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中英文对照外文翻译文献(文档含英文原文和中文翻译)原文：FEATURE-BASED COMPONENT MODELS FOR VIRTUALPROTOTYPING OF HYDRAULIC SYSTERMAbstract:This paper proposes a feature-based approach for the virtual prototyping of hydraulic systems. It presents a framework which allows the designer to develop a virtual hydraulic system prototype in a more intuitive manner, i.e. through assembly of virtual components with engineering data. The approach is based on identifying the data required for the development of the virtual prototypes, and separating the information into behaviour, structural, and product attributes. Suitable representations of these attributes are presented, and the framework for the feature-based virtual prototyping approach is established,based on the hierarchical structure of components in a hydraulic system. The proposed framework not only provides a precise model of the hydraulic prototype but also offers the possibility of designing variation classes of prototypes whose members are derived by changing certain virtual components with different features.Key words: Computer-aided engineering; Fluid power systems;Virtualprototyping1.IntroductionHydraulic system design can be viewed as a function-to-form transformation process that maps an explicit set of requirements into a physical realisable fluid power system. The process involves three main stages: the functional specification stage,the configuration design stage, and the prototyping stage.The format for the description of the design in each stage is different.The functional specification stage constitutes the initial design work. The objective is to map the design requirements. To achieve this, the design problems are specified Correspondence and offprint requests to: Dr S. C. Fok, Schoool of Mechanical and Production Engineering, Nanyang Technological University, Nanyang Avenue, Singapore 639798. The designer must identify the performance attributes, which can include pressure, force, speed, and flowrate, with the required properties such as size, cost, safety and operating sequence. performance requirements for each attribute. In this stage, the design is abstracted in terms of the performance attributes with associated values.The objective of the configuration design stage is to synthesise a hydraulic circuit that performs the required functions conforming to the performance standards within defined constraints. A typical hydraulic system is made up of many subsystems. The smallest building block in a subsystem is the standard hydraulic component (such as valves, cylinders,pumps, etc.). Each type of standard component serves a specific elemental function. The design effort in the configuration design stage is fundamentally a search for a set of optimal arrangements of standard components (i.e. hydraulic circuit) to fulfil the functional requirements of the system. Based on this framework, the designers would normally decompose the overall system functions in terms of subfunctions. This will partition the search space and confine the search for smaller hydraulic subcircuits to perform the subfunctions.Computers are often used to support the configuration design process. For example, Kota and Lee devised a graph-based strategy to automate the configuration of hydraulic circuits. After the development of the hydraulic circuits, digital simulation tools are often used to study and evaluate these configurations. With these tools, designers can compare the behaviour of different circuits and also analyse the effects when subcircuits are combined. In the configuration design stage, the design is traditionally represented as a circuit drawing using standard icons to symbolise the type of standard component. This is a form of directed graph S(C,E) where the circuit S contains components C in the form of nodes with relations between components denoted by edges E.The prototyping stage is the verification phase of the system design process where the proposed hydraulic circuit from the configuration design stage isdeveloped and evaluated. Physical prototyping aims to build a physical prototype of the hydraulic system 666 S. C. Fok et al. using industrial available components. The process of physical prototyping involves the following: Search for appropriate standard components from different manufacturers. Pre-evaluation and selection of components based on individual component cost, size, and specification, and compatibility factors between components. Procurement and assembly of the selected components.Test and evaluate the physical prototype based on the overall system requirements. Use other components or redesign the circuit (or subcircuits)if necessary.Besides dynamics, the development of the physical prototype must take into consideration other factors including structure,cost, and weight. The dynamics data are used to confirm the fluid power system behaviour whereas the geometric information is used to examine the assembly properties. The development of the physical prototype will provide the actual performance,structure, and cost of the design.The main disadvantage of physical prototyping is that it is very tedious and time consuming to look for a set of suitable combinations of standard components from among so many manufacturers. Although the basic functions of the same types of standard component from different manufacturers do not differ, their dynamics, structural and cost characteristics may not be similar, because of design variation. Hence, for a given hydraulic circuit, different combinations of parts from differentmanufacturers can have implications on the resulting system,in terms of dynamics, structure, and cost. Value engineering can be used at this stage to improve the system design by improving the attributes at the component level. This includes maximizing the performance-to-cost ratio and minimising the size-to-performance ratio. Virtual prototyping can be viewed as a computer-aided design process, which employs modelling and simulating tools to address the broad issues of physical layout, operationalconcept, functional specifications, and dynamics analysis under various operating environments. The main advantage of virtual prototyping is that a hydraulic system prototype can be assembled, analysed, and modified using digital computers without the need for physical components, thus saving lead time and cost.The main requirement of a virtual hydraulic system prototype is to provide the same information as a physical prototype for the designer to make decisions.To achieve this, the virtual prototype must provide suitable and comprehensive representations of different data. Furthermore, transformation from one representation to another should proceed formally. Xiang et al. have reviewed the past and current computer-aided design and prototyping tools for fluid power systems. The work revealed that the current tools could not provide a completerepresentation of the design abstractions at the prototyping stage for design judgement. Most of the tools concentrate on the dynamics behaviour. Vital geometrical and product information that relates to the system prototype consideration and evaluation is frequently missing.To advance the development of computer-aided virtual prototyping tools for fluid power systems, there is a need to address the formal representations of different abstractions of behaviour,structural, and product data along with their integration. This paper focuses on these issues and proposes the formalism of a unified component model and the taxonomy based on the feature-based approach. In Section 2, we discuss the feature- based approach focusing on the key information and their representations required for hydraulic system prototyping. Section 3 presents a formalism of the feature-based model and structure for the development of virtual hydraulic system prototypes.The structure is illustrated with an example. Future work and conclusions are given in Section 4.2. Feature-Based ApproachFeatures can be defined as information sets that refer to aspects of attributes that can be used in reasoning about the design, engineering or manufacturing processes. The concept of using features to integrate CAD/CAPP/CAM is not new and there are many papers on the application of this approach in CIM. In all these applications, the feature model is regarded as the basis whereas design by features is the key for the integration. To develop a feature model, the relevant information concerning the design must be identified and grouped into sets based on the nature of the information. The relevant information should contain sufficient knowledge for activities such as design, analysis, test, documentation, inspection, and assembly, as well as support various administrative and logistic functions. Design by features is the process of building a model of the design using features as primitive entities. The feature model provides the standardisation of relevant data. Through the design by features approach, vital knowledge of the design will be generated and stored. Together, the feature model and the design by features approach will provide the essential information, which can be used, not only for the simultaneous consideration of many different concerns with the design, but also to interface the many activities in the design realisation process, including the life cycle support operations. The main drawback of the feature-based design approach is that the feature model should be properly defined . This can be difficult, as features are sets of knowledge that are application dependent. The organisation of the features can also be application specific. Non-trivial data-management problems could arise if the feature model is not properly defined. To avoid these problems, the type,representation and structure of the features should be resolved prior to using the feature-based design methodology. The main concern when developing afeature model is that it is application-specific. In the domain of virtual prototyping of hydraulic systems, the details of the constituent standard components must be able to be used to describe the overall system. The component features are bearers of knowledge about that part. To create a suitable feature model for hydraulic system design based on the assembly of standard components, the relevant information associated with various standard components must be identified and classified. This definition Feature-Based Component Models 667 of the component feature set can then be extended to encompass the subsystem feature set based on the hierarchical structure between the components in the subsystem. In the same manner, a hierarchical structure for the hydraulic system feature representation would evolve by considering the system as a hierarchy of subsystems.The necessary information required for a proper description of the virtual prototype must be no less than that derived by the designer from a physical prototype for decision making. These data should generally include the shape, weight, performance properties, cost, dimensions, functionality data, etc. Comparison with the physical prototyping process, the information required for each standard component could be separated into three distinct groups: behaviour attributes, structural attributes, and product attributes.2.1 Behaviour AttributesThe behaviour of a hydraulic component can be defined in terms of the dynamics characteristics used to satisfy the functional requirements. Consider a hydraulic cylinder connected to a load. Its function is to transmit a force from the stroke of the piston to the load. The maximum force it can transmit can be used to define the functionality and the behaviour requirements can be specified in terms of the desired load acceleration characteristics. Hence for a hydraulic component, behaviour attributes express functionality and can be reflected in the dynamics characteristics. The designer is responsible for the proper definition of the overall system behaviour characteristics in terms of the desired dynamics. A standard component will have its own behaviour and provide a specific plex functions that cannot be achieved by a single standard component are derived using a combination of components. Hence, the behaviour of the standard component will play an important role as the individual behaviours of components together with their arrangement can alter the overall system function .The behaviour of a standard component can be nonlinear and can be dependent on the operating conditions. When two components are combined, it is possible that their behaviours can interact and produce undesired or unintended characteristics. These unwanted behaviours are assumed to have been resolved during the configuration design stage. The hydraulic circuit used in theprototyping stage is assumed to be realisable and without any undesirable interacting behaviours. This means that the output behaviour of a component will provide the input to the subsequent component.The representation of behaviours for hydraulic systems has been widely investigated. These representations include transfer functions, state-space and bond graphs. Transfer functions (for single-input–single-output systems) and state-space equations (for multiple-input–multiple-output systems) are based on the approximation of the dynamics about a nominal operating condition. The power bond graph model is based on the causal effects that describe the energy transformations in the hydraulic system. This approach is appealing for hydraulic system analysis. The main disadvantage is that the derivation of the dynamics equation in a bond graph of a complicated fluid power system can become very tedious. As a result, recent work has concentrated on the used of artificial intelligence to represent the nonlinear mapping between the input and output data, which can be obtained via experimental work. These nonlinear mappings can be accomplished using artificial neural networks .It is quite natural for a hydraulic system designer to use input–output data to describe the behaviour of a hydraulic component. The configuration design of a hydraulic system is often achieved through steps of function decomposition. To design a hydraulic system, the designer often tries to decompose the functions and their requirements down to the component level.译文：基于原型液压系统特征的机构模型摘要：本文为原型液压系统的设计提出了一种基于特征的方法。

