Thermal-structural coupling characteristics of axial piston pump slipper pair
-
摘要: 为了改善轴向柱塞泵滑靴副的耐磨损性能,建立了滑靴与斜盘摩擦副的瞬态热结构耦合模型,分析压力冲击条件下滑靴的表面温度、应力以及变形的变化规律.研究结果表明:某型轴向柱塞泵中滑靴温度随柱塞腔压力呈周期性变化,滑靴温度范围为45.5~49.8℃,且滑靴的最高温度出现在泵的吸排油过渡区.当滑靴处于泵的排油区时,滑靴的最大轴向应力为250MPa,集中在滑靴油腔与密封带之间的边缘区域.滑靴的轴向应力分层显著,引起滑靴的变形分化,其变形量为12.5~15μm,出现在滑靴的边缘.由于滑靴的输入热流密度增强磨粒的剪切力,加剧滑靴表面的微切削和挤压变形,导致滑靴表面出现条状剥落和凹坑磨损,呈现出黏着和磨粒磨损特征.Abstract: To improve the wear resistance of axial piston pump slipper pair, the transient thermal-structure coupling model was established based on the slipper/swash plate friction pair. Under the pressure shock condition, the slipper surface temperature, stress and deformation were analyzed. The results show that slipper temperature in a piston pump periodically changes with the piston chamber pressure and the range of slipper temperature from 45.5℃ to 49.8℃. The highest slipper temperature appears in the pump suction-discharge pressure transition zone. When the slipper runs in discharge pressure zone of pump, the maximum axial stress is 250MPa, which is concentrated on the edge region between slipper pocket and sealing belt. The layed axial stress of slipper is significant, causing the slipper deformation differentiation. The range of slipper deformation is from 12.5μm to 15μm, which appears at the edge of slipper. Shear force of abrasive particle is enhanced by input heat flux of slipper intensifying micro cutting and extrusion deformation. Furthermore, strip exfoliation and pits are presented by wear surface of slipper, which shows adhesive and abrasive wear characteristics.
-
Key words:
- thermal stress /
- temperature field /
- axial piston pump /
- slipper /
- thermal-structural coupling
-
[1] 李阳,邓海顺,王晓雷.织构化配流副摩擦磨损性能试验[J].航空动力学报,2014,29(7):1591-1596. LI Yang,DENG Haishun,WANG Xiaolei.Experiment on friction and wear performance of textured port plate pair[J].Journal of Aerospace Power,2014,29(7):1591-1596.(in Chinese) [2] Koc E,Hooke C J.Investigation into the effects of orifice size,offset and overclamp ratio on the lubrication of slipper bearings[J].Tribology International,1996,29(4):299-305. [3] Wieczorek U,Ivantysynova M.Computer aided optimization of bearing and sealing gaps in hydrostatic machines-the simulation tool CASPAR[J]. International Journal of Fluid Power,2002,3(1):7-20. [4] Bergada J M.Leakage and groove pressure of an axial piston pump slipper with multiple lands[J].Tribology Transactions,2008,51(4):469-481. [5] Kumar S,Bergada J M,Watton J.Axial piston pump grooved slipper analysis by CFD simulation of three-dimensional NVS equation in cylindrical coordinates[J].Computers and Fluids,2009,38(6):648-663. [6] Harris R M,Edge K A.Predicting the behavior of slipper pads in swash plate-type axial piston pumps[J].Journal of Dynamic System Measurement and Control,1996,118(5):41-47. [7] Harris R M,Edge K A,Tilley D G.The suction dynamics of positive displacement axial piston pumps[J].Journal of Dynamic System Measurement and Control,1994,116(2):1-7. [8] Manring N D.The relative motion between the ball guide and slipper retainer within an axial piston swash plate type hydrostatic pump[J].Journal of Dynamic System Measurement and Control,1999,121(3):518-523. [9] Manring N D,Wray C L,DONG Zhilin.Experimental studies on the performance of slipper bearings within axial-piston pumps[J].Journal of Tribology,2004,126(4):511-522. [10] Kazama T,Sasaki H,Narita Y.Simultaneous temperature measurements of bearing and seal pars of a swash plate type axial piston pump-effects of piston clearance and fluid property[J].Journal of Mechanical Science and Technology,2010,24(1):203-206. [11] Kazama T.Thermohydrodynamic lubrication model applicable to a slipper of swash plate type axial piston pumps and motors:effects of operating conditions[J].Tribology Online,2010,5(5):250-254. [12] Deeken M.Simulation of the reversing effects of axial piston pumps using conventional CAE tools[J].Ölhydraulik und Pneumatik,2002,46(6):1-12. [13] 何必海,孙健国,叶志锋.航空燃油柱塞泵滑靴静压润滑油膜计算分析[J].航空动力学报,2009,24(12):2821-2827. HE Bihai,SUN Jianguo,YE Zhifeng.Calculation and analysis on film thickness of the slippers based on hydrostatic bearing in the aeronautical fuel piston pump[J].Journal of Aerospace Power,2009,24(12):2821-2827.(in Chinese) [14] 徐兵,李迎兵,张斌,等.轴向柱塞泵滑靴副倾覆现象数值分析[J].机械工程学报,2010,46(20):161-168. XU Bing,LI Yingbing,ZHANG Bin,et al.Numerical simulation of overturning phenomenon of axial piston pump slipper pair[J].Journal of Mechanical Engineering,2010,46(20):161-168.(in Chinese) [15] 徐佩佩,叶志锋,王彬.航空燃油柱塞泵滑靴油膜的多目标优化设计[J].航空动力学报,2014,29(8):1981-1987. XU Peipei,YE Zhifeng,WANG Bin.Multi-objective optimization design of slipper film in aero-engine fuel piston pump[J].Journal of Aerospace Power,2014,29(8):1981-1986.(in Chinese) [16] 汤何胜,訚耀保,李晶.轴向柱塞泵滑靴副传热特征[J].北京航空航天大学学报,2016,42(3):489-496. TANG Hesheng,YIN Yaobao,LI Jing.Heat transfer characeristics of axial piston pump slipper pair[J].Journal of Journal of Beijing University of Aeronautics and Astronautics,2016,42(3):489-496.(in Chinese) [17] LI Jiayin,Barber J R.Solution of transient thermoelastic contact problems by the fast speed expansion method[J].Wear,2008,265(3/4):402-410. [18] 许耀铭.油膜理论与液压泵和马达的摩擦副设计[M].北京:机械工业出版社,1987:75-76.
点击查看大图
计量
- 文章访问数: 858
- HTML浏览量: 2
- PDF量: 591
- 被引次数: 0