔn)則,判定振動篩結(jié)構(gòu)靜強(qiáng)度滿足要求;通過模態(tài)分析得到篩網(wǎng)和篩箱的固有頻率以及各階振型,激振頻率16Hz避開了結(jié)構(gòu)共振點(diǎn),且相鄰兩側(cè)共振峰間隔很大,表明正常工作狀態(tài)下可避免發(fā)生共振。在諧響應(yīng)分析中,對反共振點(diǎn)進(jìn)行了驗(yàn)證,并分析了共振狀態(tài)下篩網(wǎng)和篩箱的力學(xué)性能,依據(jù)材料許用強(qiáng)度準(zhǔn)則,判定振動篩共振狀態(tài)下動強(qiáng)度滿足要求。通過瞬態(tài)動力學(xué)分析,得到了振動篩在簡諧激振力作用下的動應(yīng)力和動變形,,根據(jù)振動機(jī)械動強(qiáng)度準(zhǔn)則,判定振動篩滿足動強(qiáng)度要求。第四,運(yùn)用動力學(xué)軟件ADAMS建立虛擬樣機(jī)模型,并進(jìn)行啟動過程和停機(jī)過程仿真模擬,得到上、下質(zhì)體位移響應(yīng)曲線和隔振彈簧動載荷變化情況。仿真分析驗(yàn)證了所選反共振系統(tǒng)參數(shù)的正確性以及反共振理論在本設(shè)計(jì)中應(yīng)用的可行性。為了進(jìn)一步研究所設(shè)計(jì)振動篩的工作穩(wěn)定性,聯(lián)合使用ANSYS和ADAMS,針對激振力偏離質(zhì)心、物料量波動、主振彈簧剛度不均及兩電機(jī)轉(zhuǎn)速不同步對振動篩篩分性能的影響,進(jìn)行了仿真分析;針對懸臂篩網(wǎng)特有的“二次振動”進(jìn)行柔性體動力學(xué)分析,表明懸臂篩網(wǎng)的“二次振動”改變篩孔程度大小為0.142%,對于所設(shè)計(jì)振動篩篩分性能輕微的促進(jìn)作用,對單個篩棒進(jìn)行模態(tài)分析,發(fā)現(xiàn)激振頻率16Hz遠(yuǎn)小于篩棒第一階固有頻率215.58Hz,故振動篩反共振工作時,實(shí)現(xiàn)篩棒的共振是不現(xiàn)實(shí)的。總之,在對雙質(zhì)體反共振動力學(xué)特性分析的基礎(chǔ)上,設(shè)計(jì)出一種新型雙質(zhì)體反共振振動篩,以懸臂篩網(wǎng)為參振體,最大程度的減少參振質(zhì)量,降低能耗,相比同等規(guī)格的振動篩,參振質(zhì)量減少70%左右,電機(jī)功率預(yù)計(jì)可降低67%左右,穩(wěn)定工作基礎(chǔ)動載荷減少79%左右。通過對振動篩有限元分析,并依據(jù)強(qiáng)度準(zhǔn)則判定其結(jié)構(gòu)強(qiáng)度滿足要求。針對物料分布不均、激振力偏移質(zhì)心、主振彈簧剛度不均和兩電機(jī)轉(zhuǎn)速不同步對振動篩的工作穩(wěn)定性影響情況,進(jìn)行了仿真分析。仿真結(jié)果表明:(1)為了保證篩網(wǎng)的正常工作和篩分效果,安裝激振器時,應(yīng)保證激振力偏心距不得大于0.05m。(2)所設(shè)計(jì)振動篩從空載到滿載的物料增加過程中,其工作振幅和振動強(qiáng)度基本不變,保持良好工作狀態(tài)。篩網(wǎng)物料堆積在篩網(wǎng)一側(cè)時,會增大篩網(wǎng)左右擺動,同時篩箱在Y方向發(fā)生拍振動。物料堆積在入料口處時主要影響激振力偏心距大小,同時影響反共振點(diǎn)位置,增大篩箱振幅。(3)當(dāng)篩網(wǎng)兩側(cè)彈簧剛度不均時,會加劇篩網(wǎng)在Z方向(垂直于篩箱側(cè)板方向)的振動,造成篩網(wǎng)左右擺動,同時會增大篩箱在豎直方向上的啟動階段的共振振幅。(4)當(dāng)兩電機(jī)轉(zhuǎn)速不同步時,會出現(xiàn)轉(zhuǎn)速差,在轉(zhuǎn)速差較小時,振動篩所產(chǎn)生的拍振動振幅接近工作振幅,所產(chǎn)生的拍振動是由于頻率相差較小的簡諧振動相互疊加作用而成,在一定程度上增加了物料的振動強(qiáng)度,有助于物料篩分效果的提高。隨著轉(zhuǎn)速差增大,拍振動周期變短,在轉(zhuǎn)速差在15.6%時,拍振動基本得到消除,但是振動強(qiáng)度減弱一半,則無法滿足原先工作要求。針對懸臂篩網(wǎng)的“二次振動”進(jìn)行了動力學(xué)分析,結(jié)果顯示篩棒的“二次振動”對于篩分效果具有輕微促進(jìn)作用,減少篩孔堵塞。
[Abstract]:As a kind of common construction machinery, vibrating screen has been widely developed and applied in many industrial production fields in our country because of its simple operation, reliable operation and high efficiency. The appearance of vibrating machine has greatly promoted the development of industrial production and improved the economic benefits of enterprises. The demand for energy is increasing day by day, the consumption of energy is increasing greatly, and the environmental problems are becoming more and more serious, which in turn restricts the development of economy. Vibration machinery has many advantages, such as long life, light weight, low noise, energy saving and environmental protection. It meets the requirements of low-carbon energy saving in China's current economic development. Because of its broad development and application prospects, anti-resonance vibration machinery has attracted more and more attention. In order to study the vibration mechanism of the vibration system, the anti-resonance system parameters are introduced. There are frequency ratio, mass ratio, damping ratio, anti-resonance frequency ratio and so on. Vibration system is simulated by MATLAB software, and the influence of anti-resonance system parameters on mass displacement is obtained. On this basis, the optimization method of parameters is determined, which provides theoretical guidance and design basis for the selection of dynamic parameters in the next structural design of vibrating screen. Secondly, a new type of anti-resonance vibrating screen with cantilever screen as the upper mass is proposed on the basis of retaining the structure of cantilever screen. Screen design specification > and < GBT 26506-2011 cantilever screen vibrating screen > and other specifications and standards, the main structure of vibrating screen: cantilever screen mesh, screen box, crossbeam, frame and so on are designed, and based on the anti-resonance theory, some kinematic parameters and dynamic parameters are calculated in detail, and some important parts and components are selected with the material strength criterion. Based on the anti-resonance theory, the parameters of the anti-resonance system are determined according to the parameter selection method proposed above. Two kinds of structures