液压机外文翻译文献

液压机外文翻译文献(文档含中英文对照即英文原文和中文翻译)原文：The Analysis of Cavitation Problems in the Axial Piston Pumpshu WangEaton Corporation,14615 Lone Oak Road,Eden Prairie, MN 55344This paper discusses and analyzes the control volume of a piston bore constrained by the valve plate in axial piston pumps. The vacuum within the piston bore caused by the rise volume needs to be compensated by the flow; otherwise, the low pressure may cause the cavitations and aerations. In the research, the valve plate geometry can be optimized by some analytical limitations to prevent the piston pressure below the vapor pressure. The limitations provide the design guide of the timings andoverlap areas between valve plate ports and barrel kidneys to consider the cavitations and aerations. _DOI: 10.1115/1.4002058_ Keywords: cavitation , optimization, valve plate, pressure undershoots1 IntroductionIn hydrostatic machines, cavitations mean that cavities or bubbles form in the hydraulic liquid at the low pressure and collapse at the high pressure region, which causes noise, vibration, and less efficiency.Cavitations are undesirable in the pump since the shock waves formed by collapsed may be strong enough to damage components. The hydraulic fluid will vaporize when its pressure becomes too low or when the temperature is too high. In practice, a number of approaches are mostly used to deal with the problems: (1) raise the liquid level in the tank, (2) pressurize the tank, (3) booster the inlet pressure of the pump,(4) lower the pumping fluid temperature, and (5) design deliberately the pump itself.Many research efforts have been made on cavitation phenomena in hydraulic machine designs. The cavitation is classified into two types in piston pumps: trapping phenomenon related one (which can be prevented by the proper design of the valve plate)and the one observed on the layers after the contraction or enlargement of flow passages (caused by rotating group designs) in Ref. (1). The relationship between the cavitation and the measured cylinder pressure is addressed in this study. Edge and Darling (2) reported an experimental study of the cylinder pressure within an axial piston pump. The inclusion of fluid momentum effects and cavitations within the cylinder bore are predicted at both highspeed and high load conditions. Another study in Ref. (3) provides an overview of hydraulic fluid impacting on the inlet condition and cavitation potential. It indicates thatphysical properties (such as vapor pressure, viscosity, density, and bulk modulus) are vital to properly evaluate the effects on lubrication and cavitation. A homogeneous cavitation model based on the thermodynamic properties of the liquid and steam is used to understand the basic physical phenomena of mass flow reduction and wave motion influences in the hydraulic tools and injection systems (4). Dular et al. (5, 6) developed an expert system for monitoring and control of cavitations in hydraulic machines and investigated the possibility of cavitation erosion by using the computational fluid dynamics (CFD) tools. The erosion effects of cavitations have been measured and validated by a simple single hydrofoil configuration in a cavitation tunnel. It is assumed that the severe erosion is often due to the repeated collapse of the traveling vortex generated by a leading edge cavity in Ref. (7). Then, the cavitation erosion intensity may be scaled by a simple set of flow parameters: theupstream velocity, the Strouhal number, the cavity length, and the pressure. A new cavitation erosion device, called vortex cavitation generator, is introduced to comparatively study various erosion situations (8).More previous research has been concentrated on the valve plate designs, piston, and pump pressure dynamics that can be associated with cavitations in axial piston pumps. The control volume approach and instantaneous flows (leakage) are profoundly studied in Ref. [9]. Berta et al. [10] used the finite volume concept to develop a mathematical model in which the effects of port plate relief grooves have been modeled and the gaseous cavitation is considered in a simplified manner. An improved model is proposed in Ref.[11] and validated by experimental results. The model may analyze the cylinder pressure and flow ripples influenced by port plate and relief groove design. Manring comparedprincipal advantages of various valve plate slots (i.e., theslots with constant, linearly varying, and quadratic varyingareas) in axial piston pumps [12]. Four different numericalmodels are focused on the characteristics of hydraulic fluid,and cavitations are taken into account in different ways toassist the reduction in flow oscillations [13].The experiences of piston pump developments show thatthe optimization of the cavitations/aerations shall includethe following issues: occurring cavitation and air release,pump acoustics caused by the induced noises, maximal amplitudes of pressure fluctuations, rotational torque progression, etc. However, the aim of this study is to modifythe valve plate design to prevent cavitation erosions causedby collapsing steam or air bubbles on the walls of axial pump components. In contrast to literature studies, the researchfocuses on the development of analytical relationshipbetween the valve plate geometrics and cavitations. The optimization method is applied to analyze the pressure undershoots compared with the saturated vapor pressurewithin the piston bore.The appropriate design of instantaneous flow areas betweenthe valve plate and barrel kidney can be decided consequently.2 The Axial Piston Pump and Valve PlateThe typical schematic of the design of the axis piston pumpis shown in Fig. 1. The shaft offset e is designed in this caseto generate stroking containment moments for reducingcost purposes.The variation between the pivot center of the slipper andswash rotating center is shown as a. The swash angle αis the variable that determines the amount of fluid pumped pershaft revolution. In Fig. 1, the n th piston-slipper assembly is located at the angle of nθ. The displacement of the n thpiston-slipper assembly along the x-axis can be written asx n = R tan （α）sin （n θ）+ a sec （α） + e tan (α) (1) where R is the pitch radius of the rotating group. Then, the instantaneous velocity of the n th piston is x˙n = R 2sec ()αsin （n θ）α+ R tan （α）cos （n θ）ω+ R 2sec ()αsin （α）α + e 2sec ()αα (2) where the shaft rotating speed of the pump is ω=d n θ / dt .The valve plate is the most significant device to constraint flow in piston pumps. The geometry of intake/discharge ports on the valve plate and its instantaneous relative positions with respect to barrel kidneys are usually referred to the valve plate timing. The ports of the valve plate overlap with each barrel kidneys to construct a flow area or passage, which confines the fluid dynamics of the pump. In Fig. 2, the timing angles of the discharge and intake ports on the valve plate are listed as (,)T i d δ and (,)B i d δ. The opening angle of the barrel kidney is referred to as ϕ. In some designs, there exists asimultaneous overlap between the barrel kidney and intake/discharge slots at the locations of the top deadcenter (TDC) or bottom dead center (BDC) on the valve plate on which the overlap area appears together referred to as “cross-porting” in the pump design engineering. The cross-porting communicates the discharge and intake ports, which may usually lower the volumetric efficiency. The trapped-volume design is compared with the design of the cross-porting, and it can achieve better efficiency 14]. However, the cross-porting isFig. 1 The typical axis piston pump commonly used to benefit the noise issue and pump stability in practice.3 The Control Volume of a Piston BoreIn the piston pump, the fluid within one piston is embraced by the piston bore, cylinder barrel, slipper,valve plate, and swash plate shown in Fig. 3. There exist some types of slip flow by virtue of relative Fig. 2 Timing of the valve plate motions and clearances between thos e components. Within the control volume of each piston bore, the instantaneous mass is calculated asn M = ρn V (3) where ρ and n V are the instantaneous density and volume such that themass time rate of change can be given asFig. 3 The control volume of the piston boren n n dM dV d V dt dt dtρρ=+ (4)where d n V is the varying of the volume.Based on the conservation equation, the mass rate in the control volume isn n dM q dtρ= (5) where n q is the instantaneous flow rate in and out of onepiston. From the definition of the bulk modulus,n dP d dt dtρρβ= (6) where Pn is the instantaneous pressure within the piston bore. Substituting Eqs. (5) and (6) into Eq. (4) yields(?)n n n n n ndP q dV d V w d βθθ=- (7) where the shaft speed of the pump is n d dt θω=. The instantaneous volume of one piston bore can be calculated by using Eq. (1) asn V = 0V + P A [R tan （α）sin （n θ）+ a sec （α） + e tan (α) ](8) where P A is the piston sectional area and 0V is the volume of each piston, which has zero displacement along the x-axis (when n θ=0, π).The volume rate of change can be calculated at thecertain swash angle, i.e., α =0, such thattan cos n p n ndV A R d αθθ=（）（） (9) in which it is noted that the piston bore volume increases or decreases with respect to the rotating angle of n θ. Substituting Eqs. (8) and (9) into Eq. (7) yields0[tan()cos()] [tan sin sec tan() ]n P n n n p n q A R dP d V A R a e βαθωθαθαα-=-++（）（）（）(10)4 Optimal DesignsTo find the extrema of pressure overshoots and undershoots in the control volume of piston bores, the optimization method can be used in Eq. (10). In a nonlinear function, reaching global maxima and minima is usually the goal of optimization. If the function is continuous on a closed interval, global maxima and minima exist. Furthermore, the global maximum (or minimum) either must be a local maximum (or minimum) in the interior of the domain or must lie on the boundary of the domain. So, the method of finding a global maximum (or minimum) is to detect all the local maxima (or minima) in the interior, evaluate themaxima (or minima) points on the boundary, and select the biggest (or smallest) one. Local maximum or local minimum can be searched by using the first derivative test that the potential extrema of a function f( · ), with derivative ()f ', can solve the equation at the critical points of ()f '=0 [15]. The pressure of control volumes in the piston bore may be found as either a minimum or maximum value as dP/ dt=0. Thus, letting the left side of Eq. (10) be equal to zero yields tan()cos()0n p n q A R ωαθ-= (11) In a piston bore, the quantity of n q offsets the volume varying and then decreases the overshoots and undershoots of the piston pressure. In this study, the most interesting are undershoots of the pressure, which may fall below the vapor pressure or gas desorption pressure to cause cavitations. The term oftan()cos()p n A R ωαθ in Eq. (11) has the positive value in the range of intake ports (22ππθ-≤≤), shown in Fig. 2, which means that the piston volume arises. Therefore, the piston needs the sufficient flow in; otherwise, the pressure may drop.In the piston, the flow of n q may get through in a few scenarios shown in Fig. 3: (I) the clearance between the valve plate and cylinder barrel, (II) the clearance between the cylinder bore and piston, (III) theclearance between the piston and slipper, (IV) the clearance between the slipper and swash plate, and (V) theoverlapping area between the barrel kidney and valve plate ports. As pumps operate stably, the flows in the as laminar flows, which can be calculated as [16]312IV k k Ln i I k h q p L ωμ==∑ (12)where k h is the height of the clearance, k L is the passagelength,scenarios I –IV mostly have low Reynolds numbers and can be regardedk ω is the width of the clearance (note that in the scenario II,k ω =2π· r, in which r is the piston radius), and p is the pressure drop defined in the intake ports as p =c p -n p (13) where c p is the case pressure of the pump. The fluid films through the above clearances were extensively investigated in previous research. The effects of the main related dimensions of pump and the operating conditions on the film are numerically clarified in Refs. [17,18]. The dynamic behavior of slipper pads and the clearance between the slipper and swash plate can be referred to Refs. [19,20]. Manring et al. [21,22]investigated the flow rate and load carrying capacity of the slipper bearing in theoretical and experimental methods under different deformation conditions. A simulation tool called CASPAR is used to estimate the nonisothermal gap flow between the cylinder barrel and the valve plate by Huang and Ivantysynova [23]. The simulation program also considers the surface deformations to predict gap heights, frictions, etc., between the piston and barrel and between the swash plate and slipper. All these clearance geometrics in Eq. (12) are nonlinear and operation based, which is a complicated issue. In this study, the experimental measurements of the gap flows are preferred. If it is not possible, the worst cases of the geometrics or tolerances with empirical adjustments may be used to consider the cavitation issue, i.e., minimum gap flows.For scenario V, the flow is mostly in high velocity and can be described by using the turbulent orifice equation as((Tn d i d d q c A c A θθ= (14) where Pi and Pd are the intake and discharge pressure of the pump and ()i A θ and ()d A θ are the instantaneousoverlap area between barrel kidneys and inlet/discharge ports of the valve plate individually.The areas are nonlinear functions of the rotating angle, which is defined by the geometrics of the barrel kidney, valve plate ports, silencing grooves, decompression holes, and so forth. Combining Eqs. (11) –(14), the area can beobtained as3()K IV A θ==(15)where ()A θ is the total overlap area of ()A θ=()()i d A A θλθ+, andλis defined as=In the piston bore, the pressure variesfrom low to high while passing over the intake and discharge ports of the valve plates. It is possible that the instantaneous pressure achieves extremely low values during the intakearea( 22ππθ-≤≤ shown in Fig. 2) that may be located below the vapor pressure vp p , i.e., n vp p p ≤;then cavitations canhappen. To prevent the phenomena, the total overlap area of ()A θmight be designed to be satisfied with30()K IV A θ=≥(16)where 0()A θ is the minimum area of 0()A θ=0()()i d A A θλθ+and0λis a constant that is0λ=evaporates into a gaseous form. The vapor pressure of any substance increases nonlinearly with temperature according to the Clausius –Clapeyron relation. With the incremental increase in temperature, the vapor pressure becomes sufficient to overcome particle attraction and make the liquid form bubbles inside the substance. For pure components, the vapor pressure can be determined by the temperature using the Antoine equation as /()10A B C T --, where T is the temperature, and A, B, and C are constants [24]. As a piston traverse the intake port, the pressure varies dependent on the cosine function in Eq. (10). It is noted that there are some typical positions of the piston with respect tothe intake port, the beginning and ending of overlap, i.e., TDC and BDC (/2,/2θππ=- ) and the zero displacement position (θ =0). The two situations will be discussed as follows: (1) When /2,/2θππ=-, it is not always necessary to maintain the overlap area of 0()A θ because slip flows may provide filling up for the vacuum. From Eq. (16), letting 0()A θ=0,the timing angles at the TDC and BDC may be designed as31cos ()tan()122IV c vpk k i I P k p p h A r L ωϕδωαμ--≤+∑ (17) in which the open angle of the barrel kidney is . There is no cross-porting flow with the timing in the intake port.(2) When θ =0, the function of cos θ has the maximum value, which can provide another limitation of the overlap area to prevent the low pressure undershoots suchthat 30(0)K IV A =≥ (18)where 0(0)A is the minimum overlap area of 0(0)(0)i A A .To prevent the low piston pressure building bubbles, the vapor pressure is considered as the lower limitation for the pressure settings in Eq. (16). The overall of overlap areas then can be derived to have a design limitation. The limitation is determined by the leakage conditions, vapor pressure, rotating speed, etc. It indicates that the higher the pumping speed, the more severe cavitation may happen, and then the designs need more overlap area to let flow in the piston bore. On the other side, the low vapor pressure of the hydraulic fluid is preferred to reduce the opportunities to reach the cavitation conditions. As a result, only the vapor pressure of the pure fluid is considered in Eqs. (16)–(18). In fact, air release starts in the higher pressure than the pure cavitation process mainly in turbulent shear layers, which occur in scenario V. Therefore, the vapor pressure might be adjusted to design the overlap area by Eq. (16) if there exists substantial trapped and dissolved air in the fluid. The laminar leakages through the clearances aforementioned are a tradeoff in the design. It is demonstrated that the more leakage from the pump case to piston may relieve cavitation problems.However, the more leakage may degrade the pump efficiency in the discharge ports. In some design cases, the maximum timing angles can be determined by Eq. (17)to not have both simultaneous overlapping and highly low pressure at the TDC and BDC. While the piston rotates to have the zero displacement, the minimum overlap area can be determined by Eq. 18 , which may assist the piston not to have the large pressure undershoots during flow intake.6 Conclusions The valve plate design is a critical issue in addressing thecavitation or aeration phenomena in the piston pump. This study uses the control volume method to analyze the flow, pressure, and leakages within one piston bore related to the valve plate timings. If the overlap area developed by barrel kidneys and valve plate ports is not properly designed, no sufficient flow replenishes the rise volume by the rotating movement. Therefore, the piston pressure may drop below the saturated vapor pressure of the liquid and air ingress to form the vapor bubbles. To control the damaging cavitations, the optimization approach is used to detect the lowest pressure constricted by valve plate timings. The analytical limitation of the overlap area needs to be satisfied to remain the pressure to not have large undershoots so that the system can be largely enhanced on cavitation/aeration issues. In this study, the dynamics of the piston control volume is developed by using several assumptions such as constant discharge coefficients and laminar leakages. The discharge coefficient is practically nonlinear based on the geometrics, flow number, etc. Leakage clearances of the control volume may not keep the constant height and width as well in practice due to vibrations and dynamical ripples. All these issues are complicated and very empirical and need further consideration in the future. The results presented in this paper can be more accurate in estimating the cavitations with these extensive studies. Nomenclature0(),()A A θθ= the total overlap area between valve plate ports and barrel kidneys 2()mm Ap = piston section area 2()mm A, B, C= constants A= offset between the piston-slipper joint and surface of the swash plate 2()mmd C = orifice discharge coefficiente= offset between the swash plate pivot and the shaft centerline of the pump 2()mmk h = the height of the clearance 2()mmk L = the passage length of the clearance 2()mm M= mass of the fluid within a single piston (kg) N= number of pistons n = piston and slipper counter,p p = fluid pressure and pressure drop (bar) Pc= the case pressure of the pump (bar) Pd= pump discharge pressure (bar) Pi = pump intake pressure (bar) Pn = fluid pressure within the nth piston bore (bar) Pvp = the vapor pressure of the hydraulic fluid(bar) qn, qLn, qTn = the instantaneous flow rate of each piston (l/min) R = piston pitch radius 2()mmr = piston radius (mm )t =time (s )V = volume 3()mmwk = the width of the clearance (mm )x ,x˙= piston displacement and velocity along the shaft axis (m, m/s )x y z --=Cartesian coordinates with an origin on the shaft centerlinex y z '''--= Cartesian coordinates with an origin on swash plate pivot,αα=swash plate angle and velocity (rad, rad/s )β= fluid bulk modulus (bar ),B T δδ= timing angle of valve plates at the BDC and TDC (rad ) ϕ = the open angle of the barrel kidney (rad )ρ= fluid density (kg /m3),θω = angular position and velocity of the rotating kit (rad, rad/s )μ =absolute viscosity (Cp ),λλ=coefficients related to the pressure drop翻译：在轴向柱塞泵气蚀问题的分析本论文讨论和分析了一个柱塞孔与配流盘限制在轴向柱塞泵的控制量设计。

