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Link mechanismLinkages include garage door mechanisms, car wiper mechanisms, gear shift mechanisms.They are a very important part of mechanical engineering which is given very little attention.A link is defined as a rigid body having two or more pairing elements which connect it to other bodies for the purpose of transmitting force or motion . In every machine, at least one link either occupies a fixed position relative to the earth or carries the machine as a whole along with it during motion. This link is the frame of the machine and is called the fixed link.An arrangement based on components connected by rotary or sliding interfaces only is called a linkage. These type of connections, revolute and prismatic, are called lower pairs. Higher pairs are based on point line or curve interfaces. Examples of lower pairs include hinges rotary bearings, slideways , universal couplings. Examples of higher pairs include cams and gears.Kinematic analysis, a particular given mechanism is investigated based on the mechanism geometry plus factors which identify the motion such as input angular velocity, angular acceleration, etc. Kinematic synthesis is the process of designing a mechanism to accomplish a desired task. Here, both choosing the types as well as the dimensions of the new mechanism can be part of kinematic synthesis.Planar, Spatial and Spherical MechanismsA planar mechanism is one in which all particles describe plane curves is space and all of the planes are co-planar.The majority of linkages and mechanisms are designed as planer systems. The main reason for this is that planar systems are more convenient to engineer. Spatial mechanisma are far more complicated to engineer requiring computer synthesis. Planar mechanisms ultilising only lower pairs are called planar linkages. Planar linkages only involve the use of revolute and prismatic pairsA spatial mechanism has no restrictions on the relative movement of the particles. Planar and spherical mechanisms are sub-sets of spatial mechanisms.Spatial mechanisms / linkages are not considered on this pageSpherical mechanisms has one point on each linkage which is stationary and the stationary point of all the links is at the same location. The motions of all of the particles in the mechanism are concentric and can be repesented by their shadow on a spherical surface which is centered on the common location.Spherical mechanisms /linkages are not considered on this pageMobilityAn important factor is considering a linkage is the mobility expressed as the number of degrees of freedom.The mobility of a linkage is the number of input parameters which must be controlled independently in order to bring the device to a