So will increase the contact area,

这样会增大接触面积，鉴于影响界面特性的不同因素：螺栓预紧力和接触面的摩擦系数，分析了螺栓连接由于不同的接触特性的影响，并从这些效果更为明显在接触面的摩擦系数，以改善螺栓载荷传递的效果，在螺栓的设计和制造过程中，接触面的摩擦系数应适当增加，这将不断提高负荷传递效率。在相同的外部负载，绕螺栓孔的应力分布是没有受到明显的螺栓预紧力的增加的影响。当螺栓组受到倾覆力矩，螺栓的强度检查被分析为一个例子来进一步说明横向载荷下的普通螺栓的应力。如下图所示的油泵的应力横向安装（图5中为示出）。FN实际上是均匀分布的力从顶部逐渐减小至底部，和FY也是均匀分布的力逐渐减小从顶部到底部<br>如果螺栓的预紧固扭矩为T，摩擦系数为f，油泵重力是G，螺栓直径d。与此同时，具有最大应力螺栓的预载荷残留F也能被计算，并且预加载是通过检查螺栓强度进行分析。该公式如下（安全系数设定为2）。

So will increase the contact area, in view of the different factors influencing the interface properties: bolt pre-tightening force and the contact surface friction coefficient, analyzed the bolt connection due to the impact of different contact properties and, from these effects is more obvious in the friction coefficient of contact surface to improve the effect of bolt load transfer, in the design and manufacture process of bolt, the friction coefficient of contact surface should be appropriately increased, which will constantly improve the load transfer efficiency. Under the same external load, the stress distribution around the bolt hole is not obviously affected by the increase of bolt preload. When the bolt group is subjected to overturning moment, the strength check of the bolt is analyzed as an example to further explain the stress of the ordinary bolt under transverse load. The following figure shows the stress of the oil pump installed laterally (as shown in FIG. 5). Fn is actually the uniformly distributed force that decreases gradually from top to bottom, and Fy is also the uniformly distributed force that decreases gradually from top to bottom<br>If the pre-tightening torque of bolt is T, friction coefficient is f, oil pump gravity is G, bolt diameter d. At the same time, the residual preload F of the bolt with the largest stress can also be calculated, and the preload is analyzed by checking the bolt strength. The formula is as follows (the safety coefficient is set as 2).

所以会增大接触面积，针对影响界面性能的不同因素：螺栓预紧力和接触面摩擦系数，分析了螺栓连接时由于接触性能的不同而产生的影响，从这些影响中比较明显的是在接触面的摩擦系数上提高螺栓的载荷传递效果，在螺栓的设计和制造过程中，应适当提高接触面的摩擦系数，从而不断提高载荷传递效率。在相同的外载荷作用下，螺栓预紧力的增加对螺栓孔周围的应力分布没有明显的影响。以螺栓组承受倾覆力矩时的强度校核为例，进一步说明了普通螺栓在横向荷载作用下的受力情况。下图为横向安装的油泵的受力情况（如图5所示）。Fn实际上是自上而下逐渐减小的均布力，Fy也是自上而下逐渐减小的均布力<br>当螺栓预紧力矩为T，摩擦系数为f，油泵重力为G，螺栓直径为d时，还可以计算出最大应力螺栓的残余预紧力f，并通过校核螺栓强度来分析预紧力。公式如下（安全系数设为2）。