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摘要:
柱塞泵摩擦副多场耦合建模及求解是柱塞泵失效机理研究及可靠性提升的基础，针对双斜式柱塞泵球面配流副多场耦合模型求解难的问题，提出油膜厚度场-压力场-温度场动态耦合模型及求解方法。在球面配流副受力分析的基础上结合雷诺方程和能量方程建立球面配流副油膜厚度场-压力场-温度场耦合模型；基于有限差分法和牛顿迭代法求解动态耦合模型，温度场、压力场、厚度场间相互耦合变化；通过仿真求解，与现有模型进行对比，结果相近且更符合实际，验证了所提模型及求解方法的有效性。
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关键词:
- 双斜式柱塞泵 /
- 球面配流副 /
- 厚度场-压力场-温度场耦合模型 /
- 有限差分法 /
- 牛顿迭代法
Abstract:The multi-field coupling modeling and solution of the friction pair of the piston pump is the basis for the study of the failure mechanism of the piston pump and the improvement of its reliability. To resolve the difficulty, in solving the multi-field coupling model of the spherical port pair of the double-oblique-type axial piston pump, a dynamic coupling model of oil film thickness field-pressure field-temperature field and its solution method are proposed. First, based on the force analysis of the spherical port pair, the Reynolds equation and the energy equation are combined to establish a coupling model of the thickness field-pressure field-temperature field of the spherical port pair. Secondly, the dynamic coupling model is solved based on the finite difference method. Finally, the simulation is compared with the existing model to verify the effectiveness of the proposed model and solution method.
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图 1 双斜式柱塞泵结构
1-斜盘 2-缸体 3-配油盘 4-柱塞
Figure 1. Structure of double-oblique-type axial piston pump
图 4 缸体配流副坐标系及其参数
Figure 4. Coordinate system and parameters of cylinder distribution pair
图 6 配流副油膜动态耦合模型仿真计算流程
Figure 6. Simulation calculation process of oil film dynamic coupling model of distribution pair
图 7 配流副油膜厚度、合力变化曲线
Figure 7. Curves of oil film thickness and resultant force of distribution pair
图 8 配流副油膜厚度场、压力场和温度场分布
Figure 8. Distribution of oil film thickness field, pressure field and temperature field of distribution pair
图 9 不同转角压力分布比较
Figure 9. Comparison of pressure distribution at different rotation angles
表 1 仿真数据
Table 1. Simulation data
参数 数值 转速/(${\rm{r}}\cdot{\rm{ min}}^{-1}$) 1500 高压区压强${p_{\text{h}}}$/MPa 30 低压区压强$ {p_{\rm{l}}} $/MPa 3 柱塞倾角$\beta $/(°) 5 斜盘倾角$\gamma $/(°) 15 配流盘曲率半径$R$/mm 58.9 圆锥半径${R_{\text{f}}}$/mm 103.8 柱塞直径$d$/mm 45 柱塞滑靴总质量${m_{{\text{ps}}}}$/g 1970 柱塞球头到柱塞副距离/mm 48.52 滑靴密封带内外半径/mm 25，20.9 黏压系数${\alpha _p}$ $1.8 \times {10^{ - 8}}$ 黏温系数${\alpha _T}$ 0.03 油液比热${c_p}$/(J·(kg·℃)−1) 1 884 油液密度$\rho $/(${\text{kg}} \cdot {{\text{m}}^ - }^{\text{3}}$) 850 
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