KISSsoft软件齿轮基础培训非常全面
kisssoft齿轮传动参数设计
4. 进行强度校验：通过KISSsoft进行齿轮传动参数设计时，需要进行强度校验，以确保齿轮传动的可靠性。强度校验包括弯曲强度、接触疲劳寿命、齿面强度等。
5. 进行优化和验证：在完成齿轮传动参数设计和强度校验后，可以进行优化和验证。优化可以提高齿轮传动的性能和可靠性，验证可以检查设计方案是否满足实际应用要求。
总之kisssoft齿轮传动参数设计需要注意细节根据实际应用情况进行调整和优化以确保齿轮传动的性能和可靠性
kisssoft齿轮传动参数设计
kisssoft齿轮传动参数设计
kisssoft齿轮传动参数设计
KISSsoft是一款用于齿轮设计和分析的软件工具，它可以帮助工程师们优化齿轮传动的性能和可靠性。在使用KISSsoft进行齿轮传动参数设计时，需要注意以下几点：
总之，KISSsoft齿轮传动参数设计需要注意细节，根据实际应用情况进行调整和优化，以确保齿轮传动性能和可靠性。
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1. 确定传动类型和传动比：在进行齿轮传动参数设计之前，需要明确传动类型和传动比。传动类型包括平面齿轮、圆柱齿轮、锥齿轮等，传动比则是根据转速和扭矩的要求来确定的。
2. 计算齿轮几何参数：齿轮几何参数包括模数、齿数、齿形等。KISSsoft可以根据传动类型和传动比自动计算这些参数，但需要注意根据实际应用情况进行调整。
kisssoft齿轮传动参数设计
kisssoft齿轮传动参数设计
齿轮传动是工程领域中常见的一种传动方式，常用于轴、传动器和减速器中。
而要进行齿轮传动的设计，KISSsoft是当前比较常用和先进的齿轮传动计算软件之一。
下面介绍KISSsoft齿轮传动参数设计的基本步骤：
第一步，输入传动参数。
首先需要输入齿轮传动的一些基本设计参数，例如齿轮的齿数、模数、齿宽、压力角等。
同时还需要确定齿轮材质、润滑方式、工作温度等参数。
第二步，进行齿轮计算。
在输入完基本参数后，KISSsoft会自动进行齿轮参数的计算，包括模数、模数系数、齿距、齿顶径、齿根径等参数。
第三步，进行齿轮校验。
齿轮校验常常是齿轮传动设计中最重要的一步，它包括齿面接触应力、齿面弯曲应力、寿命和齿轮噪声等方面的校验。
KISSsoft可以快速对齿轮进行校验，计算出齿轮的寿命和工作安全系数等参数。
第四步，进行齿轮优化。
如果齿轮设计不符合要求，需要对其进行优化。
KISSsoft提供了多种优化方法，可以优化齿形、齿距、润滑条件等方面，以提高齿轮的工作性能。
第五步，输出齿轮参数。
当齿轮传动设计完成后，可以将计算结果输出为机加工图和技术参数表格等格式，方便加工和使用。
总之，KISSsoft是一种功能强大、使用方便的齿轮传动计算软件，它可以帮助工程师快速设计和校验齿轮传动，提高齿轮的工作性能和寿命。
齿轮传动设计者在使用KISSsoft进行齿轮传动参数设计的过程中，应严格按照各设计步骤进行，以确保齿轮传动的正常工作。
验证圆柱齿轮的KISSsoft中文基础教程
验证圆柱齿轮的KISSsoft中文基础教程KISSsoft教程系列圆柱齿轮的计算 1. 设计任务本系列教程将介绍如何对已知数据的齿轮通过KISSsoft软件进行详细的分析和计算从而得出一系列的结果。
因此圆柱齿轮完整计算需要规定以下几个方面 1 所需原始的数据输入KISSsoft重新计算 2 按照DIN3990标准规范 3 根据实际要求创建文档的级别标准。
1.1 输入原始数据对于随后进行的数据输入说明请参阅本教程系列的第二章内容 1.1.1 载荷参数性能功率P 3.5 kw 驱主动速度n 2500 1/min 小齿轮 1 应用系数KA 1.35 寿命周期 750 h 1.1.2 几何法面模数mn 1.5 mm 斜齿螺旋角β 25 ? 度法面压力角 20 ? 度齿数 16/43 中心距a 48.9 mm 变位系数x 小齿轮1 0.3215 齿宽b 齿1/齿2 14/14.5 mm 1.1.3分度齿廓齿根高系数hfP 齿根半径系数齿顶高系数haP 齿1 主动轮 1.25 0.3 1.0 齿2 1.25 0.3 1.0 1.1.4附加数据材料 ? 材料硬度弯曲疲劳强度极限齿面接触疲劳极限齿1 主动轮 15 CrNi 6表面硬化 HRC 60 430N/mm2 1500N/mm2 齿2 15 CrNi 6 表面硬化 HRC 60430N/mm2 1500N/mm2 润滑脂润滑微量润滑油 GB00 80?C 基圆正切长度公差范围: 齿1 小齿轮 3 数最大基圆正切长度 Wkmax 最小基圆正切长度 Wkmin 齿11.782mm 11.758mm 齿2 6 25.214mm 25.183mm 质量Q DIN3961 8/8 2主要轮齿修形方法轮齿齿面轮廓修形线性和抛物线形接触方式正常不发生改变或不正确啮合小齿轮轴的性质图1.1 小齿轮轴的应变图 ISO 6336 图片13a I53mmS5.9mm dsh14mm 2. 解决方式 2.1 启动程序通常在注册以及安装之后通常的步骤有开始gt程序gtKISSsoft 04-2010gtKISSsoft才可以启动KISSsoft软件以下为整个操作的截图2.1 2.2 计算方式的选择在树型窗口下有一个活动的Module模块选择双圆柱齿轮副这样一个命令。
kisssys入门实例教程3
KISSsys Tutorial:Gear transmission with planetary differentialStructure of the tutorial The tutorial has two parts to be studied in this order. Introduction explains the most important points in this modeling task and introduces how to start KISSsys. Building a model explains techniques how to build a KISSsys model of a complex gearbox with sevelra power path possibilities. During the study of this tutorial, questions may arise or problems may occur. The KISSsoft customer support can be reached through the address and phone number given above.K I S S s y s t u t o r a i l : T r a n s m i s s i o n w i t h p l a n e t d i f f e r e n t i a l1Table of contents1 Table of contents (2)2 Introduction (4)2.1 Summary of the most important points (4)2.2 Systematicprocedure (4)2.3 Errata and remarks (4)task (4)2.4 ModellingKISSsys (5)2.5 Starting2.6 Selection of the project directory (5)2.7 Opening an empty KISSsys model (6)templates (6)the2.8 Loadingmodel (7)3 Buildingastructure (7)3.1 Treeelements (7)3.1.1 Machine3.1.2 Loads due to overlaid shafts (7)3.1.3 Connections (9)flow (12)3.1.4 Power3.1.5 Adding KISSsoft analysis modules (14)3.2 Input of Gear-, shaft- and bearing data (15)data (15)3.2.1 Gear3.2.2 Shafts and bearings (16)View (19)4 3D4.1 Adding 3D view in the tree structure (19)4.2 Location of the shafts (19)4.2.1 Positioning of the shafts s1a and s1b (19)4.2.2 Positioning of the shaft s2 (19)4.2.3 Positioning of the shaft s6 (20)4.2.4 Positioning of the shaft s3 (20)4.2.5 Positioning of the shaft s4 (20)4.2.6 Positioning of the shaft s5 (21)4.2.7 Positioning of the planet spindle (21)4.3 Work with the 3D Viewer (21)4.3.1 Inside diameters of the gear wheels (21)4.3.2 Color and transparency (22)4.3.3 Visualizing bearings in a shaft bore (22)4.4 Insert data from CAD system (23)5 Changing of gears (24)5.1 Background Information about clutch elements (24)5.2 Applied in the current example (24)5.3 Start of the function (26)Interface (27)6 User6.1 Input of the power (27)6.2 Execute buttons for function in the User Interface (28)model (29)the7 Completing7.1 Calculation of the bearing speed in system with overlaid shafts (29)7.2 Input of the speed ratio for front and rear drive (30)7.3 Input of efficiency (31)7.4 Settings to calculation methodology (32)tooth contact of a gear wheel (32)multiple8 Calculationof8.1 Remarks (32)8.2 Calculation on-road and off-road gear selection (32)8.3 Functionality (33)9 Annex A, ...Set Speed“ (35)9.1 Code (line numbers are not part of the code) (35)9.2 Clarification (35)2Introduction2.1Summary of the most important points1)Where two or more shafts