set position.It is possible to determine this from the number of links and the number and types of joints which connect the links.A free planar link generally has 3 degrees of freedom (x , y, ). One link is always fixed so before any joints are attached the number of degrees of freedom of a linkage assembly with n links = DOF = 3 (n-1) Connecting two links using a joint which has only on degree of freedom adds two constraints. Connecting two links with a joint which has two degrees of freedom include 1 restraint to the systems. The number of 1 DOF joints = say j 1 and the number of joints with two degrees of freedom = say j 2. The Mobility of a system is therefore expressed as mobility = m = 3 (n-1) - 2 j 1 - j 2Examples linkages showing the mobility are shown below. A system with a mobility of 0 is a structure. A system with a mobility of 1 can be fixed in position my positioning only one link. A system with a mobility of 2 requires two links to be positioned to fix the linkage position.This rule is general in nature and there are exceptions but it can provide a very useful initial guide as the the mobility of an arrangement of links.Grashofs LawWhen designing a linkage where the input linkage is continuously rotated e.g. driven by a motor it is important that the input link can freely rotate through complete revolutions. The arrangement would not work if the linkage locks at any point. For the four bar linkage Grashofs law provides a simple test for this conditionGrashofs law is as follows: For a planar four bar linkage, the sum of the shortest and longest links cannot be greater than the sum of the remaining links if there is to be continuous relative rotation between two members.Referring to the 4 inversions of a four bar linkage shown below .Grashofs law states that one of the links (generally the shortest link) will be able to rotate continuously if the following condition is met. b (shortest link ) + c(longest link) a + dFour Inversions of a typical Four Bar LinkageNote: If the above condition was not met then only rocking motion would be possible for any link.Mechanical Advantage of 4 bar linkageThe mechanical advantage of a linkage is the ratio of the output torque exerted by the driven link to the required input torque at the driver link. It can be proved that the mechanical advantage is directly proportional to Sin( ) the angle between the coupler link(c) and the driven link(d), and is inversely proportional to sin( ) the angle between the driver link (b) and the coupler (c) .These angles are not constant so it is clear that the mechanical advantage is constantly changing.The linkage positions shown below with an angle = 0 o and 180 o has a near infinite mechanical advantage.These positions are