液压系统外文翻译解析

(外文翻译——中文)液压系统液压传动和气压传动称为流体传动，是根据17世纪帕斯卡提出的液体静压力传动原理而发展起来的一门新兴技术，1795年英国约瑟夫•布拉曼(Joseph Braman,1749-1814)，在伦敦用水作为工作介质，以水压机的形式将其应用于工业上，诞生了世界上第一台水压机。

1905年将工作介质水改为油，又进一步得到改善。

第一次世界大战(1914-1918)后液压传动广泛应用，特别是1920年以后，发展更为迅速。

液压元件大约在 19 世纪末 20 世纪初的20年间，才开始进入正规的工业生产阶段。

1925 年维克斯(F.Vikers)发明了压力平衡式叶片泵,为近代液压元件工业或液压传动的逐步建立奠定了基础。

20 世纪初康斯坦丁•尼斯克(G•Constantimsco)对能量波动传递所进行的理论及实际研究;1910年对液力传动(液力联轴节、液力变矩器等)方面的贡献，使这两方面领域得到了发展。

第二次世界大战(1941-1945)期间,在美国机床中有30%应用了液压传动。

应该指出,日本液压传动的发展较欧美等国家晚了近 20 多年。

在 1955 年前后 , 日本迅速发展液压传动,1956 年成立了“液压工业会”。

近20～30 年间，日本液压传动发展之快，居世界领先地位。

液压传动有许多突出的优点，因此它的应用非常广泛，如一般工业用的塑料加工机械、压力机械、机床等；行走机械中的工程机械、建筑机械、农业机械、汽车等；钢铁工业用的冶金机械、提升装置、轧辊调整装置等；土木水利工程用的防洪闸门及堤坝装置、河床升降装置、桥梁操纵机构等；发电厂涡轮机调速装置、核发电厂等等；船舶用的甲板起重机械（绞车）、船头门、舱壁阀、船尾推进器等；特殊技术用的巨型天线控制装置、测量浮标、升降旋转舞台等；军事工业用的火炮操纵装置、船舶减摇装置、飞行器仿真、飞机起落架的收放装置和方向舵控制装置等。