overlap, the bearing load from the around shaft must be transferred by a forceelement to the shaft which is under it. (see chapter 3.1.2)2)For this transfer of bearing loads from one coaxial shaft to the other, …call ‘OnCalcTorque’ duringcalculation of torque” has to be activated. (see chapter 7.4)3)Further, the relative speed of the bearings between overlaid shafts must be calculated as the differencein speed between bearing outer ring and bearing inner ring. (section 7.1)4)The speed at the two output shafts (front and rear axle) are placed with one to another in reference.Therefore the speed at one output shaft has to be set as "Constraint=Yes" and an expression is set to compute one speed (those of the front axle) from the other (the rear axle). In addition, an iteration is necessary for the calculation of the relative speed) ( section 3.1.2 and 7.1)5)"Iteration for torques” and “speed with damping" must be set to execute the iteration. (Section 7.4).2.2Systematic procedureThe following steps are involved when building a KISSsys model:1.Planning: Naming, range and goals of the model2.Insert mechanical component in the tree structure (red Icons)3.Connect mechanical component to each other (grey Icons)4.Define sources of power flow5.Add KISSsoft calculation to the mechanical components (blue Icons)6.Add 3D graphic, and position elements in the graphic7.Add tables / User Interfaces8.Program own functions9.Tests, debugging2.3Errata and remarks1)If questions or difficulties arise during the tutorial, KISSsoft Hotline can be used for assistance (e-mailaddress, tel. no. etc. see front of document).2)The planetary differential used for this example in practice would be a double planet planetary wherethe sun and the planet carrier have the same sense of rotation. However, to prevent the example becoming too complex, a simple planetary train is used. Therefore both outputs rotate contrary to each other.3)The original idea for this tutorial had planned a differential lock between the annulus and the planetcarrier. This clutch is called c3. In reality it will be not used although in the tutorial it is described. It is recommended to proceed exactly according to the tutorial instructions (i.e. the clutch c3 is to be modeled although this is not used).4)An error occurs with the nomination of the forces on s2 due the overlap of shaft s6.2.4Modelling taskA transfer gearbox for a 4x4 off-highway vehicle is to be modeled. The transmission possesses an on- and off -road gear as well as a lockable epicyclic differential acting as a longitudinal differential. A part of the power is continually taken off over a PTO. The bevel gear differentials in the axles are not modeled. The unlocked gears z1 and z2 on the input shaft clutches can be switched on or off.Figure2.4-1 Sketch of the gear train to be modeledFollowing names and characters are useds = shaft; z = gear; c = clutch/couplings; b = bearing (b1: left side bearing, b2: right side bearing) red arrow is power input respective power outputred arc is power transmitted through virtual coupling c32.5Starting KISSsysFirst, a project folder has to be created. Then, KISSsys 03/2008 is to be started and the intended folder is chosen as project folder.Using “Options”, activate the administrator mode. Then, the templates should be opened using “File/Open templates…”.Make sure the latest Patch version is installed on your computer. (Download from www.KISSsoft.ch)2.6Selection of the project directoryKISSsys works with so called ‘projects’ to manage the files. These are listed directory names, in which the KISSsys model and pertinent KISSsoft files are stored. Before a model can be opened in KISSsys, a directory must be defined in which the KISSsys model is to be stored. Therefore a new appropriate directory name has to be created in the main directory KISSsys before starting to model.Through the button in the red marked circle the new directory can be selected. Please notice, the appropriate directory shows up only if you have created the directory as described in the sentence above. In our case: C:\Programme\KISSsoft 03-2008\KISSsys\tutorial-003. After the selection of the directory in the Windowsdialogue with "opening" is to be confirmed, press “open” and KISSsys is launched.Figure2.6-1 Selection of the project directory2.7Opening an empty KISSsys modelKISSsys starts now with an empty model. As a first step, the "administrator" mode must be activated under themain menu "Options".Figure2.7-1 Activate the administrator mode under “Estras” in the main menuIf the option "administrator" can not be selected, then the KISSsys license is missing. In this case contactKISSsoft AG.2.8Loading the templatesAs a first step when creating a new KISSsys model, the templates are to be imported through the menu “File”,“Open templates…”, “templates.ks”. In the templates, all elements are now listed which can be used inKISSsys:Figure2.8-1 