本文選題：顆粒阻尼 + 磁流變液�。� 參考：《中北大學(xué)》2017年碩士論文

【摘要】：切削加工領(lǐng)域中,刀具的切削振動(dòng)嚴(yán)重影響著加工工件的表面質(zhì)量,制約著加工效率的提高,尤其是對(duì)于精密孔、深孔的鏜削加工,因其加工需要的鏜刀長(zhǎng)徑比較大,鏜刀的抑振效果必須要好,而普通鏜刀往往滿(mǎn)足不了工件孔加工質(zhì)量的要求。因此,大長(zhǎng)徑比鏜刀的顫振抑制技術(shù)已經(jīng)成為重要的研究課題。本文針對(duì)大長(zhǎng)徑比鏜刀的切削顫振現(xiàn)象,將顆粒阻尼減振技術(shù)和磁流變減振技術(shù)共同運(yùn)用于大長(zhǎng)徑比鏜刀中,設(shè)計(jì)出顆粒阻尼及磁流變復(fù)合減振鏜刀,不僅可以通過(guò)顆粒之間、顆粒與鏜桿腔壁之間的碰撞與摩擦來(lái)消耗振動(dòng)能量,產(chǎn)生減振效果,而且還可以通過(guò)磁流變液的阻尼特性、實(shí)時(shí)調(diào)控性改變復(fù)合減振鏜刀的固有頻率從而避免共振的發(fā)生,達(dá)到抑振的目的。主要研究?jī)?nèi)容與結(jié)論如下:1.闡述了課題背景及研究意義,詳細(xì)介紹了減振鏜刀的發(fā)展,重點(diǎn)介紹了顆粒阻尼減振技術(shù)和磁流變減振技術(shù)的工作機(jī)理以及國(guó)內(nèi)外研究現(xiàn)狀,提出了本文的主要研究?jī)?nèi)容。2.研究了顆粒的物質(zhì)特性,分別根據(jù)離散單元法與接觸力學(xué)原理建立了阻尼顆粒的力學(xué)模型,提供了顆粒阻尼系統(tǒng)總接觸力、總扭矩以及能量耗散的計(jì)算方法。3.建立了顆粒阻尼鏜刀的動(dòng)力學(xué)模型,并在不同的填充顆粒參數(shù)下對(duì)其進(jìn)行了錘擊與鏜削實(shí)驗(yàn),以檢驗(yàn)顆粒阻尼技術(shù)在減振鏜刀中的可行性,測(cè)試鏜刀的性能,結(jié)果表明:填充顆粒直徑越小,密度越大減振效果越好,當(dāng)填充率為70%時(shí),減振效果最佳;選取合理填充顆粒參數(shù)時(shí),鏜刀阻尼比最高達(dá)到4.38%,鏜削后的工件表面粗糙度Ra值最低為1.392μm相比于實(shí)心鏜刀降低了50.13%,顆粒阻尼鏜刀切削性能良好。采用正交試驗(yàn)方法,確定了影響鏜刀切削性能的主要和次要填充顆粒參數(shù),找到了試驗(yàn)因素對(duì)鏜刀切削性能的影響規(guī)律,最終得出了最優(yōu)方案組合。4.闡述了磁流變液的流變機(jī)理,詳細(xì)介紹了磁流變液工作模式的分類(lèi)及原理。根據(jù)四種磁流變液阻尼的動(dòng)力學(xué)模型,建立了一種修正的Bingham模型,該模型既充分體現(xiàn)了磁流變液的阻尼特性,又具備Bingham模型簡(jiǎn)單、實(shí)用性強(qiáng)的優(yōu)點(diǎn)。建立了簡(jiǎn)化的磁流變液流動(dòng)特性模型,據(jù)此計(jì)算出磁流變液的阻尼力。5.介紹了顆粒阻尼及磁流變復(fù)合減振鏜刀的結(jié)構(gòu)組成、裝配方式以及工作原理。鏜桿采用了三段式以對(duì)焊工藝進(jìn)行連接,選定了鏜桿材料,根據(jù)材料力學(xué)原理結(jié)合估算法確定出鏜桿的尺寸;選定了磁流變減振系統(tǒng)的材料,考慮到結(jié)構(gòu)尺寸限制,設(shè)定了磁流變減振系統(tǒng)的長(zhǎng)度和鏜桿軸肩的高度,依據(jù)理論,選取了磁流變減振系統(tǒng)三種主要結(jié)構(gòu)參數(shù)各三組值作為下一步正交試驗(yàn)的因素水平,通過(guò)查詢(xún)手冊(cè)與國(guó)標(biāo)確定出勵(lì)磁線(xiàn)圈的電流密度和型號(hào),并根據(jù)安培環(huán)路定理算出其匝數(shù),構(gòu)造L9(34)正交試驗(yàn)表,以ANSYS二維靜態(tài)磁場(chǎng)分析得到的阻尼通道處的磁感應(yīng)強(qiáng)度為評(píng)價(jià)指標(biāo),通過(guò)極差分析確定出磁流變減振系統(tǒng)的尺寸,最終設(shè)計(jì)出顆粒阻尼及磁流變復(fù)合減振鏜刀。6.利用ANSYS對(duì)復(fù)合減振鏜桿進(jìn)行模態(tài)分析研究其前四階固有頻率與振型,結(jié)果表明:隨著勵(lì)磁線(xiàn)圈電流從0A增大到2A其各階固有頻率都得到提高,一階固有頻率從450.69Hz提高到了505.81Hz,各階振型的相對(duì)位移降低,復(fù)合減振鏜桿具有良好的動(dòng)態(tài)性能可控性以及抑振性能;通過(guò)諧響應(yīng)分析研究復(fù)合減振鏜桿最前端外圓處一節(jié)點(diǎn)的一階固有頻率的響應(yīng),結(jié)果表明:隨著勵(lì)磁線(xiàn)圈電流從0A增大到2A,該節(jié)點(diǎn)處一階固有頻率的響應(yīng)幅值明顯減小,0A時(shí)響應(yīng)幅值為3.436μm,而2A時(shí)僅為0.908μm,進(jìn)一步證實(shí)了復(fù)合減振鏜桿良好的動(dòng)態(tài)性能可控性和抑振性能,顆粒阻尼及磁流變復(fù)合減振鏜刀達(dá)到了設(shè)計(jì)目的。
[Abstract]:In the field of cutting, the cutting vibration of the cutting tool seriously affects the surface quality of the workpiece, and restricts the improvement of the machining efficiency. Especially for the precision hole, the boring machining of the deep hole, the boring tool must be better to suppress the vibration of the boring cutter because of the larger bore length of the boring tool, and the ordinary boring knife can not meet the machining quality of the workpiece. Therefore, the flutter suppression technology of the large length diameter ratio boring cutter has become an important research topic. In this paper, the particle damping technology and magnetorheological damping technology are applied to the large length diameter ratio boring tool to design the particle damping and magnetorheological compound damping boring cutter, which not only can be used in the large diameter ratio boring tool, but also the particle damping and magnetorheological damping boring cutter can be designed. The collision and friction between the particles and the wall of the boring bar are used to consume vibration energy and produce vibration damping effect. Moreover, the natural frequency of the compound damping boring cutter can be changed by the damping characteristic of the magnetorheological fluid, so as to avoid the occurrence of resonance and achieve the purpose of vibration suppression. The main contents and conclusions are as follows: 1. the main contents and conclusions are as follows: The development of the vibration boring cutter is introduced in detail, and the mechanism of the damping and damping technology and the working mechanism of the magnetorheological damping technology are introduced in detail. The main research contents of this paper,.2., are put forward, and the material properties of the particles are studied, and the discrete element method and the contact mechanics principle are established respectively. The mechanical model of the damping particles provides the calculation method of the total contact force, the total torque and the energy