referred to as toggle positions. These positions allow the 4 bar linkage to be used a clamping tools.The angle is called the transmission angle. As the value sin(transmission angle) becomes small the mechanical advantage of the linkage approaches zero. In these region the linkage is very liable to lock up with very small amounts of friction.When using four bar linkages to transfer torque it is generally considered prudent to avoid transmission angles below 450 and 500.In the figure above if link (d) is made the driver the system shown is in a locked position.The system has no toggle positions and the linkage is a poor design Freudensteins EquationThis equation provides a simple algebraic method of determining the position of an output lever knowing the four link lengths and the position of the input lever. Consider the 4 -bar linkage chain as shown below. The position vector of the links are related as follows l 1 + l 2 + l 3 + l 4 = 0 Equating horizontal distances l 1 cos 1 + l 2 cos 2 + l 3 cos 3 + l 4 cos 4 = 0 Equating Vertical distances l 1 sin 1 + l 2 sin 2 + l 3 sin 3 + l 4 sin 4 = 0 Assuming 1 = 1800 then sin 1 = 0 and cos 1 = -1 Therefore - l 1 + l 2 cos 2 + l 3 cos 3 + l 4 cos 4 = 0 and . l 2 sin 2 + l 3 sin 3 + l 4 sin 4 = 0 Moving all terms except those containing l 3 to the RHS and Squaring both sides l 32 cos 2 3 = (l 1 - l 2 cos 2 - l 4 cos 4 ) 2l 32 sin 2 3 = ( - l 2 sin 2 - l 4 sin 4) 2Adding the above 2 equations and using the relationshipscos ( 2 - 4 ) = cos 2 cos 4 + sin 2sin 4 ) and sin2 + cos2 = 1the following relationship results.Freudensteins Equation results from this relationship as K 1 cos 2 + K2 cos 4 + K 3 = cos ( 2 - 4 )K1 = l1 / l4 K2 = l 1 / l 2 K3 = ( l 32 - l 12 - l 22 - l 2 4 ) / 2 l 2 l 4 This equation enables the analytic synthesis of a 4 bar linkage. If three position of the output lever are required corresponding to the angular position of the input lever at three positions then this equation can be used to determine the appropriate lever lengths using three simultaneous equations. Velocity Vectors for LinksThe velocity of one point on a link must be perpendicular to the axis of the link, otherwise there would be a change in length of the link.On the link shown below B has a velocity of vAB = .AB perpendicular to A-B. The velocity vector is shown. Considering the four bar arrangement shown below. The velocity vector diagram is built up as follows: As A and D are fixed then the velocity of D relative to A = 0 a and d are located at the same point The velocity of B relative to a is vAB = .AB perpendicular to A-B. This is drawn to scale as shown The velocity of C relative to B is perpedicular to CB and passes through b The velocity of C relative to D is perpedicular to CD and