Element library … Templates“.After having imported the templates, the model can now start to be built.3Building a model3.1Tree structureIn a first step all existing mechanical components must be defined in a tree structure. It is highly recommended to name gears, shafts, bearings and couplings in such a way as shown in the illustration down. User can define first shaft (e.g. “s1” with bearings “b1 and “b2”) and then copy it to avoid adding all bearings one by one.3.1.1Machine elementsFigure3.1-1 Shafts, Shafts with bearings, shafts with bearings /couplings, elements for modeling epicyclic gear trains The same names can be used several times for different mechanical components, as long as the mechanical components are in a different path of the tree. Please note all bearings are called "b". The left hand bearing is "b1"; the right hand bearing is "b2".The following is important when modeling an epicyclic gear train:1)The planet is supported only by one bearing. I.e. on the shaft …sp“ there is only one bearing…b1“(…kSysRollerBearing“ from the templates) placed.2)The planet carrier needs a special coupling: ”kSysPlanetCarrierCoupling“. Do not mix up this elementwith …kSysCoupling“. This special coupling should be named as …cc“ and will be positioned on the shaft s5. This element is necessary to rotate the planet in the world coordinate system.After these two elements are added, the tree structure looks like in illustration 3.1-1 (above right).All spur gears must be arranged on the respective shafts, the tree structure looks as follows in Figure3.1-53.1.2Loads due to overlaid shaftsForce elements on the shafts “s1” and “s2” have to be added. These force elements are to lead the bearing loads of “s1a” and “s1b” as well as “s6“ in each case on those under it lying shaft (s1 and s2). From the templates the element "kSysCentricalLoad" is used. Four forces are used in total on “s1”, on “s2” two forces are applied. The names of these forces should identify the origin of the force.The names of the forces expose themselves together:For example …f_s1ab1“:…f“ for force…s1a“ marks the shaft that the force is taken over…b1“ marks the bearing that the load is taken overFigure 3.1-2 Forces due to the overlaid shafts on s1 and s2The force components of the inserted forces must be connected with the components of the bearing loads. To do this the right mouse button must be clicked on a force (e.g. f_s1ab1), whereupon the "characteristics" (Properties) appear and must be selected, and after selecting “Fx” under “expression” the following text has to be inserting: GB.s1.s1a.b1.Fx.The expression makes sure the load on the shaftaffecting the load on the other shaft (respectivelytheir x-component) equals the x-component of thebearing load b1 on s1a.The appropriate expressions must be registered alsofor Fy, Fz, Tx and TzFor Fy: GB.s1.s1a.b1.FyFor Fz: GB.s1.s1a.b1.FzFor Tx: GB.s1.s1a.b1.MxFor Tz: GB.s1.s1a.b1.MzThese linkages of the forces must be done for allforces provided:f_s1ab1, f_s1ab2, f_s1bb1, f_s1bb2, f_s6b1, f_s6b2.Figure 3.1-3 Linking force componentAdd as well automatic positioning for the forces on the shaft according to the positions of the bearings. For thisuse functions l_p() to set positions.The expression makes sure the load position on the shaft isequal to the position of the mating bearing (respectively theiry-component).This function looks for reference element and point on parentelement and converts coordinates. Finally only y-direction istaken (*{01,0})l_p(GB.s1.s1a.b1,{0,0,0})*{0,1,0}The appropriate expressions must be registered also for allother forces.Figure 3.1-4 Linking force positionsFinally add gear components to the model.Figure3.1-5 Tree structure and KISSsys sketch with mechanical components3.1.3ConnectionsIn the next step the following connections are defined:1)Connections of the shift clutches for the road gear (c1, c1): It uses "kSysCouplingConstraint" from thetemplates.Action:First copy from the templates "kSysCouplingConstraint" and paste it to the tree structure within the group "GB". The name will be specified with "C1", thus it is clear which clutches are connected (namely c1 on s1 with c1 on s1a). In a second step the clutches which can be connected are to be selected. In addition it must be defined whether the clutch is closed (activated) or open (not activated).Figure3.1-6 Definition of a clutch connection, here for road course2)Connect the shift clutches for the off road gear (c2, c2). This clutch will be open.