对组合机床滑台动态性能的调查报告-------英文翻译与英文原文.doc
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对组合机床滑台动态性能的调查报告-------英文翻译与英文原文,this paper deals with the investigation for slide unit's impact and motion stabil¬ity in modular machine tool fay means of the method of power bond graph an...
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This paper deals with the investigation for slide unit's impact and motion stabil¬ity in modular machine tool fay means of the method of power bond graph and state space analysis. The dynamic mathematical model of self-adjusting back pressure speed control system used to drive slide unit is established. Main reasons and affect¬ing factors for slide unit impact and motion unstability are analysed through compu¬ter digital simulation, It is concluded from those that, if the structural dimensions of hydraulic cylinder and back pressure valve are designed rationally, the slide unit's dynamics will markedly be improved.
NOMENCLATURE
Sf flow source
Sei sliding friction force in slide unit
R equivalent viscous friction coefficient in slide unit
Ii mass of slide unit and cylinder
h mass of SABP valve spool
Ci,C2 hydraulic capacitances of rod chamber and non-rod chamber in cylinder re-
spec-tively
C3 spring compliance of SABP valve
R]rR2 hydraulic resistances of damping holes
R9 hydraulic resistance of orifice of SABP valve
Se2 presetting force of spring in SABP valve
I4J5 equivalent liquid inertia in pipe lines
C^Cg equivalent hydraulic capacitances in pipe lines
equivalent hydraulic resistances in pipe lines
V-j V^ oil-containing volumes in non-rod chamber and rod chamber respectively
P,r:, P-i oil pressures in non-rod chamber and rod chamber respectively
F load acted on slide unit
V slide unit velocity
* Department of Mechanical Engineering, Dalian Ur.iversity of Technology, Dalian. China.
【摘要】这一张纸处理调查利用有束缚力的曲线图和状态空间分析法对组合机床滑台的滑动影响和运动平稳性问题进行分析与研究，从而建立了滑台的液压驱动系统一自调背压调速系统的动态数学模型。通过计算机数字仿真系统，分析了滑台产生滑动影响和运动不平稳的原因及主要影响因素。从那些中可以得出那样的结论，如果能合理地设计液压缸和自调背压调压阀的结构尺寸.
本文中所使用的符号如下：
s1-流源，即调速阀出口流量；
Sel—滑台滑动摩擦力
R一滑台等效粘性摩擦系数：
I1—滑台与油缸的质量
12—自调背压阀阀心质量
C1、c2—油缸无杆腔及有杆腔的液容；
C2—自调背压阀弹簧柔度；
R1, R2自调背压阀阻尼孔液阻，
R9—自调背压阀阀口液阻
Se2—自调背压阀弹簧的初始预紧力；
I4, I5—管路的等效液感
C5、C6—管路的等效液容：
R5, R7-管路的等效液阻；
V3, V4—油缸无杆腔及有杆腔内容积；
P3, P4—油缸无杆腔及有杆腔的压力
F—滑台承受负载，
V—滑台运动速度。本文采用功率键合图和状态空间分折法建立系统的运动数学模型，滑台的动态特性可以能得到显著改善。
NOMENCLATURE
Sf flow source
Sei sliding friction force in slide unit
R equivalent viscous friction coefficient in slide unit
Ii mass of slide unit and cylinder
h mass of SABP valve spool
Ci,C2 hydraulic capacitances of rod chamber and non-rod chamber in cylinder re-
spec-tively
C3 spring compliance of SABP valve
R]rR2 hydraulic resistances of damping holes
R9 hydraulic resistance of orifice of SABP valve
Se2 presetting force of spring in SABP valve
I4J5 equivalent liquid inertia in pipe lines
C^Cg equivalent hydraulic capacitances in pipe lines
equivalent hydraulic resistances in pipe lines
V-j V^ oil-containing volumes in non-rod chamber and rod chamber respectively
P,r:, P-i oil pressures in non-rod chamber and rod chamber respectively
F load acted on slide unit
V slide unit velocity
* Department of Mechanical Engineering, Dalian Ur.iversity of Technology, Dalian. China.
【摘要】这一张纸处理调查利用有束缚力的曲线图和状态空间分析法对组合机床滑台的滑动影响和运动平稳性问题进行分析与研究，从而建立了滑台的液压驱动系统一自调背压调速系统的动态数学模型。通过计算机数字仿真系统，分析了滑台产生滑动影响和运动不平稳的原因及主要影响因素。从那些中可以得出那样的结论，如果能合理地设计液压缸和自调背压调压阀的结构尺寸.
本文中所使用的符号如下：
s1-流源，即调速阀出口流量；
Sel—滑台滑动摩擦力
R一滑台等效粘性摩擦系数：
I1—滑台与油缸的质量
12—自调背压阀阀心质量
C1、c2—油缸无杆腔及有杆腔的液容；
C2—自调背压阀弹簧柔度；
R1, R2自调背压阀阻尼孔液阻，
R9—自调背压阀阀口液阻
Se2—自调背压阀弹簧的初始预紧力；
I4, I5—管路的等效液感
C5、C6—管路的等效液容：
R5, R7-管路的等效液阻；
V3, V4—油缸无杆腔及有杆腔内容积；
P3, P4—油缸无杆腔及有杆腔的压力
F—滑台承受负载，
V—滑台运动速度。本文采用功率键合图和状态空间分折法建立系统的运动数学模型，滑台的动态特性可以能得到显著改善。
