# 第三章 螺栓连接 # 螺栓连接计算案例和kisssoft校核 一 #### 1 计算输入 一液压油缸，油压 P=1.6Mpa，D=160mm，壁厚 S=10 mm 求设计上盖的螺栓连接数量和分布直径，如图所示。 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/iUoimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/iUoimage.png) #### 2 手工螺栓选型 使用工程力学基本原理计算方法步骤如下： 1.计算螺栓工作的载荷 F1，暂取螺栓数量 z=8，则每个螺栓承受的平均轴向工作载荷为 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/T9pimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/T9pimage.png) 2\. 计算螺栓总的拉伸载荷 F，对于压力容器取残余预紧力 F2=1.8\* F1，则 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/hmVimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/hmVimage.png) 3.求螺栓直径。选取螺栓材料性能等级为 4.8 级，取安全系数 n=3，则螺栓的许用应力为 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/hvpimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/hvpimage.png) 按照强度公式计算螺栓的小径 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/8nkimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/8nkimage.png) 查表 M16 螺栓小径 13.835，因此选用螺栓为 M16 4.设计螺栓分布圆直径 D1。以油缸外径，留出 2 倍螺栓六方长度 e 即可。 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/UoKimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/UoKimage.png) 螺栓间距验证，小于 7 倍螺栓直径。 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/elpimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/elpimage.png) #### 3 Kisssoft 计算校核 ##### 3.1 Kisssoft 螺栓连接的计算逻辑 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/0IRimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/0IRimage.png) ##### 3.2 kisssoft 负载选项卡 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/b6oimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/b6oimage.png) ##### 3.3 Kisssoft 螺栓/螺母型号定义 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/FTCimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/FTCimage.png) ##### 3.4 Kisssoft被夹紧零件参数定义 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/X6Cimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/X6Cimage.png) ##### 3.5 Kisssoft 螺栓装配条件定义 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/MSKimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/MSKimage.png) #### 4 Kisssoft 计算结果和报告 ##### 4.1 Kisssoft 计算报告 - 根据最小所需装配预紧力 FM min的计算结果： [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/k4Wimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/k4Wimage.png) ##### 4.2 Kisssoft 计算报告 - 根据装配过程中产生的最大预紧力FM max的计算结果： [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/diFimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/diFimage.png) ##### 4.3 Kisssoft 计算报告 - 安全系数校核 - 根据装配过程中产生的预紧力FM max 校核 螺栓的屈服 / 疲劳， 和 被连接表面的接触应力 安全系数 - 根据装配过程中产生的预紧力FM min 校核 被连接件的滑动安全系数 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/ZUbimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/ZUbimage.png) ##### 4.4 Kisssoft 完整校核报告 [kisssoft螺栓计算案例1.M40](https://ecar.officesimple.net/attachments/2) [kisssoft螺栓计算案例报告 (一).pdf](https://ecar.officesimple.net/attachments/1) # 螺栓连接计算案例和kisssoft校核 二 #### （1）案例介绍 应用工况是电动汽车减速器内的差速器。 - 差速器是分体式设计，由壳体和差速器盖子通过6个螺栓连接。 - 差速器内半轴齿轮的最大向外涨力共32250N，平均每个螺栓承载5375N。 - 六个螺栓原始设计是M10 8.8级 40mm长度螺栓，后面考虑降低成本，需评估是否可以采用M8 8.8级 30mm长度螺栓。 - 被连接件材料是 球墨铸铁 QT600-3。被连接件盖板厚度5.5mm，行星架光孔区域长10mm，被连接件区域约7mm。 #### （2）初始M10 8.8螺栓校核 ##### 2.1 KISSOFT 参数输入 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/8C1image.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/8C1image.png) [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/1S9image.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/1S9image.png) [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/UtPimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/UtPimage.png) [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/8zdimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/8zdimage.png) ##### 2.2 KISSOFT 计算结果和报告 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/yuAimage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/yuAimage.png) - 这里14709N是软件计算出来的考虑回弹量，夹紧力损失等等因素后，为了满足最后夹紧面达到设定的6450N，在装配时需要提供的最小预紧力。 - 19122N是 14709 \* 1.3 ，1.3是设置的打紧工艺的公差系数。 - 这里 28824N 是软件计算出来的，根据螺栓本身的屈服能力，用到设定的90%，所能提供出来的最大预紧力。此时所需打紧扭矩57Nm。这个57Nm是个upper limit （红线），不能超过。一旦超过，螺栓就存在过打紧，产生塑性的风险。 - 22172 = 28824 / 1.3 得到，也是考虑打紧工艺的公差。 ##### 2.3 KISSOFT 计算源文件和报告 [bolt-differential-M10.M40](https://ecar.officesimple.net/attachments/3) [bolt-differential-M10.pdf](https://ecar.officesimple.net/attachments/4) #### （3）替换为M8 8.8螺栓校核 [![image.png](https://ecar.officesimple.net/uploads/images/gallery/2026-01/scaled-1680-/n5ximage.png)](https://ecar.officesimple.net/uploads/images/gallery/2026-01/n5ximage.png) - 按照1.2倍的安全系数，会发现所需的预紧力，和M8螺栓所能提供的预紧力，基本上刚刚好。也就是说这个M8螺栓用的恰到好处，结论可行。 KISSOFT 计算源文件和报告 - [bolt-differential-M8.M40](https://ecar.officesimple.net/attachments/5) - [bolt-differential-M8.pdf](https://ecar.officesimple.net/attachments/6) 完毕！