(…Activated=No“)because both gears can not be closed at the same time:Figure3.1-7 Definition of the clutch for off road course3)Connect both clutches c3, differential lock. The clutch will be open (…Activated=No“):Figure3.1-8 Connection between clutches c3After all clutches are connected within the transmission, the individual gears must be connecting together. For the spur gears, the type "kSysGearPairConstraint" is necessary. The planets need the type “kSysPlanetaryGearPairConstraint " two times. One where the sun wheel connects the planet, the other the planet connects the annulus. The connections are copied from the templates into the tree structure, below the group of "GB":Gear pair gp1 Gear pair gp2Gear pair gp3 Gear pair gp4Figure3.1-9 Definition of gear pairs.Gear pair sun zs between Planet zp “sp”Gear pair planet zp between annulus zr “pr”Figure3.1-10 Definition of a planet gear connection in the systemThe tree structure with the connections defined in the KISSsys sketch should look now as follows:Black line connections: active / close connectionsGrey line connections: inactive / open connectionsFigure3.1-11 Tree structure and KISSsys sketch with connections3.1.4 Power flowThe definition of the power flow in the gearbox is through the element …kSysSpeedOrForce“. This element is to be copied from the templates and pasted four times directly into the tree structure (not under …GB“)During the power input "Input" speed and the torque are given. Both values are signed sizes. If the product of the two signs is positive, then the power is positive, i.e. it concerns a positive input power.Figure3.1-12 Definition of Input power …Input“(Motor)The PTO torque is set to 10Nm (acceptance for this example). The direction of rotation is counter clockwise. The number of revolutions is therefore negative. The torque has to be entered positively thereby the power output becomes negative.Figure3.1-13 Definition of the power take off (PTO)Rear-wheel drive RWD (OutR)As a consequence, number of revs and torque follows by the input data and the type of transmission. No values are given.Figure3.1-14 Definition of the RWDFront wheel drive FWD (OutF)The condition for the front wheel drive is defined as follows:Front axle and rear axle turn with the same speed, but contrary. This condition will be still specified in section 7,2.Thus the number of revolutions at this output (the front axle) is the same as from the number of revolutions of the output “OutR", therefore "speed of constrained=yes" must be set.With the right mouse-click on the power output "OutF" and the choice in "Properties" of "speed", an expression for the speed can be defined at this output. Enter in the field "Expression":"-OutR.speed". This guarantees that the speed at the output is equal the speed of the shaft s5, but in opposite direction of rotation.Figure3.1-15 Definition of the FWDNow the kinetic calculations can be started using right mouse-clicks on menu, selection of "Calculate Kinematics". (Section 7.4 must also be considered). After a Refresh, the sketch looks as follows:Figure3.1-16 KISSsys model with power flow after execution of kinematics analysis3.1.5Adding KISSsoft analysis modulesNext step is to introduce the KISSsoft analysis modules. These are copied from the templates. KISSsoft analysis modules for shafts, bearings and gears are needed. The gear pair and planetary gear analysis are arranged directly below the appropriate connection with the same name. The shaft and bearing calculations are inserted within the appropriate shaft computation.The bearing calculation "Bearing2" is copied from the templates. The index "2" means that altogether two antifriction bearings are computed. Note: for the planet “Bearing1" must be used from the templates since the planet is stored on the spindle only through an antifriction bearing. Bearing calculations can be also done directly in shaft module, but in cases when bearings are between two shafts separate calculation modules should be used to set speed for bearing correctly (relative speed between two shafts).Figure3.1-17 Tree structure with computations (left), and templates used (right)3.2Input of Gear-, shaft- and bearing data3.2.1Gear dataThe following teeth data in Figure 3.2 is used in this example. In addition double-click on the computations (blue Icons) in the tree structure. After entering the design data, the input in each case has to be confirmed with"calculation F5". Afterwards, close the KISSsoft window with "exit" (cross in the right upper corner).Figure3.2-1 Input data gear pair gp1 Figure3.2-2 Input data gear pair gp2Figure3.2-3 Input data gear pair gp3 Figure3.2-4 Input data gear pair gp4Figure3.2-5 Input data for epicyclic drive train3.2.2Shafts and bearingsPosition of elements cIn: y = 5 mm c1: y = 70 mm c2: y = 140 mmPosition of bearings: y = 15 mm y = 170 mmPosition of gear z6: y = 190 mmFigure3.2-6 Input data shaft s1Position of gears: z2 y = 50 mm z4 y = 120 mmPosition of bearings: y = 15 mm y = 195 mmFigure3.2-7 Input data shaft s2Position of the clutches: y=28 mm for s1a, s1b and s6Position of the gear 15 mm Position of bearings 5 mm and 25 mmFigure3.2-8 Input data s1a, s1b, s6Coupling: cc y = 5mmcrOut: y = 190 mm c3: y = 70 mmBearings 90 mm and 170 mmFigure3.2-9 Input data s5coupling cfOut: y=10mm, zs: y=190Bearings 