are designed for the spring connection of screen and screen box, which are connected by plate spring and spiral spring respectively. Compared with the coil spring, the guide rod and sleeve are not needed to simplify the structure. By comparison and analysis, the plate spring is selected as the main vibration spring, and a new type of anti-resonance vibration screen with the main vibration spring cantilever screen mesh as the reference body is designed. The elastodynamic performance of the double-body anti-resonance vibrating screen designed by our institute is studied. The three-dimensional model is simplified and then imported into ANSYS Workbench for finite element analysis, including static strength analysis, modal analysis and harmonic response analysis. The static strength of the vibrating screen meets the requirements; the natural frequencies and modes of the screen and the box are obtained by modal analysis, and the excitation frequency is 16Hz to avoid the resonance point of the structure, and the adjacent resonance peaks are separated greatly, which indicates that resonance can be avoided under normal working conditions. According to the allowable strength criterion of materials, the dynamic strength of vibrating screen under resonance is determined to meet the requirements. The dynamic stress and deformation of vibrating screen under the action of harmonic exciting force are obtained by transient dynamic analysis. According to the dynamic strength criterion of vibrating machine, it is determined that the vibrating screen meets the requirements of dynamic strength. Fourthly, the virtual prototype model is established by using the dynamic software ADAMS, and the simulation of start-up and shutdown process is carried out. The displacement response curves of upper and lower mass and the dynamic load changes of vibration isolation spring are obtained. In order to further study the working stability of the vibrating screen, ANSYS and ADAMS are combined to simulate the influence of the exciting force deviating from the center of mass, the fluctuation of material quantity, the uneven stiffness of the main vibrating spring and the asynchronous speed of the two motors on the performance of the vibrating screen. Mechanical analysis shows that the "secondary vibration" of the cantilever screen changes the size of the screen hole to 0.142%. For the slight promotion of the screening performance of the designed vibrating screen, the modal analysis of a single screen rod shows that the excitation frequency of 16Hz is far less than the first natural frequency of the screen rod 215.58Hz. Therefore, the resonance of the screen rod is realized when the vibrating screen is anti-resonant. In short, on the basis of the analysis of the dynamic characteristics of the dual-body anti-resonance, a new type of dual-body anti-resonance vibrating screen is designed. The cantilever screen mesh is used as the vibrating body to minimize the vibration quality and energy consumption. Compared with the vibration screen of the same specifications, the vibration quality is reduced by about 70% and the motor power is expected to be reduced by 67%. The dynamic load of the stabilized working foundation is reduced by about 79%. Through the finite element analysis of the vibrating screen and according to the strength criterion, the structural strength meets the requirements. The simulation results show that: (1) In order to ensure the normal operation and screening effect of the screen, the eccentricity of the exciting force should not be greater than 0.05m when installing the vibrator. (2) The working amplitude and vibration intensity of the designed vibrating screen are basically unchanged during the process of increasing the material from no-load to full-load, and keep good working condition. When the material is piled up at the inlet, the eccentricity of the exciting force is mainly affected, and the position of the anti-resonance point is also affected, and the amplitude of the screen box is increased. (3) When the stiffness of the springs on both sides of the screen is uneven, the vibration of the screen in the Z direction (perpendicular to the side plate of the screen box) will be intensified. When the rotating speed