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摘 要
ener-g-force本次设计主要是对轻型货车制动系统结构进行分析的基础上，根据对轻型货车制动系统的要求，设计出合理的符合国家标准和行业标准的制动系统。
首先制动系统设计是根据整车主要参数和相关车型，制定出制动系统的结构方案，其次设计计算确定前、后鼓式制动器、制动主缸的主要尺寸和结构形式等。最后利用计算机辅助设计绘制出了前、后制动器装配图、制动主缸装配图、制动管路布置图。最终对设计出的制动系统的各项指标进行评价分析。另外在设计的同时考虑了其结构简单、工作可靠、成本低等因素。结果表明设计出的制动系统是合理的、符合国家标准的。
关键词：轻型货车；制动；鼓式制动器；制动主缸；液压系统.
Abstract
Braking system is one of the most important system in the automotive . because of the continuous development with the the work of the increasing reliability requirements,Brake work of a reliable car,guarantee the safety of travelling,This shows that, The braking system design of practical significance.
The braking system is one of important system of active safety. Based on the structural analysis and the design requirements of intermediate car’s braking system, a braking system design is performed in this thesis, according to the national and professional standards.
First through analyzing the main parameters of the entire vehicle, the braking system design starts from determination of the structure scheme. SecondlyCalcula
ting and determining the main dimension and structural type of the front、rear drum brake，brake master cylinder ans so on，Finally use of computer-aided design drawing draw the engineering drawings of the front and rear brakes, the master brake cylinder, the diagram of the brake pipelines. Furthermore, each target of the designed system is analyzed for checking whether it meets the requirements. some factors are considered in this thesis, such as simple structure, low costs, and environmental protection, etc. The result shows that the design is reasonable and accurate, comparing with the related national standards.
Key words：light truck；brake；drum brake；master cylinder； 2) (+sin)R=178.91mm
=arctan=arctan0.3=16.7°
θ=90°—θ2=90°—90°2=45°
=arctan°
2）从蹄的效能因数
-+=16.7奥德赛°-5.83°+20°=30.87°
Kt= =1.6(0.8×cos30.87°1.1×cos5.83×sin16.7+1)
=0.5
后轮总的效能因数k27 Kt= Kt +Kt=1.03+0.5=1.53
2.前轮双向自增力效能因数：
摩擦衬片包角θ=102°θ=123°
摩擦衬片起始角θ=48° θ=30°
制动蹄支承点位置坐标a=118mm
制动蹄支承点位置坐标c=132mm
制动器中心到张开力P作用线的距离e=90mm
制动鼓半径 R=162.56mm
摩擦衬片包角 =90°
摩擦片摩擦系数=0.3~0.5 取0.3
=arctan=arctan0.3=16.7°
θ=90°—θ2=90°—90°2=45°
=2+车位尺寸-θ-θ2=7.7°
Kt= =0.92
次领蹄制动效能因数
Kt= =2.5
双增力总的效能因数Kt= Kt+ Kt=3.42
奇瑞qq汽车报价3.7 鼓式制动器零部件的结构设计
1）摩擦衬片
摩擦衬片选择应满足以下条件：具有稳定的摩擦因数，有良好的耐磨性。要尽可能小的压缩率和膨胀率。制动时不易产生噪音，对环境无污染。应采用对人体无害的摩擦材料。有较高的耐挤压强度和冲击强度，和抗剪切能力。摩擦衬块的热导率应控制在一定范围内。
2）制动底板
制动底板是除制动鼓外制动器各零件的安装基体，应保证各安装零件相互间的正确位置，制动底版承受着制动器工作时的制动反力矩，故应有足够的刚度，为此本次设计选用具有凹凸起伏形状的钢板冲压成型的制动底板。
3）摩擦材料
对汽车的摩擦材料有如下要求：
（1）具有高而稳定的摩擦系数，热衰退应该较为缓和，不能在温升到某一值后，摩擦系数三菱风迪思
骤然下降。
（2）耐磨性好
（3）吸水性和吸油率低
（4）有较高的耐挤压强度和冲压强度
（5）制动时不发生噪声和臭气
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