dissipation of the particle damping system.3.. The dynamic model of the particle damping boring cutter is set up, and the hammer and boring experiments are carried out under the different filling particle parameters to test the feasibility of the particle damping technology in the damping boring tool and the test boring. The performance of the cutter shows that the smaller the diameter of the filling particle is, the better the damping effect is, the better the damping effect is. When the filling rate is 70%, the damping effect is the best. The damping ratio of the boring cutter is up to 4.38% when selecting the reasonable filling particle parameters. The Ra value of the surface roughness after the boring is 1.392 mu m compared to the solid boring cutter, 50.13% and the particle damping boring. The cutting performance of the cutter is good. Using the orthogonal test method, the main and secondary filling particle parameters that affect the cutting performance of the boring cutter are determined. The influence of the test factors on the cutting performance of the boring cutter is found. Finally, the optimum scheme combination.4. is obtained to explain the rheological mechanism of the magnetorheological fluid, and the classification of the working mode of the magnetorheological fluid is introduced in detail. According to the dynamic model of four kinds of magnetorheological fluid damping, a modified Bingham model is established. The model not only fully embodies the damping characteristic of the magnetorheological fluid, but also has the advantages of simple Bingham model and strong practicability. The simplified model of the flow characteristics of the magnetorheological fluid is established, and the damping force.5. of the magnetorheological fluid is introduced. The structure composition, assembly mode and working principle of the particle damping and magnetorheological damping boring cutter are made. The boring bar adopts three sections to connect the welding process, selects the boring bar material, and determines the size of the boring bar according to the mechanics principle of material, and selects the material of the magnetic flux and vibration damping system, taking into account the limitation of the structure size, The length of the magnetorheological vibration damping system and the height of the shaft shoulder of the boring bar are set. According to the theory, the three values of the three main structural parameters of the magnetorheological vibration damping system are selected as the factor level of the next orthogonal test. The current density and model of the excitation coil are determined by the inquiry manual and the national standard, and the turns are calculated according to the ampere loop theorem. The L9 (34) orthogonal test table is constructed, and the magnetic induction intensity at the damping channel obtained by the ANSYS two-dimensional static magnetic field analysis is the evaluation index, and the size of the magnetorheological damping system is determined by the extreme difference analysis. Finally, the particle damping and the magnetorheological compound damping boring tool.6. are designed to study the modal analysis of the compound damping boring bar with the ANSYS. The first four order natural frequencies and modes of vibration show that the natural frequencies of each order increase with the excitation coil current from 0A to 2A, the first natural frequency is increased from 450.69Hz to 505.81Hz, the relative displacement of each order mode is reduced, and the composite damping boring bar has good dynamic performance controllability and vibration suppression performance; the harmonic response analysis is used. The response of the first order natural frequency of a node at the front end of the composite damping boring bar is studied. The results show that the response amplitude of the first natural frequency of the excitation coil decreases obviously with the excitation coil current increasing from 0A to 2A, and the response amplitude is 3.436 m at 0A, while 2A is only 0.908 mu m, which further confirms the good dynamics of the compound damping boring bar. Performance control and vibration suppression performance, particle damping and magnetorheological composite damping boring cutter achieve the purpose of design.
【學(xué)位授予單位】：中北大學(xué)
【學(xué)位級(jí)別】：碩士
【學(xué)位授予年份】：2017
【分類(lèi)號(hào)】：TG53

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