30 mm and 150 mmFigure3.2-10 Input data s4Figure3.2-11 Input Planet pin (sp)To calculate shaft with only one support it may be necessary to activate calculation with bearing internal geometry.z5: y =10mm zr: y = 20mmclutch c3: y=65 mm b1: y = 30 mm b2: y = 58 mmFigure3.2-12 Input data s343D View4.1Adding 3D view in the tree structureFrom the templates, the 3D view "kSys3Dview" is inserted into the highest level of the tree structure. Select “show" using right mouse button by touching the insert function. All mechanical components are still in the same position because their position in the working sheet is not defined. Therefore, the next step will be to arrange the positions of the shafts in the coordinate system.Figure4.1-1 3D view of the gear train model4.2Location of the shafts4.2.1Positioning of the shafts s1a and s1bThe shafts “s1a” and “s1b” are positioned in reference to shaft “s1”. The shafts have a radial distance of zero, and axial length of 35mm and 105mm for “s1a” and “s1b” respectively on shaft “s1”.Figure4.2-1 Positioning of the shafts s1a and s1b to s14.2.2Positioning of the shaft s2The shaft s2 is positioned relative to shaft s1. Both shafts s1 and s2 end at the same horizontal X-position. The distance between the two shafts is equal to the centre distance (a) of the gear pair gp1. (or gp2; or gp4)Figure4.2-2 Positioning of the shaft s24.2.3Positioning of the shaft s6The shaft s6 is positioned relative to shaft 2 (s2). The radial distance is zero. The relative Y-position to the shaft s2 is delta y=180mm.Figure4.2-3 Positioning of the shaft s64.2.4Positioning of the shaft s3This shaft must be placed such that both gears “z5” and “z4” are touching each other through both centre lines of the facewidth. Shaft “s3” has to be placed relative to “s2”. The distance is exactly the centre distance between gear pair “gp3”. The y-position is defined by the position of both gears. The location of the gears on the shaft itself is stored in the variable …position“. Furthermore, the shaft “s3” is located vertically below the shaft “s2”. (phi = -90 deg)Figure4.2-4 Positioning of the shaft s34.2.5Positioning of the shaft s4The shaft “s4” is positioned in reference to shaft “s3”. Both are concentric to each other. The relative Y-position must be chosen in a way that the centre-line of both the gear “zr” on the shaft “s3” and gear “zs” on the shaft “s4” have the same absolute Y-value.Figure4.2-5 Positioning of the shaft s44.2.6Positioning of the shaft s5The shaft “s5” is positioned in reference to the shaft “s3”. They have the same centre line. The relative y position must be selected in such a way that “zp” gear (planet) and “zr” gear (annulus) are on the same absolute y position. The right shaft end of the planet spindle is in the same position as the left shaft end of “s5”. The distance from the centre of the planet to the end of planet spindle is 5mm.Figure4.2-6 Positioning of the shaft s54.2.7Positioning of the planet spindleThe planet spindle is positioned in reference to the shaft “s3”. The planet and the annulus have the same Y-position. The centre distance is given through the KISSsoft gear calculation of the gear stage.Figure4.2-7 Positioning of the planet spindlePress “Refresh” button on menu to see all components places correctly in the space.4.3Work with the 3D Viewer4.3.1Inside diameters of the gear wheelsThe inside diameters of the gear wheels should be set equal to the outside diameter of the respective shaft. For all gear wheels, except the internal gear, the variable “di” should have the following text inserted in the field “expression”:Figure4.3-1 Expression for (i)This supplies the outside diameter of the shaft at the place where the gear part is located.For the internal gear zr, the value for "di" must be inserted manually (in the field "value") equal to the inside diameter of the shaft, but negative:Figure4.3-2 Insert of …di“ by the internal gear zr4.3.2Color and transparencyA variable “kSys_3DColor” and “kSys_3Dtransparency” can be affixed to the mechanical components (gear wheels "z", bearings ”b”, shafts "s" and clutches "c"). This will change the colour and transparency of the selected element. Numerical values 0-255 change the colors, while for transparency between select obscure (0) to transparent (1). User can also use setting functionality from the menu to set colors and appearance for the components.Figure 4.3-3 3D graphic settings4.3.3Visualizing bearings in a shaft boreThe following trick must be used to set correct visualization for the bearings defined according to internal geometry. For both bearings on the shafts “s1a”, “s1b” and “s6” from the variable "d" under “Properties” expression must be deleted for each case.The expression from “d”need to be deletedFigure4.3-4 Necessary …Trick“ for visualizing bearings in a shaft boreAfter a refresh command, the 3D view looks like the following:Bearing: green.Shaft