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大型3d网络游戏人气排行榜2017大型3d网络游戏人气排行榜网络游戏，简称“网游”。
以互联网为传输媒介，以游戏客户端软件为信息交互窗口的旨在实现娱乐、休闲、交流和取得虚拟成就的具有可持续性的个体性多人在线游戏。
2017年最具人气的网络游戏有哪些?下面yjbys店铺为大家分享网游排行榜，欢迎阅读!NO.1 传说之下这是一款角色扮演类剧情游戏，在游戏中玩家将控制一个掉入一个地下怪物世界的人类找到出去的路，亦或是选择留下。
这款游戏在Steam 上的好评率非常的高，达到了9 6%，同时也是去年排名第二的人气游戏。
今年《传说之下》的登顶，也说明好的独立游戏是一定会有广大的玩家基础的。
NO.2 守望先锋屁股先锋就不用多说了吧，从最开始暴雪放出资料片，到申请内测，再到正式公测，感觉今年屁股先锋已经从春天红到了秋天。
虽然198的买断制让一些玩家望而却步，但是也无法阻挡它来势汹汹的步伐。
能把FPS做的如此有趣耐玩，也就非暴雪莫属了吧。
NO.3 精灵宝可梦GO作为今年夏天的绝对网红，《pokemon go》的出现可谓是激起了全世界人民的G 点。
只要一个地方开服，就会引起一阵捕捉小精灵的热(sao)情(luan)。
可惜的是，从8月到12月连备案信息都有了，《pokemon go》的国服还是迟迟没有消息，而比卡丘也无情的沦为了过气网红。
NO.4 神秘的信使这是一款名不见经传的韩国女性向手游，至于为何会排在这么靠前的位置，大概是今年没有出什么爆款韩剧，所以姑娘们都玩手游去了?作为一款剧情丰富的恋爱题材手机游戏，妹子们可以解决那个“面对自己喜欢的对象却又无从直接告白”的困境，而且对象都是花美男哦，养眼的不行!NO.5 精灵宝可梦太阳/月亮作为口袋妖怪粉们期盼已久的最新力作，《精灵宝可梦太阳/月亮》最大的惊喜莫过于，任天堂爸爸终于推出了大家心心念念的中文版。
据最新消息称，宝可梦公司旗下游戏《精灵宝可梦：太阳/月亮(Pokémon Sun/Moon)》在欧洲地区发售12天之后销量就突破了210万，不得不说世界各地的玩家对于驯化小精灵对战还是有种秘制喜爱。
文章题目：探索虚拟计算机在3DMax毕业设计题目中的应用1.引言在当今数字化时代，虚拟计算机技术已经渗透到各个领域，从工程设计到娱乐产业，都有着广泛的应用。
其中，3DMax作为一款优秀的三维建模和动画设计软件，也受益于虚拟计算机技术的发展。
在毕业设计中，学生可以借助虚拟计算机技术，实现更加想象力丰富和现实感强的作品创作。
2.虚拟计算机技术在3DMax中的应用2.1 三维建模虚拟计算机技术为3DMax提供了更加强大的三维建模功能。
通过虚拟计算机技术，设计师可以在3DMax中创造出更加真实的场景和模型，使得毕业设计作品更加生动和引人入胜。
2.2 渲染技术虚拟计算机技术的发展也为3DMax的渲染技术带来了更多的可能。
使用虚拟计算机技术，可以实现更加逼真的光影效果和材质质感，使得毕业设计作品在视觉上更加震撼和吸引人。
2.3 动画设计虚拟计算机技术还为3DMax的动画设计提供了更多的创作可能。
通过虚拟计算机技术，学生可以创造出更加流畅、细腻的动画效果，为毕业设计作品增添更多的艺术感和表现力。
3.个人观点和理解虚拟计算机技术的不断发展，为3DMax在毕业设计中的应用带来了更多的机遇和挑战。
作为文章写手，我个人认为学生在毕业设计中应该积极借助虚拟计算机技术，不断探索和实践，创作出更加具有创新性和艺术性的作品。
我也鼓励学生在虚拟计算机技术的基础上，加强对美术、设计等方面的综合素养，努力提升自己的创作水平和专业能力。
4.总结与回顾通过本文的探讨，我们了解到虚拟计算机技术对3DMax毕业设计题目的重要性和影响。
在未来的发展中，虚拟计算机技术将继续为毕业设计带来更多的创作空间和想象力。
希望学生们能够善于利用虚拟计算机技术，不断挖掘和拓展自己的创意，创作出更具有价值和影响力的作品。
5.结语通过深入地探讨虚拟计算机在3DMax毕业设计中的应用，我们对这一主题有了更加清晰和深刻的理解。
希望本文能够对读者有所启发，为他们在毕业设计中的创作提供一些新的思路和方法。