一个完整的液压系统由五个部分组成，即动力元件、执行元件、控制元件、辅助元件和液压油。

液压机械与液压泵外文翻译文献

液压机械与液压泵外文翻译文献液压机械与液压泵外文翻译文献(文档含中英文对照即英文原文和中文翻译)Hydraulic machinery and pumpHydraulic machinery are machines and tools which use fluid power to do work. Heavy equipment is a common example.In this type of machine, high-pressure liquid - called hydraulic fluid - is transmitted throughout the machine to various hydraulic motors and hydraulic cylinders. The fluid is controlled directly or automatically by control valves and distributed through hoses and tubes.The popularity of hydraulic machinery is due to the very large amount ofpower that can be transferred through small tubes and flexible hoses, and the high power density and wide array of actuators that can make use of this power.Hydraulic machinery is operated by the use of hydraulics, where a liquid is the powering medium. Pneumatics, on the other side, is based on the use of a gas as the medium for power transmission, generation and control.Hydraulic circuitsFor the hydraulic fluid to do work, it must flow to the actuator and or motors, then return to a reservoir.The fluid is then filtered and re-pumped. The path taken by hydraulic fluid is called a hydraulic circuit of which there are several types. Open center circuits use pumps which supply a continuous flow. The flow is returned to tank through the control valve's open center; that is, when the control valve is centered, it provides an open return path to tank and the fluid is not pumped to a high pressure. Otherwise, if the control valve is actuated it routes fluid to and from an actuator and tank. The fluid's pressure will rise to meet any resistance, since the pump has a constant output. If the pressure rises too high, fluid returns to tank through a pressure relief valve.Hydraulic pumps supply fluid to the components in the system. Pressure in the system develops in reaction to the load. Hence,a pump rated for 5,000 psi is capable of maintaining flow against a load of 5,000 psi.Pumps have a power density about ten times greater than an electric motor (by volume). They are powered by an electric motor or an engine, connected through gears, belts, or a flexible elastomeric coupling to reduce vibration.Common types of hydraulic pumps to hydraulic machinery applications are;Gear pump: cheap, durable, simple. Less efficient, because they are constant displacement, and mainly suitable for pressures below 20 MPa (3000 psi).Vane pump: cheap and simple, reliable (especially in g-rotor form). Good for higher-flow low-pressure output.Axial piston pump: many designed with a variable displacement mechanism, to vary output flow for automatic control of pressure. There are various axial piston pump designs, including swashplate and checkball. The most common is the swashplate pump.Radial piston pump: A pump that is normally used for very high pressure at small flows.Piston pumps are more expensive than gear or vane pumps, but provide longer life operating at higher pressure, with difficult fluids and longer continuous duty cycles. Pistonpumps make up one half of a hydrostatic transmission. Control valvesDirectional control valves route the fluid to the desired actuator. They usually consist of a spool inside a cast iron or steel housing.Directional control valves are usually designed to be stackable, with one valve for each hydraulic cylinder, and one fluid input supplying all the valves in the stack.The spool position may be actuated by mechanical levers, hydraulic pilot pressure, or solenoids which push the spool left or right.The main valve block is usually a stack of off the shelf directional control valves chosen by flow capacity and performance. Some valves are designed to be proportional (flow rate proportional to valve position), while others may be simply on-off. The control valve is one of the most expensive and sensitive parts of a hydraulic circuit.Pressure relief valves are used in several places in hydraulic machinery; on the return circuit to maintain a small amount of pressure for brakes, pilot lines, etc... On hydraulic cylinders, to prevent overloading and hydraulic line rupture. On the hydraulic reservoir, to maintain a small positive pressurewhich excludes moisture and contamination.Pressure reducing valves reduce the supply pressure as needed for various circuits.Check valves are one-way valves, allowing an accumulator to charge and maintain its pressure after the machine is turned off, for example.Counterbalance valves are in fact a special type of pilot controlled check valve. Whereas the check valve is open or closed, the counterbalance valve acts a bit like a pilot controlled flow control.Hydraulic pump typesGear pumpsGear pumps (with external teeth) (fixed displacement) are simple and economical pumps. The swept volume or displacement of gear pumps for hydraulics will be between about 1 cm3(0.001 litre) and 200 cm3(0.2 litre). These pumps create pressure through the meshing of the gear teeth, which forces fluid around the gears to pressurize the outlet side. Some gear pumps can be quite noisy, compared to other types, but modern gear pumps are highly reliable and much quieter than older models.Rotary vane pumpsRotary vane pumps (fixed and simple adjustable displacement) have higher efficiencies than gear pumps, but are also used for mid pressures up to 180 bars in general. Some types of vane pumps can change the centre of the vane body, so that a simple adjustable pump is obtained. These adjustable vane pumps are in general constant pressure or constant power pumps: the displacement is increased until the required pressure or power is reached and subsequently the displacement or swept volume is decreased until an equilibrium is reached.Screw pumpsScrew pumps (fixed displacement) are a double Archimedes' screw, but closed. This means that two screws are used in one body. The pumps are used for high flows and relatively low pressure (max 100 bar). They were used on board ships where the constant pressure hydraulic system was going through the whole ship, especially for the control of ball valves, but also for the steering gear and help drive systems. The advantage of the screw pumps is the low sound level of these pumps; the efficiency is not that high.Bent axis pumpsBent axis pumps, axial piston pumps and motors using the bent axis principle, fixed or adjustable displacement, exists in two different basic designs. The Thoma-principle (engineer Hans Thoma, Germany, patent 1935) with max 25 degrees angle and the Wahlmark-principle (GunnarAxel Wahlmark, patent 1960) with spherical-shaped pistons in one piece with the piston rod, piston rings, and maximum 40 degrees between the driveshaft centerline and pistons (V olvo Hydraulics Co.). These have the best efficiency of all pumps. Although in general the largest displacements are approximately one litre per revolution, if necessary a two-liter swept volume pump can be built. Often variable-displacement pumps are used, so that the oil flow can be adjusted carefully. These pumps can in general work with a working pressure of up to 350–420 bars in continuous work.Axial piston pumps swashplate principleAxial piston pumps using the swashplate principle (fixed and adjustable displacement) have a quality that is almost the same as the bent axis model. They have the advantage of being more compact in design. The pumps are easier and more economical to manufacture; the disadvantage is that they are more sensitive to oil contamination.Radial piston pumpsRadial piston pumps (fixed displacement) are used especially for high pressure and relatively small flows. Pressures of up to 650 bar are normal. In fact variable displacement is not possible, but sometimes the pump is designed in such a way that the plungers can be switched off one by one, so that a sort of variable displacement pump is obtained.Peristaltic pumpsPeristaltic pumps are not generally used for high pressures.Pumps for open and closed systemsMost pumps are working in open systems. The pump draws oil from a reservoir at atmospheric pressure. It is very important that there is no cavitation at the suction side of the pump. For this reason the connection of the suction side of the pump is larger in diameter than the connection of the pressure side. In case of the use of multi-pump assemblies, the suction connection of the pump is often combined. It is preferred to have free flow to the pump (pressure at inlet of pump at least 0.8 bars). The body of the pump is often in open connection with the suction side of the pump.In case of a closed system, both sides of the pump can be at high pressure. The reservoir is often pressurized with 6-20 bars boost pressure. For closed loop systems, normally axial piston pumps are used. Because both sides are pressurized, the body of the pump needs a separate leakage connection.Multi pump assemblyIn a hydraulic installation, one pump can serve more cylinders and motors. The problem however is that in that case a constant pressure system is required and the system always needs the full power. It is more economic to give each cylinder and motor its own pump. In that case multi pump assemblies can be used. Gearpumps can often be obtained as multi pumps.The different chambers (sometimes of different size) are mounted in one body or built together. Also vane pumps can often be obtained as a multi pump. Gerotor pumps are often supplied as multi pumps. Screw pumps can be built together with a gear pump or a vane pump. Axial piston swashplate pumps can be built together with a second pump of the same or smaller size, or can be built together with one or more gear pumps or vane pumps (depending on the supplier). Axial plunger pumps of the bent axis design can not be built together with other pumps.翻译：液压机械及泵液压机械是机械和工具,它使用流体的力量去做的工作。

