阀配流压力脉动扰动下的柱塞泵滑靴副润滑特性

赵凯平; 何涛; 王传礼; 陈强曼; 罗刚

doi:10.13224/j.cnki.jasp.20220441

阀配流压力脉动扰动下的柱塞泵滑靴副润滑特性

doi: 10.13224/j.cnki.jasp.20220441

赵凯平^{1, 2,},
何涛^{1, 2,*, ,},
王传礼^{1, 2},
陈强曼¹,
罗刚¹

1.
安徽理工大学机械工程学院，安徽淮南 232001
2.
安徽理工大学矿山智能装备与技术安徽省重点实验室，安徽淮南 232001

基金项目: 国家自然科学基金（52205041）；安徽省高校优秀青年人才支持计划（gxyq2022017）；矿山智能装备与技术安徽省重点实验室开放基金（ZKSYS202101）；安徽省矿山智能技术与装备科研创新团队（2022AH010052）

详细信息

作者简介:
赵凯平（1997-），男，博士生，主要从事流体传动与控制技术研究。E-mail：zkp52262@163.com

通讯作者:
何涛（1987-），男，副教授，博士，主要从事流体传动与控制及矿山机电工程技术研究。E-mail：taoheaust@163.com

中图分类号: V228；TH137.5
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出版历程
- 收稿日期: 2022-06-20
- 网络出版日期: 2023-05-16

Lubrication characteristics of slipper pair of piston pump under the disturbance of valve distribution pressure pulsation

ZHAO Kaiping^{1, 2
,},
HE Tao^{1, 2,*
, ,},
WANG Chuanli^{1, 2},
CHEN Qiangman¹,
LUO Gang¹

1.
School of Mechanical Engineering， Anhui University of Science and Technology，Huainan Anhui 232001，China
2.
Anhui Key Laboratory of Mine Intelligent Equipment and Technology， Anhui University of Science and Technology，Huainan Anhui 232001，China

摘要

摘要:
阀配流轴向柱塞泵滑靴受力状态及油膜动态边界值与端面配流泵不同，为研究其润滑特性，建立一种应用于阀配流轴向柱塞泵的滑靴副工况模拟和数值解析耦合求解模型，分析柱塞运动频率、系统负载及不同分级定流量对滑靴副润滑特性的影响。结果表明：阀配流滑靴副主要在摩擦力矩作用方向发生倾覆，高压区到低压区的过渡期及低压区更易发生偏磨磨损；柱塞运动频率增大会降低滑靴发生倾覆偏磨的危险性，但也会降低滑靴副稳定性；系统负载增大会使油膜厚度减小，且高压区滑靴倾覆角减小，而低压区滑靴倾覆角增大；不同分级定流量下，当柱塞数大于3时，奇数柱塞组合时滑靴不易发生倾覆，而偶数柱塞组合时滑靴易发生倾覆磨损且高低压区压力变化幅度增大。
- 阀配流 /
- 压力脉动 /
- 轴向柱塞泵 /
- 滑靴副 /
- 润滑油膜
Abstract:
The stress state and oil film dynamic boundary value of slipper of valve distribution axial piston pump are different from those of end face distribution pump. In order to study its lubrication characteristics, a coupling model for slipper pair working condition simulation and numerical analysis applied to valve distribution axial piston pump was established to analyze the effects of plunger motion frequency, system load and different graded constant flows on the lubrication characteristics of slipper pair. The results showed that the sliding shoe pair of valve distribution overturned mainly in the direction of friction torque, and eccentric wear was more likely to occur in the transition period from high pressure zone to low pressure zone and in the low pressure zone; the increase of the plunger movement frequency could reduce the risk of overturning and eccentric wear of the slipper, but it may also reduce the stability of the slipper pair; with the increase of the system load, the oil film thickness decreased, and the overturning angle of the slipper in the high pressure area decreased, while the overturning angle of the slipper in the low pressure area increased; under different grading and constant flow rates, when the number of plungers was greater than 3, the slippers were not easy to overturn when the odd number of plungers were combined, while the slippers were easy to overturn and wear when the even number of plungers were combined, and the pressure change range in the high and low pressure zones increased.
- valve distribution /
- pressure pulsation /
- axial piston pump /
- slipper pair /
- lubricating oil film