with the non-locater bearing: grey, obscure.Underlying shaft: grey, transparentAlso shown: The local coordinate system from thesame shaft.Figure4.3-5 Correct view of the bearing4.4Insert data from CAD systemDepending upon version of KISSsys *.sat, *.iges or *.step data from any CAD system can be imported. In addition, "kSysCasing" has to be copied from the templates into the tree structure. In this example, four individual CAD data records are read in, and four KISSsys elements of type "kSysCasing" are created. They are called in this example "Wheel1" to "Wheel4": The file attached in this example is called “tut-003-CAD-data.igs”Figure4.4-1 Tree structure with inserted elements for the integration of the CAD data (left), dialogue to “kSysCasing” elements (right)If the dialogue window is open by the right mouse button, then under “Type”” Read file” must be selected. In the field "file name" the complete file name inclusive path is to be indicated if file is not in located in the project folder. Positioning of the Wheels can be done manually entering in the Properties and changing position values.After a refresh the 3D view can look as follows:Figure4.4-2 3D view of the transmission gearbox with imported geometry5 Changing of gears5.1 Background Information about clutch elementsFor the clutch connection the function:setConfig(Activation,Torque constrain)There are the following usual cases:• Clutch is closed, no slip, torque is calculated: setConfig([TRUE, 0], FALSE)• Clutch is closed, slip and torque is given: setConfig([TRUE, slip], [TRUE, moment]) • Clutch is open, no torque: setConfig(FALSE, FALSE)• Clutch is open, torque is given: setConfig(FALSE, [TRUE, moment])For a transmission with two gears, with a given torque at the output in the first gear and given torque at the input by the second gear, a changing gear function can look as follows: (Note! This is only example code)IF gear=1 THEN Coupling1.setConfig([TRUE, 0], FALSE); Coupling2.setConfig(FALSE, FALSE); Input.setConfig(TRUE, FALSE); Output.setConfig(FALSE, TRUE); ELSIF gear=2 THEN Coupling1.setConfig(FALSE, FALSE);Coupling2.setConfig([TRUE,0], FALSE);Input.setConfig(FALSE, FALSE);Output.setConfig(TRUE, TRUE);ENDIFCheck if gear 1 is connected. Set clutches according to the gear selection Set boundary conditions If gear 2 selected do settings according to that 5.2 Applied in the current exampleThe function for changing gears should be contained in a table "Settings". First from the templates the table "user interface" must be copied into the highest level of the tree structure. The table has to be named "Settings". Using the right mouse button, the size of the table can be defined under "dialogue". The table can be visualized by selecting "show". Using the right mouse-click under "Settings" in the tree structure, on selection of "new variable" a further variable with the name "SetSpeed" of the type "function" can be insert.By the right mouse-click on "Settings" and the selection of …Properties", the following window opens. Now the function editor can be called by the right mouse-clicks on "set speed" and the selection by "Edit".Further, a variable "OnOffRoad" of the type "real" is to be added. This will describe the momentarily selected gear. If it is 0, then the on-road gear is active, and if 1 then the off-road gear is engaged.Figure5.2-1 Properties (different variables) under …Settings“. NOTE: the new variables OnOffRoad, Set Speed appeared.Figure5.2-2 Function …Set Speed“ (NOTE:more details about this in Annex A)The function "CADH_VarDialog" generates a dialogue in which can be defined whether the on- or off- road gear is selected. The dialogue supplies an array of "res" as result. Zero elements into "res" is 1 (or TRUE) if the dialogue is confirmed using "OK", 0 (or FALSE) if the dialogue is closed with "CANCEL". The first element of the array corresponds to the selection made. If "on-Road" is selected then 0 is returned, otherwise "off Road" is selected and 1 is set.The first “IF” condition examines if the dialogue was closed with "OK". After this the selection is put into the variable “Settings.OnOffRoad”. If "on-Road" was selected, the clutch “C1” is closed, “C2” is open. If "off Road" was selected, the clutch “C2” is closed, and “C1” is open. Next, the kinematics calculation is called to calculate new power flow. The function can still be extended so that the open clutch in the 3D diagram is translucently represented, the closed clutch obscurely:Figure5.2-3 Function …SetSpeed“。
kisssoft教程
kisssoft教程
口碑软件是一款广泛应用于机械传动系统计算与分析的工具，它可以帮助工程师进行齿轮传动的设计和优化。
本教程将介绍如何使用KISSsoft软件进行齿轮设计。
第一步是创建一个新的项目。
在菜单栏中选择“文件”>“新建项目”，然后填写项目名称和文件夹路径。
单击“确定”按钮创建新项目。
接下来，我们需要输入齿轮的基本参数。
在菜单栏中选择“数据”>“齿轮”，然后填写齿轮的齿数、模数、压力角等参数。
点击“确定”按钮保存并关闭。
现在，我们可以开始进行齿轮系统的计算和分析。
在菜单栏中选择“计算”>“齿轮系统计算”，然后选择所需的计算类型，例如齿轮传动效率、载荷分析等。
输入所需的参数并点击“确定”进行计算。
完成计算后，我们可以查看计算结果。
在菜单栏中选择“结果”>“计算结果”，然后选择所需的结果类型，如载荷分布、齿轮精度等。