液压传动和传动油外文文献翻译、中英文翻译、外文翻译

fluid driven and transmission oilFormer statement fluid transmission is including gas (pressure) transmission and liquid transmission, hydraulic transmission into liquid transmission, hydraulic transmission and fluid Nien transmission. Hydraulic transmission based on the interior market, the pressure to be able to impart impetus liquid; Hydraulic transmission based on Oula equation to the liquid changes to the short wheel drive transmission; For Newton, Nien transmission fluid friction law, the sticky liquid to impart dynamism to.Hydraulic transmission is the basic hydraulic components and hydraulic Bianjuqi coupled device. Hydraulic coupled devices is a fundamental component of a number of radial plane leaves, a work of the pump and turbine round. Hydraulic transmission oil in the work of the cycle of high-speed mobile transmission power, oil pumps round her so involved with the campaign because centrifugal force role do centrifuge campaign from pumps round (and imported axis) and to absorb mechanical energy into moment of momentum (mVR) incremental, high-speed Yeliu round water from the pump to the heart to do turbine flow release moment of momentum. promote turbine (and export axis) rotation, work-driven plane (and load) homework. Hydraulic Bianjuqi basic components are pumps round, and the turbine-round, they are a space (bending) leaves work round by the work of a relevant order. Hydraulic transmission oil pumps were working round the turbine mix for incremental Ye Liu was moment of momentum, after transfer-round water turbine Yeliu direction after the release of moment of momentum (kinetic energy) to promote the work of the turbine-driven rotary rush.My hydraulic components in the development of faster, 2003 hydraulic coupled devices produced about 70,000 National Taiwan. Widely used for Daishishusongji, rail carriers, ball mill, air-compressors, compressors, pumps and fuel pumps, and other equipment, transmission, improve transmission quality and energy conservation. My hydrauliccoupled with the current maximum output rotational speed for 6500r/min, minimum power to 0.3kW, the maximum power to 7100kW. Hydraulic trend is coupled with a high rotational speed and power.International hydraulic coupled device products to the most famous German Fuk under special company, according to information that has reached 20000r/min rotational speed and power to 55000kW products, which are still visible in considerable gap. Of course, the power of the big oil hydraulic components for hydraulic transmission requirements higher. Hydraulic Bianjuqi mainly for engineering machinery, machinery and diesel oil. Hydraulic Bianjuqi main internal combustion engine with matching applications, the scope of its rotational speed in 2000~3000r/min. Mechanical engineering applications more, the greatest power 700HP about output about 70,000 Taiwan. Oil machinery applications less power to 1500HP. Diesel applications less power up 3000HP.Nien transmission fluid is a liquid transmission doors emerging disciplines in the country are still at an infancy stage. Because liquid Nien transmission products (such as fluid mechanics using Nien) and hydraulic transmission products (such as governor-hydraulic coupled device) Notwithstanding the different nature, but because of similar performance and the same purposes (governor energy), in a number of technical activities (such as the formulation of development plans, standards, technology management, orders, and other activities) are regarded as the same type, with the hydraulic industry commonalities, it is another chapter on the work of its product mix and transmission oil.First, the performance characteristics of the oil and hydraulic transmission hydraulic transmission oil development not only as a transmission medium for work, but also to provide lubrication bearings and gear while the carrier is further bad fever, heat away. Hydraulic transmission oil is a complex and require specialized research topics, which is directly related to the reliability of hydraulic components,transmission efficiency and service life. Should arouse the attention of extensive in-depth study.Hydraulic transmission oil should meet the following requirements : 1、A suitable low-viscosity liquid viscosity, liquid indicate friction within small, mobile resistance small loss may reduce hydraulic components hydraulic losses; But lubricant sealed perspective, the viscosity can not be too low. Provide lubrication and therefore should meet the requirements of sealed premise as a low-viscosity liquid to improve hydraulic components transmission efficiency. Wen Xing Nien also called liquid than for the high-temperature or low-temperature, and still maintain an effective lubricant sealed.2、A greater emphasis on the hydraulic components for the moment and the power transmission and liquid working for the re-direct, it is liquid-degrees the higher the better.3、The performance can have a stable bubble, aging and sedimentation.4、Suanzhi sealed pieces to be neutral to low, and a good compatibility, not dwell inflation, not dissolved, the non-corrosive metal.5、A higher flash point and lower congeal point hydraulic components work Youwen change significantly, sometimes up to 160 degrees, and therefore require flash point higher than 180 degrees, and congeal point lower than -20 degrees, low-temperature environment for the benefit of the start-up of hydraulic components.6、A good lubricant performance liquid sufficient greasiness to the good parts in the surface material, a good lubricant.At present, and hydraulic transmission applications work more liquid types, among all oil-based products, has used the water or other liquid Nanran (coal mine explosion and fire in defense applications). Domestic hydraulic components commonly used 6th hydraulic transmission oil (also useful 8th hydraulic transmission oil), and sometimes to 22 turbine fuel substitution.Diesel oil is dedicated to the life of not less than 2,000 hours andfor the initial operation of new equipment installed oil after 100 hours and 500 hours of the first, second formula, can still be used after the filter.Is one of the following situations, the need to replace the new oil : Water content greater than 0.2%; 50 degrees in the new oil viscosity higher than 6% mounted; Mechanical impurities (benzene Burong objects) to reach 0.2%; A high lipid intake or Suanzhi; Excessive bubble effects transmission power. More articles on the diesel-hydraulic transmission oil outside the oil will definitely reference value.Second, Transmission and hydraulic oil brands in (slightly)Third, Fluid Nien transmission of the oil transmission fluid requirements may Nien Tien National Petroleum Corporation December thickness operational changes are divided into two categories : one category is in operation slick thickness constant fluid Nien transmission, such as silicone oil slick thickness using fans is fixed, changes in the operational work of