HTML

图 1 阀配流轴向柱塞泵及配流阀结构示意图

Figure 1. Structure diagram of valve distribution axial piston pump and distribution valve

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图 2 阀配流轴向柱塞泵工况模拟仿真模型

Figure 2. Working condition simulation model of axial piston pump with valve distribution

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图 3 不同柱塞频率及系统负载下的柱塞腔压力

Figure 3. Piston cavity pressure under different piston frequencies and system loads

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图 4 不同柱塞组合供流下的柱塞腔压力

Figure 4. Piston chamber pressure under different piston combination supply

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图 5 滑靴副受力及油膜厚度场模型

Figure 5. Force and oil film thickness field model of slipper pair

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图 6 滑靴副相对运动及油膜密封带数值离散示意图

Figure 6. Schematic diagram of relative motion of slipper pair and numerical dispersion of oil film sealing belt

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图 7 阀配流轴向柱塞泵滑靴副润滑油膜耦合求解流程

Figure 7. Solution flow of lubricating oil film coupling of slipper pair of axial piston pump with valve distribution

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图 8 不同柱塞运动频率下的滑靴副油膜特性

Figure 8. Oil film characteristics of slipper pair under different piston motion frequencies

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图 9 不同系统负载下的滑靴副油膜特性

Figure 9. Oil film characteristics of slipper pair under different system loads

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图 10 不同柱塞组合供流下的滑靴副倾覆角θ_x、θ_y、θ_ot

Figure 10. Overturning angle of slipper pair under different piston combination supply θ_x，θ_y，θ_ot

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图 11 不同柱塞组合供流下的油膜中心膜厚

Figure 11. Central film thickness of oil film under different piston combination supply

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图 12 低压区θ_max和h_c（min）

Figure 12. θ_max and h_c（min） in low pressure area

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图 13 不同柱塞组合供流下的高压区油膜压力场（φ=90°）

Figure 13. Oil film pressure field in high pressure zone under different piston combination supply （φ=90°）

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图 14 不同柱塞组合供流下的低压区油膜压力场（φ=270°）

Figure 14. Oil film pressure field in low pressure zone under different piston combination supply（φ=270°）

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图 15 Ivantysynova团队油膜压力场分布

Figure 15. Distribution of oil film pressure field of Ivantysynova team

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图 16 本文计算所得油膜压力场分布

Figure 16. Distribution of oil film pressure field calculated in this paper

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表 1 配流阀关键参数

Table 1. Key parameters of distribution valve

参数	排液阀	吸液阀
阀口直径D_v/m	0.0055	0.009
阀芯直径d_v/m	0.013	0.015
阀芯质量m_v/kg	0.003	0.004
阀座半角γ_v/（°）	45	45
弹簧刚度k_sv/（N/m）	4000	3000
阀芯液动力F_v/N	3	2

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表 2 仿真与计算参数

Table 2. Simulation and calculation parameters

参数	数值
斜盘倾角/（°）	15
柱塞数S_n	9
柱塞直径d/m	0.022
单柱塞质量m_s/kg	0.045
柱塞质量m_p/kg	0.070
油液密度ρ/（kg/m³）	870
系统负载p_s/MPa	20
电动机转速/（r/min）	1500
阻尼孔长度l/m	0.0007
油膜密封带内半径r_in/m	0.0078
油膜密封带外半径r_out/m	0.0154
油液动力黏度μ /（N·S/m²）	0.02784
中心压紧弹簧刚度k/（N/m）	32500
中心弹簧压缩量Δx/m	0.0366

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