KISSsoft将显示相应的结果图表和数据。
最后，我们可以对齿轮系统进行优化。
在菜单栏中选择“优化”>“参数优化”，然后选择所需优化的参数和范围。
KISSsoft 将自动进行参数优化，并显示优化后的结果。
通过这些简单的步骤，您可以快速上手使用KISSsoft软件进行齿轮设计和优化。
祝您成功！。
KissSoft教程：圆柱齿轮的精细选型
KISSsoft教程:圆柱齿轮的精细选型操作流程1.任务1.1任务本章将对斜齿轮进行深入的研究。
给出的基本参数为：工作寿命5000小时，传动功率为5KW，转速为400rpm，应用系数为1.25，传动比为1:4（减速的情况下），齿轮材料为18CrNiMo7-6。
本章的任务是通过对斜齿轮副的优化，达到最佳的重合度和噪音比要求。
强度的计算是依据ISO6336 methodB标准来完成的。
1.2开始齿轮副的计算[斜齿轮]首先按照前一章要求对打开KISSsoft软件，并且在模块一栏中打开“cylindrical ge ar pairs”，并进入计算界面。
有两种方式可以打开该圆柱齿轮的界面：1.点击File/open，选择example里面的“Tutorial-009-step1”到“Tutorial-009-step5”之间的内容为本章所讲案例。
每一步都告诉你需要打开哪一个文件，如下图1.1所示。
图1.1 在教程中所涉及到的每一部的文件都可以在example里面找到2. 在软件project 一栏中也可以直接找到相应的文件，如图1.2所示。
图1.2 软件中自带的教程同步案例2.齿轮副的粗略选型2.1 开启粗略选型的功能KISSsoft 考虑到需要输入的数据比较多，将一些基本数据参数（齿轮必须）放到一个对话框中，并且要用户必须对其进行输入。
如图1.3所示如下操作。
图1.3 粗略选型功能打开方式快捷按钮接下来需要你去输入很多基本参数，比如：传动比（使用%形式，这里采用5%），传动的功率和必须的材料。
你也可以输入定义好的螺旋角和中心距。
螺旋角是由在轴上使用的轴承来决定的，同样螺旋角的大小也是由轴承能够承受的轴向力大小来决定的。
螺旋角可以在下面步骤的fine sizing里面得到优化。
而在初始数据一栏中你只需要将输入大概的螺旋角数值就行了，直齿轮直接输入0度。
在“几何”一栏中，你还可以将在右上角的“细节”一栏中对接下来需要输入的基本参数进行一定范围设置，比如小齿轮的齿数，齿形几何大小和中心距等，如图1.4所示。
(中文)KISSsoft软件基础培训 轴承
ε为寿命指数，对于球轴承，ε = 3； 对于滚子轴承，ε = 10/3
当轴承的当量动载荷等于基本额定动载 荷C时，基本额定寿命L10等于1，代入上式 得： 若轴承工作转速为n（单位为r/min），则以小时数表示的基本 额定寿命为：
上式含有C、P、n和L10h共四个参数，当已 知其中的三个，即可建立另一参数的计算关系 或校核关系。
二.轴承分类和特征 2．一端双向固定、一端游动（single or as tandem->Fixed bearing adjusted on both sides 和Non-locating bearing） 当轴较长或工作温度较高时，轴的热膨胀收缩量较大，宜采用 一端双向固定、一端游动的支点结构。 固定端由单个轴承或轴承组承受双向轴向力，而游动端则保证 轴伸缩时能自由游动。作为双向固定支承的轴承，因要承受双向轴 向力，故内外圈在轴向都要固定。
三. 轴承计算方法介绍 常规运转条件 可以假定这种运 转条件为：轴承正确安装、无外物侵 入、充分润滑、按常规加载、工作温 度不过高或过低，以及不以特别高或 特别低的速度运转。 可靠度：一组相同轴承能达到或超 过规定寿命的百分比。
基本额定动载荷：当一套轴承运转 达到一百万转时，轴承所能承受的载荷 寿命为1百万转时. 可靠度为90%， C。向心轴承记为：Cr，推力轴承记为： 寿命为5百万转时. 可靠度只有50%。 Ca。 当量额定动载荷P：系值在一恒定载荷，在该载荷作用下，滚 动轴承具有与实际载荷条件下相同的寿命。
因此我们要认真学习贯彻准则和条例吃透精神把握实质把各项要求刻印在心就更要坚持以党章为根本遵循坚决维护党章权威自觉学习党章遵守党章贯彻党章维护党章坚持用党章党规党纪规范言行内化于心外化于行不断增强贯彻执行党章党规党纪的自觉性和坚定性努力成为党章党规党纪的坚定捍卫者党和人民事业发展的有力推动者做对党忠诚信念坚定的好干部
中文 KISSsoft软件基础培训 轴
五. 轴模块DIN 743标准简介
危险截面安全系数S的校核计算公式为：
拉伸、压缩应力幅值： σzda 弯曲应力幅值： σba
扭转切应力幅值：τta
许用拉伸、压缩的应力幅值： σzdADK 许用弯曲应力幅值： σbADK
许用扭转切应力幅值：τtADK
五. 轴模块DIN 743标准简介
几何尺寸影响系数 K2（d）：在直径或厚度变大时，弯曲交变强度会转化为拉伸/
挤压交变强度，类似地，扭曲交变强度也会降低。
这些这两个参数后面会使用KISSsoft软件做一
个案例帮助大家案例理解。
表面粗糙度影响系数 KF ：考虑表面粗糙度对局部应力的附加影响。
表面硬化的影响系数 Kv ：考虑的是通过各工艺方法改变的表面状态对疲劳强度的 影响（内应力、硬度）。
使用缺口冲击系数βσ（KISSsoft）比较常见， 而在该参数不清楚的情况下，使用应力集中系数ασ 代替，但是请注意：α>β。
六. KISSsoft界面介绍
静强度和疲劳强度 安全系数计算结果
循环特征系数（以平均应力形式）
许用安全系数[S]
六. KISSsoft界面介绍
壳体温度和
材料的不同，收 缩和热膨胀对轴 系统的影响也不 同。
Resulting X-Z表示（X²+Z²）的平方根
2. 尽量避免在轴上开横孔、切口或凹槽;
3.重要结构可增加卸载槽B、过渡肩环、凹切圆角、 增大圆角半径。也可以减小过盈配合处的局部应力。
四. 轴的结构分析
轴的结构 ：轴主要由轴颈、 轴头、 轴身三部分组 成(如图10-5)。 轴上被支承的部分为轴颈，如图中③， ⑦段； 安装轮毂的部分称做轴头，如图中①，④段； 联 接轴颈和轴头的部分称做轴身，如图中②，⑥段。
(中文)KISSsoft软件基础培训 轴承
一. 知名轴承厂商概述
一. 知名轴承厂商概述
一. 知名轴承厂商概述
对于自定义轴承，在数据库中也可以完成，但是仅限 于该种类型范围内的设置。对于KISSsoft中没有涉及到的 特殊轴承，由于几何形状的特殊性（载荷计算差异不是很 大），需要谨慎使用，请于KISSsoft官方联系。
的标准适时更新，不断推出新版 本和新模块。
一. 知名轴承厂商概述
回转支承（轴承）设置案例 Four point slewing bearing
二.轴承分类和特征 向心轴承 Annular bearing
滚动轴 承类型
按载荷方向分
推力轴承
Thrust bearing
annular contact 向心推力轴承 thrust bearing 球轴承 Ball bearing
二.轴承分类和特征
使用KISSsoft软件举例说明：
一、选择轴承类型（type）、厂商 （label）[从数据库资料提取信息] 及轴承根据轴直径内外尺寸的选择 （diameter）。
二.轴承分类和特征
二、设置转速（speed）、轴承数目（Number of bearings）、轴向载荷（axial force）、径向载荷（radial force）、许用寿命（required service life ）。 三、设置支承的配置形式（Angular contact）：一端双向固定、一端游动。在type of bearing一栏中设置对应轴承的定位类型：Fixed bearing on both sides和 nonlocating bearing。
KISSsoft软件基础培训 ------轴承
kisssoft齿轮变位系数_解释说明
kisssoft齿轮变位系数解释说明1. 引言1.1 概述齿轮变位系数是在机械工程领域中广泛应用的一个重要参数。
它描述了齿轮啮合时，啮合点相对于齿轮基准面的位移量。
通过研究齿轮变位系数，我们可以更好地理解齿轮传动系统的性能，并做出有效的设计和优化。
1.2 文章结构本文将围绕着齿轮变位系数展开讨论，分为五个主要部分。
首先是引言部分，介绍文章的背景和目的。
然后是第二部分，讨论齿轮变位系数的定义、背景以及应用领域。
接下来，第三部分将详细介绍计算齿轮变位系数的方法与原理。
紧接着，在第四部分中，我们将分析齿轮变位系数对传动性能的影响，并着重讨论动态性能、噪声与振动以及寿命预测与可靠性评估等方面。
最后，在第五部分中给出结论总结，并提出进一步研究方向和展望。
1.3 目的本文旨在全面解释和说明kisssoft软件中齿轮变位系数的概念、应用和计算方法。
通过深入探讨这一关键参数，我们可以更好地了解齿轮传动系统，并为相关领域的工程师和研究人员提供有价值的参考和指导。
同时，我们也将对齿轮变位系数对传动性能的影响进行分析，以期对齿轮设计与优化提供实用的建议。
2. 齿轮变位系数的定义与背景:2.1 齿轮变位系数的概念:齿轮变位系数是用来描述齿轮传动中两个啮合齿轮相对于理想位置的偏移程度的参数。
在齿轮传动中，由于制造和安装误差、载荷等因素的影响，实际上啮合的两个齿轮可能存在一定程度的相对位置偏移。
这种位置偏移会导致传动性能下降、噪声和振动增加以及寿命缩短。
2.2 齿轮变位系数的应用领域:齿轮变位系数是齿轮设计和分析中一个重要的参数，广泛应用于机械工程领域。
特别是在高速、精密、大功率传动系统中，更加重视减小齿轮变位系数以提高传动效率和可靠性。
2.3 齿轮变位系数的重要性:齿轮变位系数对于确定有效载荷分布、计算接触应力、考虑弹性变形等都具有重要作用。
通过准确计算和控制齿轮变位系数，可以优化设计方案并提高传动系统的性能。
减小齿轮变位系数可以降低齿轮传动中产生的噪声和振动，提高系统的工作平稳性和舒适性。
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三. KISSsoft 03-2011 数据库介绍
如下图，为经典的齿轮材料（金属材料的属性一般差 异性不是很大，而塑料各材料之间则比较大）S—N曲线。
KISSsoft给出的S—N曲线
三. KISSsoft 03-2011 数据库介绍
有了齿轮材料S—N曲线，就可以根据齿轮在载荷谱条 件下的应力—循环次数曲线和S—N曲线计算出齿轮的安全 系数、损伤率和寿命。还可以根据齿轮应力—循环次数曲 线相对的S—N曲线的位置，来直观判断齿轮工作寿命是否 达到设计要求和齿轮材料选取的好坏。
2. 1.
1. 手动输入经验值于表格内，请注意包括修形类型（type of modification） 和数值（value）。 2. KISSsoft自动推荐值，依据标准计算出数值（value）和相关系数。
四、KISSsoft2011版本的3D界面介绍
齿轮修形（Gear modification）
一对齿轮副，由另
一个和它装配的齿轮来 检验，保证运行流畅。
CAD图形导出介绍
五. KISSsoft软件直齿和斜齿轮及行星轮基本模块介绍
五. KISSsoft软件直齿和斜齿轮及行星轮基本模块介绍
Thread model Step 1: Wrap a thread around the base circle. Step 2: Unwind the thread from the base circle. Step 3: Fixed to the thread, a pen paints the involute.