passes through d The velocity of P is obtained from the vector diagram by using the relationship bp/bc = BP/BC The velocity vector diagram is easily drawn as shown. Velocity of sliding Block on Rotating LinkConsider a block B sliding on a link rotating about A. The block is instantaneously located at B on the link.The velocity of B relative to A = .AB perpendicular to the line. The velocity of B relative to B = v. The link block and the associated vector diagram is shown below. Acceleration Vectors for LinksThe acceleration of a point on a link relative to another has two components: 1) the centripetal component due to the angular velocity of the link. 2.Length 2) the tangential component due to the angular acceleration of the link. The diagram below shows how to to construct a vector diagram for the acceleration components on a single link.The centripetal acceleration ab = 2.AB towards the centre of rotation. The tangential component bb = . AB in a direction perpendicular to the link. The diagram below shows how to construct an acceleration vector drawing for a four bar linkage. For A and D are fixed relative to each other and the relative acceleration = 0 ( a,d are together ) The acceleration of B relative to A are drawn as for the above link The centripetal acceleration of C relative to B = v 2CB and is directed towards B ( bc1 ) The tangential acceleration of C relative to B is unknown but its direction is known The centripetal acceleration of C relative to D = v 2CD and is directed towards d( dc2) The tangential acceleration of C relative to D is unknown but its direction is known. The intersection of the lines through c1 and c 2 locates c The location of the acceleration of point p is obtained by proportion bp/bc = BP/BC and the absolute acceleration of P = ap The diagram below shows how to construct and acceleration vector diagram for a sliding block on a rotating link. The link with the sliding block is drawn in two positions.at an angle dThe velocity of the point on the link coincident with B changes from .r =a b 1 to ( + d) (r +dr) = a b 2 The change in velocity b1b2has a radial component r d and a tangential component dr + r d The velocity of B on the sliding block relative to the coincident point on the link changes from v = a b 3 to v + dv = a b 4.The change in velocity = b3b4 which has radial components dv and tangential components v d The total change in velocity in the radial direction = dv- r d Radial acceleration = dv / dt = r d / dt = a - 2 r The total change in velocity in the tangential direction = v d + dr + r Tangential acceleration = v d / dt + dr/dt + r d / dt = v + v + r = r + 2 v The acceleration vector diagram for the block is shown belowNote : The term 2 v representing the tangential acceleration of the block relative to the coincident point on the link is called the coriolis component and results whenever a block slides along a rotating link and whenever a link slides through a swivelling block- 9 -连杆机构连杆存在于车库门装置,汽车擦装置,齿轮移动装置中。