the degree to which oil-exporting rotational speed. Another operation is slick thickness is variable fluid Nien transmission, such fluid Nien Nien transmission products including fluid mechanics using, liquid Nien brakes, fluids Nien dynamometer, fluid Nien shaft coupling, fluid mechanics Nien devices. Current applications are more fluid mechanics using Nien, fluid mechanics devices and silicone oil Nien fans Clutch.1、Fluid mechanics using Nien and transmission oil fluid mechanics using Nien through its owners, driven friction between the film to a number of oil transmission power, relying on the apparent effectiveness initiative friction films "draw" driven friction with the direction of rotation films, transmission moment with oil viscosity, two films - "goes bad" proportional, and with oil thickness (films gap) negatively. Initiative friction films and imported axle and power machine linked to the importation of rotational speed as constants. Driven friction films and the work associated with the export of axle, and the output rotational speed with control pressure changes, spherical tank pressure control, a slick filmthinning, export rotational speed rise, and vice versa. When the control pressure enough, the owners, driven friction films together into the transmission straight. When sufficient pressure control small owners, driven films from friction, zero export rotational speed. Nien in fluid mechanics using rotational speed than 0>1 change from the process of film-friction conditions showing a liquid friction "(a mechanical liquid) mixed friction" (purely mechanical) border friction. Therefore fluid mechanics using Nien are in the process of separation-state governor, the state governor and the state face. Work in fluid liquid is the role of transmission Nien transmission power, heat dissipation and cooling lubricant should have the following functions : (1) the appropriate viscosity. (2) is a good lubricant performance (greasiness and very pressurised nature). (3) a good oxidation insecurities. (4) higher than the thermal capacity and higher heat conductivity. In addition to the above requirements, but also work with rustproof liquid role, anti-bubble capacity, congeal points lower, flash point should be high, not volatile, non-toxic. Nien currently made in China fluid mechanics using more oil as a hydraulic transmission work on the 8th of liquid. The domestic fluid mechanics using a TL - Nien and HC type rated rotational speed mostly 1500r/min, individual 3000r/min. 75kW power transmission smallest, the largest of 1100kW. Fluid mechanics starts with the mechanics of hydraulic Nien coupled devices, are in the rotational speed electrical driven downward in the low-speed, power and small, inefficient. To this end in fluid mechanics using input Nien before or after the installation of vertical transmission-export, or to meet with the power machine and the matching machine work, so a new device -- liquid Nien governor devices.2、Fluid mechanics devices Nien current production and application of two different structures liquid Nien governor devices, a category is the U.S. Philadelphia drove parallel axle fluid production company Nien governor devices into rotational speed 1785r/min exporting rotational speed 5000r/min, transmitting power to 5200kW. My hill Xian too Salihcoal mine in the smaller Daishishusongji specifications. Oil is brought by the United States of its transmission. Baoding propeller factory design, produced with structurally similar products. Another is the United States Dodge (Dodge) companies CST fluid mechanics devices Nien, it is in Park pillar gear -- planetary reducer round of the robustness of the export-round, and export axis (connecting the Sun round), in parallel with export large Chijuan fluid mechanics using Nien (driven friction films fixed), start-up liquid separation Nien governor in the state starts (idling), gradually increasing pressure control, when his transmission torque and the torque equivalent output bearings, export axle (with load) started turning and continue to increase the pressure until the joint control of the situation, the export axle assume full power output. CST fluid mechanics device known as Nien large Daishishusongji soft start system in the country's major coal Daishishusongji already applied. CST series products, the importation of rotational speed 1483r/min, rated slowdown than to 15.38~57.66, transmitting power scope 702~3115kW. CST series of products supplied by the United States dedicated hydraulic transmission oil.3、Silicone oil producing fans with liquid silicone oil work of the fan clutch, driven plate with a 78-98 derby leaves, the two derby leaves mutual alternate inserted, a number Park derby gap (oil), use these links, the sticky oil to impart momentum. The process of routing thickness unchanged through changes Chongyou volume and the size of the area to exploration by sheared governor.Engine in the appropriate temperature can be higher fuel efficiency, overheating is not too cold. Automotive firm to offer fans of silicone oil and engine linked driven sites linked with the fans, for liquid silicone oil viscosity larger. On temperature devices for cooling water to control the rear airflow temperature feelings Chongyou volume. When the engine cooling water temperature low, the air currents temperature low temperature equipment made Chongyou small amount of oil shearedsmall size, transmission moment small, low rotational speed fans for the engine cooling capacity low. Conversely, when the engine cooling water temperature is high, the fans rotational speed is high, awareness of the engine cooling effect. This will allow a regular in the most appropriate temperature. Fuel efficiency, noise small, extended engine life.Silicone oil used silicone oil is a fan using synthetic lubricants, not petroleum refining come from. It is the semi-organic silicon polymers or copolymer, containing duplicate silicon modules for yuan oxygen machine backbone, and the silicon atoms along the chain, replace clustering levonorgestrel, the general chain-guns. To meet the prescribed performance requirements, availability of different organic polymers to replace the base elements or the size of the adjustment (that is, to change its molecular weight), to change its viscosity or acquire other properties.Silicone oil depends on the physical properties of polymer molecular structure, such as molecular weight, organic genetic types and quantity, location and length of extension chain. In the liquid oil thickness constant use silicone oil Nien transmission of the main reasons is that it has a high viscosity, good performance and strong resistance Nien Wen sheared capacity.Silicone oil can be used in all types of vehicles using fans, currently our applications are mainly jeeps, and other vehicles Beijing 130. Motor oil production plant with Beijing and Changchun First Automobile Works Bengchang units.液压传动和传动油流体传动包括气体(压)传动和液体传动，液体传动分为液压传动、液力传动和液粘传动。