of the two motors is not synchronous, the rotating speed difference will occur. When the rotating speed difference is small, the amplitude of the beat vibration produced by the vibrating screen is close to the working amplitude. The beat vibration is caused by the superposition of the simple harmonic vibration with small frequency difference. With the increase of rotational speed difference, the beat vibration period becomes shorter. When the rotational speed difference is 15.6%, the beat vibration is basically eliminated, but the vibration intensity is reduced by half, which can not meet the original work requirements. Dynamics analysis shows that the "secondary vibration" of the screen rod can slightly promote the screening effect and reduce the blockage of the screen hole.
【學(xué)位授予單位】：濟(jì)南大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2017
【分類號】：TH237.6
本文編號：2208923
[Abstract]:As a kind of common construction machinery, vibrating screen has been widely developed and applied in many industrial production fields in our country because of its simple operation, reliable operation and high efficiency. The appearance of vibrating machine has greatly promoted the development of industrial production and improved the economic benefits of enterprises. The demand for energy is increasing day by day, the consumption of energy is increasing greatly, and the environmental problems are becoming more and more serious, which in turn restricts the development of economy. Vibration machinery has many advantages, such as long life, light weight, low noise, energy saving and environmental protection. It meets the requirements of low-carbon energy saving in China's current economic development. Because of its broad development and application prospects, anti-resonance vibration machinery has attracted more and more attention. In order to study the vibration mechanism of the vibration system, the anti-resonance system parameters are introduced. There are frequency ratio, mass ratio, damping ratio, anti-resonance frequency ratio and so on. Vibration system is simulated by MATLAB software, and the influence of anti-resonance system parameters on mass displacement is obtained. On this basis, the optimization method of parameters is determined, which provides theoretical guidance and design basis for the selection of dynamic parameters in the next structural design of vibrating screen. Secondly, a new type of anti-resonance vibrating screen with cantilever screen as the upper mass is proposed on the basis of retaining the structure of cantilever screen. Screen design specification > and < GBT 26506-2011 cantilever screen vibrating screen > and other specifications and standards, the main structure of vibrating screen: cantilever screen mesh, screen box, crossbeam, frame and so on are designed, and based on the anti-resonance theory, some kinematic parameters and dynamic parameters are calculated in detail, and some important parts and components are selected with the material strength criterion. Based on the anti-resonance theory, the parameters of the anti-resonance system are determined according to the parameter selection method proposed above. Two kinds of structures are designed for the spring connection of screen and screen box, which are connected by plate spring and spiral spring respectively. Compared with the coil spring, the guide rod and sleeve are not needed to simplify the structure. By comparison and analysis, the plate spring is selected as the main vibration spring, and a new type of anti-resonance vibration screen with the main vibration spring cantilever screen mesh as the reference body is designed. The elastodynamic performance of the double-body anti-resonance vibrating screen designed by our institute is studied. The three-dimensional model is simplified and then imported into ANSYS Workbench for finite element analysis, including static strength analysis, modal analysis and harmonic response analysis. The static strength of the vibrating screen meets the requirements; the natural frequencies and modes of the screen and the box are obtained by modal analysis, and the excitation frequency is 16Hz to avoid the resonance point of the structure, and the adjacent resonance peaks are