它是一给予很少关注的机械工程学的组成部分。联杆是具有两个或更多运动副元件的刚性机构,用它的连接是为了传递力或运动。在每个机器中,在运动期间,联杆或者占据一相对于地面的固定位置或者作为一个整体来承载机床。这些连杆是机器主体被称为固定连杆。基于由循环的或滑动的分界面的元件连接的布局被称作连接。这类旋转的和菱形的连接机构被称作低副。高副基于接触点或弯曲分界面的。低副的例子包括铰链循环的轴承和滑道以及万向接头。高副的例子包括通信区主站和齿轮。动力分析得到,根据机件几何学有利条件研究是一特别的机构,它是识别输入角速度和角加速度等等的运动。运动合成作用是处理机构设计到完成完成要求的任务。这里, 两者的选择类型和新的机制尺寸可能是运动学的综合部份。平面的、空间性的和球面运动机构平面的机构是其中全部的点描述平面曲线是间隔和全部平面是共面的, 大多数连杆和机构被设计成这样,例如刨床体系。主要的理由是这个平面的体系对工程师来说更方便。计算机综合法对工程师来说空间性的装置会有更多的麻烦。平面低副机构被称作二维的连接装置。平面的连接仅仅包括旋转的和一对等截面的使用。空间机构没有对相对运动的点的限制。平面的和球面运动机构是亚垫铁等锻工工具的空间机构。空间机构的连接不是被认为这时候被记录。球面运动机构有一接触点接通各个连杆,它是不动的并且平稳点在所有当中联杆场中工作。在所有机件当中,运动是同心并且由他们的盲区接通球面表现出来,它是集中于普遍的定位。空间机构的连接认为不是这时候被记录。可动性连杆在运动中所表现的自由度数是一个很重要的问题。为了使装置被送到指定位置应控制独立的活动自由度。它可能是由杆的数量和连接方式决定的。一自由连杆通常有3个自由度(x , y, )。由于自由度数的限制在n连杆装置中,通常把一个杆固定。自由度数=3(n-1).连接二连杆的机构有两个自由度约束的增加。有两个约束的二连杆连接,其中一个自由度是来约束这个系统的。有一个约束的连杆机构的自由度是j1,有两个约束的连杆机构的自由度是j2。这个系统的自由度数可表示为 m = 3 (n-1) - 2 j 1 - j 2以下为可动的连杆机构装置的示例0是这个体系中可动的机构。系统中仅仅由一连杆的位置固定可以将可动1安装在固定位置。系统中需要一个可动的2与两个连杆来确定连接位置。这是个一般的规则,但也存在例外,它可以作为一个可动性连杆布局的很有用的参考。格朗定律当设计一连接连杆时,在连续地旋转连杆处,例如由一马达输入时,连线可以自由地旋转完全运行驱动是很重要的。如果连杆锁在任一点则方案不会工作。四杆联动机构和grashof定律对这个情况进行提供了简单的测验。格朗的定律如下:b(短的链环)+c(长的链环)a+d四个典型的四连杆机构注意:如果非之上情况则只有连杆滑块机构可行。四连杆机构的优点四连杆机构按比例增大了施加在主动杆上的输入扭矩。可以证明其正比例系数是Sin( )其中是c、d 两杆之间的角度。反比例于sin( )。其中是b、c两杆之间的角度。这些角度不恒定,因此很明显,机构的优点是规律性的变幻。 如下图显示当角度=0 o或则=180 o时接近于无限增矩机构。这些位置是极限位置, 这些位置使四连杆机构可以用于夹具机构。角被叫做“传输角度”。当传输角度的sin值趋于无限小时,机构的增距接近于0。在这样的情况下连杆容易因为很小的摩擦而产生自锁。一般来说,当使用四连杆机构时,避免采用低于400到500的传输角度。弗洛伊德方程这些方程提供了确定内外连杆位置及连杆长度的简单代数学方法。假设四连杆机构如下所示:四连杆的位置矢量如下:l 1 + l 2 + l 3 + l 4 = 0 水平位移方程:l 1 cos 1 + l 2 cos 2 + l 3 cos 3 + l 4 cos 4 = 0 垂直位移方程:l 1 sin 1 + l 2 sin 2 + l 3 sin 3 + l 4 sin 4 = 0 假设 1 = 1800 then sin 1 = 0 and cos 1 = -1 Therefore 而l 1 + l 2 cos 2 + l 3 cos 3 + l 4 cos 4 = 0 l 2 sin 2 + l 3 sin 3 + l 4 sin 4 = 0方程两边同时消去l 3:l 32 cos 2 3 = (l 1 - l 2 cos 2 - l 4 cos 4 ) 2 l 32 sin 2 3 = ( - l 2 sin 2 - l 4 sin 4) 2由以上两式可得如下关系cos ( 2 - 4 ) = cos 2 cos 4 + sin 2sin 4 ) and sin2 + cos2 = 1结果如下所示弗洛伊德方程得出这样的参数关系结论K 1 cos 2 + K2 cos 4 + K 3 = cos ( 2 - 4 )K1 = l1 / l4 K2 = l 1 / l 2 K3 = ( l 32 - l 12 - l 22 - l 2 4 ) / 2 l 2 l 4 这个方程符合四连杆机构的有限元分析。如果外连杆机构中的三个参量已知,那么可以由公式得出其他连杆的位置与长度参数。连杆的速度矢量杆上一点的速度必须与杆的轴向垂直否则连杆的长度将产生变化。在B下的连杆速度为vAB = .AB,方向垂直于AB杆,速度矢量图如下: 考虑到下面四连杆机构的实例,速度矢量图表示如下:1)A和D相连并固定,相对加速度=0,A和D位于同一点2)B点相对A点加速是vAB = .AB垂直于AB杆。3)C点相对D点速度通过D点垂直于CD杆。4)P店读速度由速度矢量图和比例bp/bc = BP/BC获得。速度矢量简图如下所示:连杆上滑块的速度认为B滑块绕着A在连杆上滑动,滑块瞬间位移到B点。B点的速度为A = .AB并垂直于线的方向。其链接滑块和速度矢量图如下所示: 连杆的加速矢量杆上一点相对另一点的加速矢量由两部分组成:1)向心加速度由其角速度和连杆长度决定为 2.L2)角加速度由连杆角加速度度决定以下图表显示如何到构造一矢量图表下图显示如何构造单连杆机构的加速矢量向心加速度ab = 2.AB方向指向圆心,角加速度为bb = . AB方向垂直于杆。