游戏笔记本电脑排名推荐_十大最佳游戏笔记本推荐当提到PC游戏时，那么首先就需要选择一个合适的电脑主机来获得良好的游戏效果。
那么这时候你就需要一台游戏笔记本电脑。
下面店铺分享了游戏笔记本电脑排名，一起来了解吧。
游戏笔记本电脑排名推荐1.神舟精盾K790S-i76499元神舟精盾K790S-i7D1笔记本采用17.3英寸屏幕、屏幕分辨率为1600×900;采用全尺寸键盘、包括独立的数字小键盘，便于游戏快捷操作;使用安桥扬声器系统、机身快捷键分布合理、拥有两个USB3.0接口。
配置上，该机采用酷睿i7-3630QM四核处理器、2GBDDR5显存的NVIDIAGeforceGTX660M独立显卡、8GBDDR3-1600MHz内存、1TB硬盘;内置802.11B/G/N无线网卡、蓝牙模块、200万像素摄像头以及Windows7HomePremium操作系统。
小编点评：神舟精盾K790S-i7D1笔记本的硬件配置也完全能够胜任电子竞技比赛的需求，而且这是一款高分屏产品，画面细节展示更生动;数字小键盘也方便了游戏比赛中编队、技能、道具等快捷操作。
2.惠普dv6-7208tx(C5G87PA)6299元惠普dv6-7208tx(C5G87PA)笔记本采用了手感细腻、带有塑料条纹硬质金属拉丝顶盖，摸上去能听到“沙沙”的声音，正面看上去非常低调，而一块金属材质的惠普LOGO在A面上则比较显眼，笔记本运行的时候，金属LOGO发出白色的光，而休眠的时候光会自然熄灭。
该机还拥有独立的数字小键盘区，便于游戏中的快捷操作。
小编点评：惠普dv6-7208tx(C5G87PA)笔记本采用酷睿i7-3632QM四核处理器搭配NVIDIAGeForceGT650M独立显卡，基本上可以满足电子竞技比赛的需求;独立的数字小键盘也便于游戏中的编队、道具使用、技能释放等操作。
3.戴尔灵越17RTurbo(INS17TD-4728)8499元凭借可选背光键盘以及高端阳极氧化铝外壳、蜂巢式纹理表面和浑然一体的掌托，戴尔灵越17RTurbo笔记本精美外观和所需的强大功能;该机采用17.3英寸、1920×1080分辨率的全高清防眩光屏、具备独立的数字小键盘区，便于游戏快捷操作。
世嘉MD平台能排前十名的经典游戏都有什么？展开全文早年的大部分玩家熟悉的游戏平台或许就只有街机游戏和FC游戏，当然还有不少人民币玩家在那些年就已经接触到了MD、SFC和GBA 平台的游戏。
后期的很多玩家在电脑模拟器上面才接触到这些游戏平台的，这时候才发现原来当年错过了太多的经典。
不知道玩家们有没有一种感觉，早年的而游戏特别有亲和力，代入感非常强让玩家很容易就入戏。
比起后期的大型3D游戏，早年的游戏显得更有灵魂。
现在的很多热门游戏，即使人气很高像是吃鸡、农药这类游戏，玩家们都是说放下就能放下，并不会对这类游戏产生什么感情，昙花一现慢慢就被玩家遗忘，即使再过几十年估计也不会有情怀。
而早年的主机游戏不同，满满的都是回忆和感情。
因此，很多怀旧的玩家宁愿玩玩早年的MD游戏，找找情怀，也不愿意去尝试近几年最新的游戏。
近期有不少朋友问我，MD有哪些经典游戏值得怀念。
今天，小编就为大家带来MD时代最经典的十部经典之作。
一.《怒之铁拳》如果要在MD平台上面找一款游戏代表横版过关游戏的巅峰，那绝对是《怒之铁拳》系列。
而该系列最经典的则是《怒之铁拳3》，这款游戏可以说是将16位的MD性能发挥到了极致，玩家对这款游戏的评价非常高。
就光是操作感上面来讲，甚至很多街机游戏都望尘莫及。
《怒之铁拳3》不仅仅传承了前两作的优点，动作更多美观流畅、人物身材看上去比例协调、另外增加了蓄力系统、必杀增加到三个、大大强化了特殊技能，另外还增加了两名隐藏人物。
游戏过关之后都有剧情，而且每一关剧情都紧密连接，非常有代入感。
二.《光之继承者》《光之继承者》是MD上面最成功的ACT游戏，也是MD系列游戏最有代表性的这款游戏耐玩性非常高，它的趣味性或许只有玩过的玩家才能感受得到。
战斗场面非常有创意，方法也是丰富多彩的。
可以使用很多的招式和奇特的魔法，还可以召唤精灵。
遗憾的是，当年小编一直没有打通关，有机会的时候得恶补一下三.《魂斗罗铁血兵团》当年很多玩家误以为这款游戏是《魂斗罗3》，其实并不是。