2. KISSsoft软件支持并推荐的一种快捷的3D导出方法介绍。
3. KISSsoft软件关于3D的高级应用：不加载荷的齿形3D接 触斑点操作。
四、KISSsoft2011版本的3D界面介绍 熟练使用的KISSsoft软件当中的Example里面的案例，能够帮助
用户快速了解软件的功能。
加入 鼓形 修形 后的 接触 斑点
三. KISSsoft 03-2011 齿轮模块介绍
齿轮的优化对于齿轮箱整体设计起到非常重要的作用，使 用KISSsoft软件能够以极低的代价、极短的时间取得理想的齿轮 设计结果。
齿轮影响整个传动系统承载能力和体积有以下参数：
1）材料参数：如材料硬度、极限应力； 2）齿轮参数：基本几何参数，如侧隙、顶隙和压力角等； 3）刀具参数：如齿顶高系数、刀尖圆角半径系数； 4）啮合参数：如中心距、滑动比等； 5）制造参数：齿轮精度、表面粗糙度等； 6）使用参数：如输入转速、计算寿命等； 7）结构参数：如齿轮的偏移位置等；
研究接触斑点可以有效的研究齿间载荷的分布情况，产品齿轮和测 量齿轮的接触斑点，可用于评估齿轮螺旋线和齿廓精度。
四、KISSsoft2011版本的3D界面介绍
目前，国内在齿轮修形方面仍处于经验摸索阶段，修 形主要靠经验，缺乏系统的理论支撑。齿轮在进行修形时， 一般采取先根据经验修形，加工出齿面，再进行接触斑点 实验，得到齿轮在不同工况下的齿面接触斑点，然后根据 得到的接触斑点修形设计，重新加工和实验。但这种方法 必须通过多轮实验和设计修改来确定接触斑点，成本大且 时间长。而KISSsoft软件可以很好地模拟这些实验过程， 有效地节省成本并缩短设计周期。
齿向修形（Tooth trace modification）
K形图解释（国标）
四、KISSsoft2011版本的3D界面介绍
齿轮修形（Gear modification）
KISSsoft软件基于用户所选的计算标准，充分考虑轮 齿受载变形及安装误差，给出相应的修形量建议值，也可 以根据自身状况相应修改。
作为传动系统的重要部件，齿轮的振动噪音过大是发生 异响的主要来源，但该问题的发生往往并不是因为齿轮参数设 计的不合理，而是由于齿面接触状况不合导致的。齿轮在系统 绝对刚性且无任何安装制造误差的情况下，齿面接触状况最理 想，传递误差曲线在理想条件下为一条直线。而在实际工作中， 齿轮会因传动系统壳体、轴、轴承及其自身等变形而出现错位， 导致齿轮的接触状况不再理想，使齿轮可能出现严重的偏载和 传递误差过大，最终齿轮载荷能力（寿命）下降和传动及其不 平稳，导致最后噪音过大。
四、KISSsoft2011版本的3D界面介绍
齿轮修形（Gear modification）
目前国内在齿轮修形方面处于摸索阶段，主要借助于 经验，修形后进行接触斑点试验，如不满意重新修形试验， 因此需要的成本高周期长。
借助KISSsoft软件进行齿廓和齿向修形可以大大的节省 成本并缩短周期。修形时，定义一组修形参数，并不断调 整，以减小传递误差和优化接触斑点及降低最大齿面接触 及齿根弯曲的强度作为目标，进行修形。而传统人工单一 考虑优化目标进行的修形得到的设计结果不全面也不合理。 因此，多目标综合修形具有十分重要的理论和工程实际应 用价值。
Roll distance 滚动距离 Each circle segment belongs每段圆弧都属于一个渐 开线段 to an involute segment Length of the circle segments = length of the thread = roll distance 圆弧长度= 线的长度 = 滚动距 离
通过修起鼓量、线性和抛物线等不同的组合方式，得 到合理的修形曲线，改善齿面接触状况。同时修形要做到 对接触斑点和传递误差的综合控制，通过不断的调整修形 值和组合方式，得到一组最佳的修形结果，达到减小传递 误差和优化接触斑点的目的。
四、KISSsoft2011版本的3D界面介绍
齿轮修形（Gear modification）
三. KISSsoft 03-2011 数据库介绍
基本材料（material basic data）
拉伸试验
齿轮
轴
轴承
键
根据不同工况，对于零件尺寸、形
状、强度要求都不一样，所以对于右边 各零部件的功能属性要求都完全不一样。
三. KISSsoft 03-2011 数据库介绍
KISSsoft的数据库材料的定义也是按照这种方 法来的。点击 ，选择可以读写的功能。
因此，KISSsoft推荐使用各类零件的S—N曲线，并建 议用户建立自己相应的S—N曲线数据库。如果用户暂时没 有自己的，可以根据经验，找材料性能接近的S—N曲线作 为参考，使用KISSsoft软件，对已有准确结果的产品进行 建模，根据实际的结果来修正原材料S—N曲线，经过多次 修正和比较，最后就可以得到一个相对准确的S—N曲线。 对于重要的传动应用和关键零件，KISSsoft推荐必须使用 各类零Байду номын сангаас自己的S—N曲线。
齿侧面 = 渐开线
Tooth thickness sb. 齿厚 sb
区别 Facewidth b. 齿宽 b
Tip circle and root circle limit the standard tooth.
齿顶圆和齿根圆限定了标准齿的形状。
五. KISSsoft软件直齿和斜齿轮及行星轮基本模块介绍
第一步: 沿基圆绕线 第二步: 将线展开拉直 第三步: 将笔固定于线，可画出渐开线
Developing 展成原理
五. KISSsoft软件直齿和斜齿轮及行星轮基本模块介绍
Standard tooth 标准齿
Standard geometry of gear teeth
轮齿的标准几何外形
Flanks = involutes.
四、KISSsoft2011版本的3D界面介绍
齿轮修形（Gear modification）
齿向修形：在齿宽方向修去一部分，比如为了避免由 于热变形使负荷沿齿宽分布复杂。
可以看出，无论是齿廓修形还是齿向修形，依据现有 的标准只给出一个取值范围，对于具体的生产情况，可能 并不适用，而不恰当的修形反而进一步降低齿轮传动性能， 起到相反的效果。
齿轮轮齿的修形量就是遵循齿轮工作时振动噪声较小、 最大接触应力较小的原则，参照GB/T 3480-1997（ISO 6336或者DIN 3990）渐开线圆柱齿轮承载能力计算方法确 定的。
五. KISSsoft软件直齿和斜齿轮及行星轮基本模块介绍
一、直齿和斜齿轮模块介绍
在齿轮基本数据界面，有 大基础版块，齿轮参数设置必不可少的。
三. KISSsoft 03-2011 数据库介绍
通过添加用户设置的新数据，ID将先从20000开始记 录，一旦添加成功，将不会被删除，但是可以在数据库中 隐藏。而ID为1到19999存储了各种机械标准里的参考表格 及实验数据，相当于非常齐全的电子档机械手册。
举例：使用KISSsoft对齿轮常用材料C60不同热 处理，在数据库自定义的设置操作情况。
三. KISSsoft 03-2011 数据库介绍
我们这次培训使用的是目前最新的KISSsoft的2011版 本，一些老客户可以保留以前的版本，不会相互冲突，但 是我们软件的模块和数据在不断更新和完善，有义务将最 新的功能使用方法交到大家的手上，希望大家能够对软件 有一个更全面的认识。
请大家先打开这次培训的 第一篇章 用户使用界面，其中包 含了三部分内容：
三. KISSsoft 03-2011 数据库介绍
关于传动系统中，最关键的零件就是齿轮， 由于齿轮的形状比标准试棒复杂，对齿轮热处理 方式不同，使用时润滑油的情况也不相同，这些 因素就会使得齿轮材料的疲劳特性与标准试棒的 疲劳特性产生很大的差异。因此，对不同材料和 形状的齿轮，进行专门设计和制造，使用专门的 润滑油，在专门的实验台架上按规定的流程进行 齿轮材料测试，得到材料的S—N曲线和弯曲S—N 曲线，才能真实反映齿轮材料实际的接触和弯曲 疲劳特性。
因此，为了校正齿面接触状况不良和提高齿轮传动平稳性，
必须对齿轮进行修形，优化齿面接触状况，使接触斑点达到最 优。
四、KISSsoft2011版本的3D界面介绍