1、Gear reducer based on U G 3 d entity model and movement simulation Abstract: this paper introduces the final version with UG software UG NX MOSLING module gear reducer for the three-dimensional entity model, the main parts including shaft, gear, gear, shaft, the lower housing, on housing and assembl
2、y. Finally in the MOTION module of UG assembly model for the MOTION simulation. Key words: UG; Three dimensional entity modeling; Gear reducer; The simulation Chinese classification number: TH16 literature identifier: A UG is a three-dimensional entity model in the integration of CAD/CAM/CAE technol
3、ogy and is widely used in computer aided design, analysis, manufacturing software. In this article, there are a few problems that should be paid attention to is: the involute gear tooth profile model, when operating hollow-out style cover, gear position between the shaft and gear assembly. 1 drawing
4、 involute tooth profile of the gear On the other hand gear involute tooth profile gear in UG (3) the expression in the drawing, the involute gear teeth with vc + + 6.0 configuration file articles saved coordinate scheme and the corresponding data file tooth profile face value, and define spline draw
5、ing involute tooth profile gear use dot read from the file. Involute polar parameter equation is Will rk and the expansion of the substitution and the expression of trigonometric functions, can be obtained: Here is in the K point of involute tooth profile radius, Angle is involute in AK, is radius o
6、f base circle, is at the K point of pressure Angle. Figure 1, figure 2 With vc + + 6.0 program to change from 0 to 180 K (K +), you can get corresponding Xk and Yk, and save the corresponding data file JKX. Dat, as shown in figure 1. In UG with insert - curve - simulation in the main menu, click the
7、 by button will pop up dialog box, and then the system displays as shown in figure 2 are connected by a spline. Click the take from the file button and select the aforementioned data file JKX. Dat, can get the corresponding involute as shown in figure 3. Figure 3 Due to tooth thickness and reference
8、 circle tooth space width is equal to the gear tooth and tooth space is quite relative central Angle, then the opposite half tooth thickness is central Angle, that is, z represents the number of teeth, should be XC shaft rotation and through the expression of calculate, Angle is due to the reference
9、 standard gear pressure Angle for, should be XC shaft rotation. On the XC shaft drawing a straight line, and then select the line as the centerline of the mirror, cable on line mirror to mirror involute, the tooth profile surface and the radius of addendum Angle is, m as the modulus, is the nominal
10、pressure Angle, is the coefficient of tooth bottom. Finally, you can get the gear as shown in figure 4, the three-dimensional entity model. . Figure 4Similarly, you can get the gear involute gear shaft contour. 2 when the cover is modeling some problems deserve attention Hollow cap to cover the enti
11、re model, completed the receive part of the entity, cant fully perfect entity. In this article, we use hollowing out in the area and the coverage can be divided into two parts: the bearing seat, and raised levels and boarding and can join together is a part of them; The rest is another part, and the