下图显示如何构造四连杆机构的加速矢量画法1). A和D相连并固定,相对加速度=0(a,d同)2). B点相对A点加速在上面的杆上画出3). B点相对C点向心加速度为:B = v 2CB,方向指向B。4). B点相对C点角加速度未知但是方向已知5). C点相对D点向心加速度为:D = v 2CD, 与d( dc2)方向相同。6). C点相对D点角加速度未知但是方向已知7). 通过线c1 和c 2的交叉点找出cP点的速度由比例bp/bc=bp/bc获得,且其绝对加速度为P = ap。下面的图表显示其构造方式和转杆上滑块的加速矢量图。两个滑块之间呈dw角。连杆上点的速度与B点变化一致,变化范围为.r =a b 1 到 ( + d) (r +dr) = a b 2b1b2速度的变化分为沿杆方向的r d 及沿其切线方向的dr + r d。滑块上B点的速度与连杆上相关点的变化有关v = a b 3 to v + dv = a b 4.沿着dv与v d 方向速度的变化= b3b4 。在速度切线方向总变化= dv- r d 加速度 = dv / dt = r d / dt = a - 2 r 速度在正切方向总变化= v d + dr + r 正切加速= v d / dt + dr/dt + r d / dt = v + v + r = r + 2 v 加速矢量图表显示如下:注: 其中2 v代表块的正切加速度。每当链接滑通过一个旋转的块,相对一致点沿着一旋转链环一块滑动。- 7 -一、课题的目的、意义、国内外现状及发展方向1、目的该振动筛的筛分物料为球磨机产品。该产品的大小不是很平均,为了做出更符合要求的物料就需要用振动筛来将球磨机产品进一步细分,将不符合要求的物料从新用球磨机磨小。经过这样的反复处理最终将物料全部做成符合要求的产品1。2、意义矿山机械产品属于小批量、多品种、使用面广的机械设备,按用途可分为采掘设备、提升设备、矿用车辆、破碎粉磨设备、筛分设备、洗选设备及焙烧设备等七大类2 。矿山机械为重机装备,是为基础原材料工业服务的,是我国机械工业中的一个重要分支。长期以来,矿山机械在开发我国矿业资源、促进矿业经济发展、实现矿山生产现代化的进程中起着十分重要、不可替代的支撑作用。而矿业资源的开发、利用主要是通过矿山机械来实现、完成的。因此,矿山机械的先进性与现代化,在一定程度上反映了一个国家的工业化水平。可见,矿山机械对于国民经济的发展有着特别重要的地位和作用3 。筛分设备在矿山机械中占有重要地位,它的发展不仅仅代表着中国矿山机械的发展,它还代表着中国国力的增强,着一个国家的基础工业的实力和工业科技水平4。3、国内外现状目前国内筛机产品种类有圆振动筛、直线振动筛、椭圆振动筛、高频振动筛、弧形筛、等厚筛、概率筛、冷矿筛、热矿筛、节肢筛等,旋振筛和各种振动给料机械,多达50多个系列近1000种规格,产品已在冶金、矿山、煤炭、轻工等许多行业得到广泛的应用,基本上满足了国内国民经济建设的需要5。据2002年行业调查了解,全国筛分机械制造企业已多达300余家,从所有制来看,除国营、集体、股份制外,还有外资和合资企业,特别是股份制、民营企业发展很快。全国筛分机械市场年产值约为5亿元左右,今年又有大的增长,年产值超过1500万元以上的企业有10余家6 。由于我国东部经济发展较快,筛分机械制造企业也主要分布在东北、华北、华东和中南地区,尤其是鞍山新乡地区,这两个地区的筛分机械产值约占全国总产值的50左右,可是在西部地区,还没有一家像样的筛分设备制造企业。我国筛分设备制造企业虽然很多,但是真正具备实力的很少。目前全国具有独立研究开发新产品能力的企业不多,大约有34家,每年能创新开发几个新产品,而大多数企业仍是生产常规较为陈旧的产品。在产品设计和制造水平上,全国大约只有45家企业的机械装备和工艺水平真正具备制造较大筛分机械的能力7。德国申克和K H D公司是国际著名的筛分机械制造企业,他们的新产品开发是和工程设计同时进行的:首先要对被筛物料的物理、化学性质以及在工艺流程中所需达到的要求进行分析,选择合理的技术参数、进行模拟样机试制、进行必要的设计计算、工作图设计、产品试制、检验、服务、工艺试验、跟踪服务、产品改进设计、定型等一系列程序,最后实现交钥匙工程8。4、发展方向(1)深入研究新的筛分理论和技术2002年,中国矿大机械厂为解决大型振动筛强度问题,提出了超静定网梁结构理论并使用成功,获得国家专利。最近,新乡威猛集团将12台2m3m的节肢筛组合在一起,形成了目前国内最大的7.2m振动筛,用于选煤系统的分级和脱水、脱介,效果很好。同样,中国科技大学为铁法矿务局晓青矿研制了筛框不动、筛网振动的大型振动筛9。(2)引入现代化设计手段,采用新材料、新技术、新工艺对现有的筛分机械进行运动分析和结构改进,引入现代化设计手段,采用优化设计,计算机辅助设计,用计算机对筛分结构强度进行计算,提高设计的可靠性;建立振动筛试验台,对筛机产品进行检测。全面推广使用新材料、新技术新工艺。对振动机械用的钢材、轴承、弹簧、筛网进行专门研究,筛面应从金属筛网向非金属筛网发展,应用橡胶筛板、聚氨酯筛网、弹性杆筛面;支承元件应采用橡胶弹簧和复合弹簧;推广环槽铆钉和高强度螺栓联接10。(3)向标准化、系列化、通用化发展提高三化水平,这是便于设计、组织专业生产和保证质量的途径。有些零部件如标准化、通用化了,组织专业化生产,可大大降低成本,提高企业效益。4.5强化筛机技术参数根据不同用途研制新筛机。发展大型、重型、超重型筛分设备,筛机振动筛强度可达5.4以上,筛分面积向27m2以上发展(德国一家筛子技术公司曾生产5mllm、筛分面积达55m的筛机),提高筛机的处理能力和承载能力11。(4)不断扩大筛机应用领域根据不同用途,研制出各种不同型式的筛机,目前,国内对于细和超细物料的分级,含水分7-13粘性物料的分级还存在问题。重机网曾联系国内外需要100目以下,生产能力为15t/h的细筛,国内就没厂家能接,我们应发展特殊用途筛分设备,满足国民经济建设发展的需要,并担当对外出口的任务12。二、课题主要研究内容1、振动筛分的基本原理直线振动筛(直线筛)工作原理:振动筛工作时,两电机同步反向放置使激振器产生反向激振力,迫使筛体带动筛网做纵向运动,使其上的物料受激振力而周期性向前抛出一个射程,从而完成物料筛分作业13。