硬件、软件配置3dsmax所要求的系统配置高。
一般家用电脑配上Windows2000或WindowsXP操作系统就可以运行。
当然，之后的Windows操作系统就更好。
1、CPU:至少500MHz。
CPU的主频越高越好，是影响软件运行速度的最重要因素。
2、内存：256MB以上。
最好配备512MB以上。
如果内存不足将使处理大场景变得非常困难。
3、显示卡：要求显卡至少支持分辨率1024*768，推荐使用24位色，3D加速显示卡。
4、显示器：至少支持1280*1024*75HZ(刷新率)、17英寸以上的显示器。
5、光驱：建议配一个24速以上的CD-ROM光驱，可以获取丰富的造型和多彩多姿的图形图像文件。
有条件的话可以添置一些制作三维动画的设备，比如扫描仪、手写板、数码相机、外接阵列硬盘、实时采集录制卡等。
利用这些设备，三维动画制作过程加会更加方便。
编辑本段使用领域1、游戏动画主要客户有EA、Epic、SEGA等，大量使用于游戏的场景、角色建模和游戏动画制作。
3ds max参和了大量的游戏制作，其他的不用多说，大名鼎鼎的《古墓丽影》系列就是3ds max 的杰作。
即使是个人爱好者利用3ds max，也能够轻松地制作一些动画角色。
对于3ds max 的使用范围，只要充分发挥想象力，就可以将其运用在许多设计领域。
2、建筑动画北京申奥宣传片等。
绘制建筑效果图和室内装修是3ds max系列产品最早的使用之一。
先前的版本由于技术不完善，制作完成后，经常需要用位图软件加以处理，而现在的3ds max直接渲染输出的效果就能够达到实际使用水平，更由于动画技术和后期处理技术的提高，这方面最新的使用是制作大型社区的电视动画广告。
3、室内设计在3DMAX等软件中，可以制作出3D模型，可用于室内设计、例如室内设计效果图模型。
4、影视动画《阿凡达》《诸神之战》《2012》等热门电影都引进了先进的3D技术。
前面已经说过3ds max 在这方面的使用。
PC上十款经典的3D次世代游戏伴随着索尼公司的Play Station 3和微软公司的XBox 360的发布，游戏进入了高画质高品质时代，由于两台游戏机都是八核心高速处理器，所以在游戏品质上面相比与传统PC 游戏更是上了一个大台阶。
“次世代”是由日语原字“次世代”进入中国而来。
看字面上意思就是“下一代”游戏。
次世代游戏，原是指对应次世代游戏主机的游戏。
不管说XBOX 360也好，还是PS3也好，一些越来越经典的游戏被搬上了PC平台，这是证明了PC主机硬件的不断改革与进入，游戏不在是单纯的主机独占，多平台才是让更多玩家来畅游游戏的核心要点，就让我们来细数一下那些从PS和XBOX搬上PC平台的十款经典次世代游戏吧鬼泣4如果说你没玩过鬼泣，那你可以说你没有玩过真正的动作冒险游戏了，《鬼泣4》是《鬼泣》系列的第四作，当大家将目光聚焦在但丁如何在次时代上挥舞大剑、摆弄枪械的时候，CAPCOM以“但丁在前作中的实力已经达到了顶峰”为由将其推到次席，而将另一位狂放不羁的少年选为新作品的代言人。
新主角尼禄是一名厌世的教团骑士成员，他不仅具有酷似但丁的银发红衣，就连攻击方式也十分相似，唯一不同之处在于尼禄拥有一招独有的右手特殊攻击“恶魔爆破”。
正是由于右手的不同，尼禄在战斗中战术的应用比起但丁来说变得更为丰富多彩。
在这次的游戏中，不但将支持每秒60张的高画质画面，而且还将追加破关后的隐藏角色让玩家使用，再加上游戏中两名主角但丁与尼禄也都会有独特的操作方式与战斗技巧，玩家必须利用两人的长处来进行战斗，如此一来才能让战斗更有效率地进行。
本作场景风格还是很大程度的继承了之前几作的样式，有着浓郁的欧洲古典风格。
【游戏截图】鬼泣4 (Devil May Cry 4) 中文免安装版评分:7.8类别：动作冒险大小：6.71G 语言：中文查看详细信息>>下载2175 次真三国无双5真三国无双的最大乐趣就是一夫当关万夫莫开的气势，游戏给玩家营造了一个英雄的角色，让玩家体验在万军丛中取上将首级的感觉。
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“。