12、 hollow. The key point is to join before hollowing out, and must be after the hollowing out. We believe that the complex system should be broken down into simple, and hollowed out respectively, and then join. 3 the position of the gear shaft and gear assembly Between gears and gear shaft axial posit
13、ion when in the assembly is to determine, so the interference may occur between the teeth. In UG, there are eight types of restrictions, such as: gear, alignment, Angle, parallel, perpendicular, center, distance and tangent, but they are not sure the two gear meshing relationship. Therefore, it is n
14、ecessary when the entity model of gear shaft and gear design drawing the relative position. We paint in the assembly process of the gear shaft centerline with the centerline of the gear space and two lines should be kept parallel to each other, can avoid the interference between the tooth and. We ha
15、ve installed parallel to the edge line of above two lines respectively, with parallel restriction relationship, so, two parallel lines may be more. Therefore, tooth interference will not occur in the process of eating. We have completed the reducer is a major component of three-dimensional entity mo
16、del. Then, lets do it in the motion simulation. First of all, in the case of establishing motion analysis, gear shaft and bearing inner ring as the first connection; Shaft, the gear, had been fixed distance ring and inner ring bearings as the second link. Then, established the joint movement of the
17、unit. That is established between the gear shaft and gear rotary separately. Finally, set the composite gear rotary movement one and two. Select kinematic/dynamic analysis on the picture, and insert the time and steps, we can get the gear reducer movement simulation. 基于 U G的减速器三维实体模型和运动仿真摘要：本文介绍了用UG
18、软件的最终版UG NX的MOSLING模块对减速器进行了三维实体造型，主要零件包括轴、齿轮、齿、轮轴、下箱体、上箱体及相应的装配。最后在UG的MOTION模块中对装配模型进行了运动仿真。关键词：UG；三维实体造型；减速器；仿真中文分类号：TH16 文献标识码：AUG是三维实体模型于一体的CAD / CAM/ CAE技术及广泛应用于全球的计算机辅助设计、分析、制造软件。在这篇文章中有几个问题应注意的是：渐开线齿齿轮轮廓模型、当操作时镂空造型的封面、齿轮轴和齿轮之间的装配时的位置。1 绘制渐开线齿廓齿轮齿另一方面齿轮渐开线齿廓齿可在UG3里的“表达”绘制，这个渐开线齿轮齿牙用VC+ 6.0配置文件
19、的文章保存协调方案和相应的数据文件中齿廓面价值，并用定义样条绘制渐开线齿廓齿轮使用“从文件中读点”。渐开线极坐标参数方程是将和代入和三角函数表达式的扩展，可得到：这里的是在K点处的渐开线齿形半径，是渐开线在AK段得角度，是基圆半径，是在K点处的压力角。 图1 图2用VC+ 6.0程序来改变从0到180改变（K+K），可以得到相应的Xk和Yk，并保存相应的数据文件jkx . dat，如图1所示。在UG的主菜单中有插入曲线仿真，单击“通过点”按钮会弹出对话框，然后系统显示如图2通过点样条。单击“从文件中取点”按钮并且选择前面提到的数据文件jkx . dat，可以得到如图3中相应的渐开线。 图3由于
20、齿厚和参考圆齿空间宽度是相等的，齿轮的齿与齿的空间相对圆心角是相当的，那么相反的半齿厚中心角是，即，z代表齿数，XC轴应旋转并且通过的表达式算出，角是由于参考标准齿轮压力角为，XC轴应该旋转。在XC轴上绘制一条直线，然后选择这条线作为镜像的中线，用“已有线”在“镜像线”来镜像渐开线，在齿廓面和齿顶的半径角是，m为模数，是公称压力角，是齿底系数。最后，可以的得到如图4齿轮的三维实体模型。. 图 4同理，可以得到齿轮渐开线齿轮轴轮廓。2 当覆盖建模是有些问题应该得到重视空心盖在完成了覆盖整个模型，可以得到部分实体，不能得到充分完美的实体。此文中，我们利用“空心化”里的“区域”和将覆盖分为两部分：轴
21、承座，突起的水平和寄宿而且可以联接在一起的是其中的一部份；其余的是另外一部分，和空心分离的。这关键点就是在空洞化之前联接，并且必须在空洞化之后。我们认为，复杂的机构应当分解为简单的机构，并分别挖空，然后再联接。3 齿轮轴和齿轮装配时的位置齿轮和齿轮轴之间的轴向位置当在组装是去确定的，所以干扰可能发生在齿间。在UG中，有八种类型的限制，例如：啮合、对齐、角度、平行、垂直、中心、距离和正切，但他们都不确定两个齿轮的啮合关系。因此，有必要在齿轮轴和齿轮的实体模型设计时绘制相对位置。在装配过程中我们绘制齿轮齿轴中心线与中心线空间齿轮齿和两行应保持相互平行，所以干扰可避免与齿间。我们一直与边缘线以上两行分别平行安装，带平行制约的关系，所以，两直线可能更平行。因此，轮齿在吃过程中不会发生干扰。 我们完成了减速器三维实体模型的主要组成部分。然后，我们来做它的运动仿真。首先，在建立运动分析的情况下，齿轮轴和轴承内圈的作为第一个联接；轴、齿轮、已固定距离的环和相应的内圈轴承作为第二联接。接着，成立了联合运动的单位。即成立了齿轮轴和齿轮之间的分开回转。最后，设置复合齿轮的回转一和二运动。选择运动学/动力学分析图画，并且插入时间和步骤，我们可以得到减速器的运动仿真。
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