2、振动筛总体方案的比较与确定经过仔细的研究后选择下列性能参数的方案:筛面尺寸1000X2000,筛面层数1,网孔尺寸2-200,产量21t/h,能耗0.74kw,振幅2mm。3、主要零件选择方案的比较与确定主要螺栓、防撞击垫片等均采用国家标准,以减少制作成本。三、主要问题及解决方案1、振动筛降噪措施紧固振动筛上的所有部件,特别是需要经常更换的筛板,避免由于个别部件的松动而产生的额外振动;将冲孔钢筛板更换为弹性模量小、冲击噪声低的聚氨酯筛板或者橡胶筛板;在筛箱的侧板、入料给料口、排料口和接料底盘内加贴橡胶板,这样可以有效地抑制侧板的高频振动,减少辐射噪声;采用柔性辐板齿轮来代替钢齿轮,即在齿轮的辐板上利用橡胶弹性体传递扭矩,吸收齿轮啮入、啮出所造成的振动;用橡胶弹簧替代钢制弹簧,以减少冲击;在激振器的体外加装软式隔声罩;对轴承的内外套之间加以阻尼处理,轴承的滚动体可以制作成空心滚动体或者在空心滚动体的内部加入阻尼材料,这样能够减小轴承的振动和降低轴承的噪声14。2、常见故障及处理措施(1)筛分时筛子不下料或下料不畅一是给煤溜槽与筛面之间有落差太小,应是其落差在400500mm之间。二是新更换或新安装的振动筛实际处理量达不到理论设计时的处理量,即无法满足生产要求,这时应提高筛子角度、加大激振力,如果还无法满足要求,就需要对筛面进行改造:将入料端的筛孔加大。还要注意的一点是给料槽宽度要适中,如果过窄,物料则不能均匀地分布于筛面的宽度方向上,筛子的筛分面积也不能合理有效利用,筛分效果将会受到影响15。(2)筛框断裂根据断裂力学的原理,筛框颤抖容易发生断裂,所以解决该问题的最佳办法就是加厚侧板,或者对激振器附近的侧板局部增加附板以增强整个筛体的刚性,这样筛框就不容易发颤和断裂了16。(3)轴承过热第一种最常见的原因是由于轴承径向游隙太小。由于振动筛上的轴承承载的负荷较大,频率较高,且载荷一直是变动的,所以轴承必须采用大游隙。如果使用的是普通游隙的轴承,就必须将轴承外圈再次磨削,使之成为大游隙。再者就是轴承压盖顶得太紧,也会造成这种现象。压盖与轴承外围之间必须有一定间隙,以保证轴承正常的散热和一定的轴向串动。该间隙可以通过端盖和轴承座之间的密封垫来进行调整17。3、筛分的分级(根据筛分的目的)(1)独立筛分其目的是得到适合于用户要求的最终产品。例如,在黑色冶金工业中,常把含铁较高的富铁矿筛分成不同的粒级,合格的大块铁矿石进入高炉冶炼,粉矿则经团矿或烧结制块入炉18。(2)辅助筛分这种筛分主要用在选矿厂的破碎作业中,对破碎作业起辅助作用。一般又有预先筛分和检查筛分之别。预先筛分是指矿石进入破碎机前进行的筛分,用筛子从矿石中分出对于该破碎机而言已经是合格的部分,如粗碎机前安装的格条筛,筛分其筛下产品。这样就可以减少进入破碎机的矿石量,可提高破碎机的产量。(3)准备筛分其目的是为下一作业做准备。如重选厂在跳汰前要把物料进行筛分分级,把粗、中、细不同的产物进行分级淘汰19。(4)选择筛分如果物料中有用成分在各个粒级的分布差别很大,则可以经筛分分级得到质量不同的粒级,把低质量的粒级筛除,从而相应提高了物料的品位,有时又把这种筛分叫筛选。(5)脱水筛分筛分的目的是脱除物料的水分,一般在洗煤厂比较常见。此外,物料含水含泥较高时,也用筛分进行脱泥20。四、日程安排第4周:查找毕业设计资料及外文翻译资料并综述第5周:外文翻译第6周:完成开题报告第7周:总体方案设计第8周:运动学与动力学参数的选择与计算第910周:装配图设计第11周:完成装配图第1213周:零部件设计与修改第1415周:撰写并完善毕业设计说明书第16周:准备答辩第17周:答辩五、参考文献:1刘树荚,韩清凯,闻邦椿.新型振动破碎机非线性动力学分析J .振动与冲击,2000(3) 2刘树英.动破碎机的发展与应用.振动利用与控制工程的若干理论及应用D. 长春吉林科学技术出版社,20003李以农,刘树英,闻邦椿.惯性振动圆锥破碎机新工艺及动力分析M.矿山机械,2001(2)4 Wenying li,Shibo xiong.Dynamic Anlysis of Large Vibrating ScreenM. Beijing: Mechanical industry publishing house,19895彭运军译.圆锥破碎机J. 选矿机械,1992(2)6张世礼.PZ-450振动圆锥破碎机实验研究J矿山机械,1997(2)7Hua Zhao. Journal of China University of Mining and Techonolgy M. Mining machinery. 1997(2)8镇江农业机械学院.农业机械制造工艺学M.北京:中国农业机械出版社,19819闻邦椿.振动给料机,振动输送机与振动筛的设计M.北京:化学工业出版社,198910闻邦椿、刘树英.振动机械的理论与动态设计方法M.北京:机械工业出版社,200111Teyn,Jacques.Fatigue failure of deck support on a vibrating screenD.the international joumal of pressure vessels and pipingM.volume:61,issue:2-3,1995,315-327 12赵国珍等.钻井振动筛的工作原理与测试技术D.北京:石油工业出版社,198413吴佳常.机械制造工艺学M.北京:中国标准出版社,199214Li Meng. Journal of Coal Science and EngineeringM.et,199815柳连舜、霍光庶.译铝生产机械化D.中国有色金属工业总公司轻金属编辑部199116 张国柱编译.惯性圆锥破碎机结构探讨J.矿山机械,1992(6)17 任德树.粉碎筛分原理与设备M.北京;冶金工业出版社,198418 陈懋圻.机械制造工艺学M.沈阳:辽宁科学技术出版社,198619 李留全.KID型惯性圆锥破碎机用于金刚石矿物处理J.矿山机械,199520Andersen.E.Y. Pedersen,Structural Monitoring of the Great Belt East BridgeA.Proceedings of the Thied symposium on Steai Crossing,Edited by Jon KrokedorgBalkemaM.et,1994,54-62
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