耦合滑靴副和配流副的柱塞泵振动及润滑特性研究

doi:10.3969/j.issn.1004-132X.2026.02.003

摘要/Abstract

摘要：

为探究轴向柱塞泵振动特性与油膜耦合作用的内在关联机制，构建了轴向柱塞泵各关键组件动力学模型，并与滑靴副及配流副的油膜润滑模型耦合，形成完整的耦合动力学分析框架。采用显隐结合法与控制容积法联合求解该模型，系统分析了不同工况下柱塞泵的振动响应以及滑靴副与配流副的油膜润滑行为，并通过振动实验验证模型的准确性。研究结果表明：在振动特性方面，耦合模型的预测结果与实验数据具有较高的吻合性；在油膜特性方面，转速增大导致中心油膜厚度增大，而压力增大则使高压区中心油膜厚度减小，油膜压力分布与柱塞腔压力呈同步周期性变化趋势，且油膜泄漏量随压力和转速的增大而显著增大，尤其在高压区增幅更大。研究结果为轴向柱塞泵设计提供了重要的理论支持。

关键词: 轴向柱塞泵, 滑靴副, 配流副, 耦合动力学模型, 振动特性, 油膜特性

Abstract:

This paper investigated the vibration-oil film coupling mechanism in axial piston pumps through an integrated dynamics model combining pump component dynamics with slipper/swashplate and valve plate/cylinder block lubrication models. The model was solved using a combined explicit-implicit approach with control volume method. Experimental validation confirmed the model effectiveness in predicting vibration characteristics. The results indicate that calculated results of coupled model show strong agreement with experimental data； in terms of oil film characteristics， increases of rotational speed lead to greater central oil film thickness， while pressure elevation results in reduces of oil film thickness at the center of high-pressure regions. The oil film pressure distribution exhibits periodic variation in sync with the plunger chamber pressure. Leakage increases markedly with both increases of pressure and speed， especially in high-pressure regions. The coupled model demonstrates superior predictive accuracy compared to conventional decoupled approaches. The research provides important theoretical support for the design of axial piston pumps.

Key words: axial piston pump, slipper pair, valve plate pair, coupled dynamics model, vibration characteristic, oil film characteristic

中图分类号:

TH137.51

赖荣燊, 朱小腾, 权云晴, 苗克非, 叶绍干, 鲍岳, 刘会祥, 赵守军. 耦合滑靴副和配流副的柱塞泵振动及润滑特性研究[J]. 中国机械工程, 2026, 37(2): 275-284.

LAI Rongshen, ZHU Xiaoteng, QUAN Yunqing, MIAO Kefei, YE Shaogan, BAO Yue, LIU Huixiang, ZHAO Shoujun. Research on Vibration and Lubrication Characteristics of Piston Pumps with Coupled Slipper Pair and Valve Plate Pair Interactions[J]. China Mechanical Engineering, 2026, 37(2): 275-284.

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链接本文: https://www.cmemo.org.cn/CN/10.3969/j.issn.1004-132X.2026.02.003

https://www.cmemo.org.cn/CN/Y2026/V37/I2/275

图/表 18

图1 耦合滑靴副和配流副油膜作用的柱塞泵动力学模型示意图

Fig.1 Schematic of piston pump dynamics model incorporating oil film interactions in slipper-swashplate and valve plate-cylinder interfaces

图2 滑靴副油膜厚度

Fig.2 Oil film thickness of slipper pair

图3 滑靴副油膜流体微元模型

Fig.3 Slipper pair oil film fluid micro-element model

图4 滑靴副油膜网格划分及控制容积

Fig.4 Slipper pair oil film mesh division and control volume

图5 配流副油膜网格划分

Fig.5 Meshing for oil film in port plate pair

图6 耦合动力学模型求解流程图

Fig.6 Flowchart for solving coupled dynamic model

图7 测点布置及实验设备连接示意图

Fig.7 Schematic diagram of measuring point arrangement and test equipment connection

图8 不同转速Y方向振动速度仿真与实验对比

Fig.8 Comparison of simulated and experimental Y-direction vibration velocities at different rotational speed

图9 不同压力下Y方向振动速度仿真与实验对比

Fig.9 Comparison of Y-direction vibration velocities between simulation and experiment under different pressures

表1 油膜耦合模型仿真参数

Tab.1 Simulation parameters of the oil film coupling model

斜盘倾角β/（°）	15.4
滑靴密封带内径r₁/mm	1.41
滑靴密封带外径r₂/mm	2.96
配流盘密封带内径R₁/mm	5.22
配流盘密封带外径R₂/mm	7.82
油液温度θ₀/℃	50
油液密度ρ/（kg·m $- 3$ ）	850
油液动力黏度μ/（Pa·s）	0.085

表1 油膜耦合模型仿真参数

Tab.1 Simulation parameters of the oil film coupling model

斜盘倾角β/（°）	15.4
滑靴密封带内径r₁/mm	1.41
滑靴密封带外径r₂/mm	2.96
配流盘密封带内径R₁/mm	5.22
配流盘密封带外径R₂/mm	7.82
油液温度θ₀/℃	50
油液密度ρ/（kg·m $- 3$ ）	850
油液动力黏度μ/（Pa·s）	0.085

图10 不同转速下的滑靴副油膜厚度场和压力场分布情况

Fig.10 Distribution of oil film thickness and pressure fields in slipper pair at different rotational speeds

图11 不同压力下的滑靴副油膜厚度场和压力场分布情况

Fig.11 The distribution of oil film thickness and pressure fields in the slipper pair under varying pressures

图12 不同转速下的滑靴副油膜泄漏功率

Fig.12 Leakage power of slipper pair oil film at different rotational speeds

图13 不同压力下的滑靴副油膜泄漏功率

Fig.13 Leakage power of the slipper pair oil film under different pressures

图14 不同转速下的配流副油膜厚度场和压力场分布情况

Fig.14 Distribution of oil film thickness and pressure field in the port plate pair under different rotational speeds

图15 不同压力下的配流副油膜厚度场和压力场分布情况

Fig.15 Distribution of oil film thickness and pressure fields in the port plate pair under varying pressures

图16 不同转速下的配流副油膜泄漏功率

Fig. 16 The leakage power of the oil film in the port plate pair under varying rotational speeds

图17 不同压力下的配流副油膜泄漏功率

Fig. 17 The oil film leakage power of the port plate paiunder varying pressures

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