separated greatly, which indicates that resonance can be avoided under normal working conditions. According to the allowable strength criterion of materials, the dynamic strength of vibrating screen under resonance is determined to meet the requirements. The dynamic stress and deformation of vibrating screen under the action of harmonic exciting force are obtained by transient dynamic analysis. According to the dynamic strength criterion of vibrating machine, it is determined that the vibrating screen meets the requirements of dynamic strength. Fourthly, the virtual prototype model is established by using the dynamic software ADAMS, and the simulation of start-up and shutdown process is carried out. The displacement response curves of upper and lower mass and the dynamic load changes of vibration isolation spring are obtained. In order to further study the working stability of the vibrating screen, ANSYS and ADAMS are combined to simulate the influence of the exciting force deviating from the center of mass, the fluctuation of material quantity, the uneven stiffness of the main vibrating spring and the asynchronous speed of the two motors on the performance of the vibrating screen. Mechanical analysis shows that the "secondary vibration" of the cantilever screen changes the size of the screen hole to 0.142%. For the slight promotion of the screening performance of the designed vibrating screen, the modal analysis of a single screen rod shows that the excitation frequency of 16Hz is far less than the first natural frequency of the screen rod 215.58Hz. Therefore, the resonance of the screen rod is realized when the vibrating screen is anti-resonant. In short, on the basis of the analysis of the dynamic characteristics of the dual-body anti-resonance, a new type of dual-body anti-resonance vibrating screen is designed. The cantilever screen mesh is used as the vibrating body to minimize the vibration quality and energy consumption. Compared with the vibration screen of the same specifications, the vibration quality is reduced by about 70% and the motor power is expected to be reduced by 67%. The dynamic load of the stabilized working foundation is reduced by about 79%. Through the finite element analysis of the vibrating screen and according to the strength criterion, the structural strength meets the requirements. The simulation results show that: (1) In order to ensure the normal operation and screening effect of the screen, the eccentricity of the exciting force should not be greater than 0.05m when installing the vibrator. (2) The working amplitude and vibration intensity of the designed vibrating screen are basically unchanged during the process of increasing the material from no-load to full-load, and keep good working condition. When the material is piled up at the inlet, the eccentricity of the exciting force is mainly affected, and the position of the anti-resonance point is also affected, and the amplitude of the screen box is increased. (3) When the stiffness of the springs on both sides of the screen is uneven, the vibration of the screen in the Z direction (perpendicular to the side plate of the screen box) will be intensified. When the rotating speed of the two motors is not synchronous, the rotating speed difference will occur. When the rotating speed difference is small, the amplitude of the beat vibration produced by the vibrating screen is close to the working amplitude. The beat vibration is caused by the superposition of the simple harmonic vibration with small frequency difference. With the increase of rotational speed difference, the beat vibration period becomes shorter. When the rotational speed difference is 15.6%, the beat vibration is basically eliminated, but the vibration intensity is reduced by half, which can not meet the original work requirements. Dynamics analysis shows that the "secondary vibration" of the screen rod can slightly promote the screening effect and reduce the blockage of the screen hole.
【學(xué)位授予單位】：濟(jì)南大學(xué)
【學(xué)位級別】：碩士
【學(xué)位授予年份】：2017
【分類號】：TH237.6
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4 韋繼春;雙質(zhì)體振動理論應(yīng)用的研究及其虛擬樣機(jī)的優(yōu)化設(shè)計(jì)[D];北京化工大學(xué);2004年
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