液压系统外文文献翻译、中英文翻译、外文文献翻译

附录Hydraulic SystemHydraulic presser drive and air pressure drive hydraulic fluid as the transmission is made according to the 17th century, Pascal's principle of hydrostatic pressure to drive the development of an emerging technology, the United Kingdom in 1795 •Barman Joseph (Joseph Barman, 1749-1814), in London water as a medium to form hydraulic press used in industry, the birth of the world's first hydraulic press. Media work in 1905 will be replaced by oil-water and further improved.After the World War I (1914-1918) ,because of the extensive application of hydraulic transmission, especially after 1920, more rapid development. Hydraulic components in the late 19th century about the early 20th century, 20 years, only started to enter the formal phase of industrial production. 1925 Vickers (F. Vickers) the invention of the pressure balanced vane pump, hydraulic components for the modern industrial or hydraulic transmission of the gradual establishment of the foundation. The early 20th century G • Constantia scofluctuations of the energy carried out by passing theoretical and practical research; in 1910 on the hydraulic trans- mission (hydraulic coupling, hydraulic torque converter, etc.) contributions, so that these two areas of development.The Second World War (1941-1945) period, in the United States 30% of machine tool applications in the hydraulic transmission. It should be noted that the development of hydraulic transmission in Japan than Europe and the United States and other countries fornearly 20 years later. Before and after in 1955, the rapid development of Japan's hydraulic drive, set up in 1956, "Hydraulic Industry." Nearly 20 to 30 years, the development of Japan's fast hydraulic transmission, a world leader.Hydraulic transmission There are many outstanding advantages, it is widely used, such as general industrial use of plastics processing machinery, the pressure of machinery, machine tools, etc.; operating machinery engineering machinery, construction machinery, agricultural machinery, automobiles, etc.; iron and steel industry metallurgical machinery, lifting equipment, such as roller adjustment device; civil water projects with flood control and dam gate devices, bed lifts installations, bridges and other manipulation of institutions; speed turbine power plant installations, nuclear power plants, etc.; ship from the deck heavy machinery (winch), the bow doors, bulkhead valve, stern thruster, etc.; special antenna technology giant with control devices, measurement buoys, movements such as rotating stage; military-industrial control devices used in artillery, ship anti- rolling devices, aircraft simulation, aircraft retractable landing gear and rudder control devices and other devices.A complete hydraulic system consists of five parts, namely, power components, the implementation of components, control components, auxiliary components and hydraulic oil.The role of dynamic components of the original motive fluid into mechanical energy to the pressure that the hydraulic system of pumps, it is to power the entire hydraulic system. The structure of the form of hydra- ulic pump gears are generally pump, vane pump and piston pump.Implementation of components (such as hydraulic cylinders and hydraulic motors) which isthe pressure of the liquid can be converted to mechanical energy to drive the load for a straight line reciprocating movement or rotational movement.Control components (that is, the various hydraulic valves) in the hydraulic system to control and regulate the pressure of liquid, flow rate and direction. According to the different control functions, hydraulic pressure control valve can be divided into valves, flow control valves and directional control valve. Pressure control valves are divided into benefits flow valve (safety valve), pressure relief valve, sequence valve, pressure relays, etc.; flow control valves including throttle, adjusting the valves, flow diversion valve sets, etc.; directional control valve includes a one-way valve , one-way fluid control valve, shuttle valve, valve and so on. Under the control of different ways, can be divided into the hydraulic valve control switch valve, control valve and set the value of the ratio control valve.Auxiliary components, including fuel tanks, oil filters, tubing and pipe joints, seals, pressure gauge, oil level, such as oil dollars.Hydraulic oil in the hydraulic system is the work of the energy transfer medium, there are a variety of mineral oil, emulsion oil hydraulic molding Hop categories.The role of the hydraulic system is to help humanity work. Mainly by the implementation of components to rotate or pressure into a reciprocating motion.Hydraulic system and hydraulic power control signal is composed of two parts, the signal control of some parts of the hydraulic power used to drive the control valve movement.Part of the hydraulic power means that the circuit diagram used to show the differentfunctions of the interrelationship between components. Containing the source of hydraulic pump, hydraulic motor and auxiliary components; hydraulic control part contains a variety of control valves, used to control the flow of oil, pressure and direction; operative or hydraulic cylinder with hydraulic motors, according to the actual requirements of their choice.In the analysis and design of the actual task, the general block diagram shows the actual operation of equipment. Hollow arrow indicates the signal flow, while the solid arrows that energy flow.Basic hydraulic circuit of the action sequence - Control components (two four-way valve) and the spring to reset for the implementation of components (double-acting hydraulic cylinder), as well as the extending and retracting the relief valve opened and closed. For the implementation of components and control components, presentations are based on the corresponding circuit diagram symbols, it also introduced ready made circuit diagram symbols.Working principle of the system, you can turn on all circuits to code. If the first implementation of components numbered 0, the control components associated with the identifier is 1. Out with the implementation of components corresponding to the identifier for the even components, then retracting and implementation of components corresponding to the identifier for the odd components. Hydraulic circuit carried out not only to deal with numbers, but also to deal with the actual device ID, in order to detect system failures.DIN ISO1219-2 standard definition of the number of component composition, which includes the following four parts: device ID, circuit ID, component ID and component ID.The entire system if only one device, device number may be omitted.Practice, another way is to code all of the hydraulic system components for numbers at this time, components and component code should be consistent with the list of numbers. This method is particularly applicable to complex hydraulic control system, each control loop are the corresponding number with the systemWith mechanical transmission, electrical transmission compared to the hydraulic drive has the following advantages:1. a variety of hydraulic components can easily and flexibly to layout.2. light weight, small size, small inertia, fast response.3. to facilitate manipulation of control, enabling a wide range of stepless speed regulation (speed range of 2000:1).4. to achieve overload protection automatically.5. the general use of mineral oil as a working medium, the relative motion can be self-lubricating surface, long service life;6. it is easy to achieve linear motion .7. it is easy to achieve the automation of machines, when the joint control of the use of electro-hydraulic, not only can achieve a higher degree of process automation, and remote control can be achieved.The shortcomings of the hydraulic system:1. as a result of the resistance to fluid flow and leakage of the larger, so less efficient. If not handled properly, leakage is not only contaminated sites, but also may cause fire and explosion.2. vulnerable performance as a result of the impact of temperature change, it would be inappropriate in the high or low temperature conditions.3. the manufacture of precision hydraulic components require a higher, more expensive and hence the price.4. due to the leakage of liquid medium and the compressibility and can not be strictly the transmission ratio.5. hydraulic transmission is not easy to find out the reasons for failure; the use and maintenance requirements for a higher level of technology.In the hydraulic system and its system, the sealing device to prevent leakage of the work of media within and outside the dust and the intrusion of foreign bodies. Seals played the role of components, namely seals. Medium will result in leakage of waste, pollution and environmental machinery and even give rise to malfunctioning machinery and equipment for personal accident. Leakage within the hydraulic system will cause a sharp drop in volumetric efficiency, amounting to less than the required pressure, can not even work. Micro-invasive system of dust particles, can cause or exacerbate friction hydraulic component wear, and further lead to leakage.Therefore, seals and sealing device is an important hydraulic equipment components. The reliability of its work and life, is a measure of the hydraulic system an important indicator of good or bad. In addition to the closed space, are the use of seals, so that two adjacent coupling surface of the gap between the need to control the liquid can be sealed following the smallest gap. In the contact seal, pressed into self-seal-style and self-styled self-tight seal (ie, sealed lips) two.The three hydraulic system diseases1. as a result of heat transmission medium (hydraulic oil) in the flow velocity in various parts of the existence of different, resulting in the existence of a liquid within the internal friction of liquids and pipelines at the same time there is friction between the inner wall, which are a result of hydraulic the reasons for the oil temperature. Temperature will lead to increased internal and external leakage, reducing its mechanical efficiency. At the same time as a result of high temperature, hydraulic oil expansion will occur, resulting in increased com- pression, so that action can not be very good control of transmission. Solution: heat is the inherent characteristics of the hydraulic system, not only to minimize eradication. Use a good quality hydraulic oil, hydraulic piping arrangement should be avoided as far as possible the emergence of bend, the use of high-quality pipe and fittings, hydraulic valves, etc.2. the vibration of the vibration of the hydraulic system is also one of its malaise. As a result of hydraulic oil in the pipeline flow of high-speed impact and the control valve to open the closure of the impact of the process are the reasons for the vibration system. Strong vibration control action will cause the system to error, the system will also be some of the more sophisticated equipment error, resulting in system failures. Solutions: hydraulic pipe should be fixed to avoid sharp bends. To avoid frequent changes in flow direction, can not avoid damping measures should be doing a good job. The entire hydraulic system should have a good damping measures, while avoiding the external local oscillator on the system.3. the leakage of the hydraulic system leak into inside and outside the leakage. Leakagerefers to the process with the leak occurred in the system, such as hydraulic piston-cylinder on both sides of the leakage, the control valve spool and valve body, such as between the leakage. Although no internal leakage of hydra- ulic fluid loss, but due to leakage, the control of the established movements may be affected until the cause system failures. Outside means the occurrence of leakage in the system and the leakage between the external environment. Direct leakage of hydraulic oil into the environment, in addition to the system will affect the working environment, not enough pressure will cause the system to trigger a fault. Leakage into the environment of the hydraulic oil was also the danger of fire. Solution: the use of better quality seals to improve the machining accuracy of equipment.Another: the hydraulic system for the three diseases, it was summed up: "fever, with a father拉稀" (This is the summary of the northeast people). Hydraulic system for the lifts, excavators, pumping station, dynamic, crane, and so on large-scale industry, construction, factories, enterprises, as well as elevators, lifting platforms, Deng Axle industry and so on.Hydraulic components will be high-performance, high-quality, high reliability, the system sets the direction of development; to the low power, low noise, vibration, without leakage, as well as pollution control, water-based media applications to adapt to environmental requirements, such as the direction of development; the development of highly integrated high power density, intelligence, macaronis and micro-light mini-hydraulic components; active use of new techniques, new materials and electronics, sensing and other high-tech.---- Hydraulic coupling to high-speed high-power and integrated development of hydraulic transmission equipment, development of water hydraulic coupling medium speedand the field of automotive applications to develop hydraulic reducer, improve product reliability and working hours MTBF; hydraulic torque converter to the development of high-power products, parts and components to improve the manufacturing process technology to improve reliability, promote computer-aided technology, the development of hydraulic torque converter and power shift transmission technology supporting the use of ; Clutch fluid viscosity should increase the quality of products, the formation of bulk to the high-power and high-speed direction.Pneumatic Industry:---- Products to small size, light weight, low power consumption, integrated portfolio of development, the implementation of the various types of components, compact structure, high positioning accuracy of the direction of development; pneumatic components and electronic technology, to the intelligent direction of development; component performance to high-speed, high-frequency, high-response, high-life, high temp- erature, high voltage direction, commonly used oil-free lubrication, application of new technology, new technology and new materials.1. Used high-pressure hydraulic components and the pressure of continuous work to reach 40Mpa, the maximum pressure to achieve instant 48Mpa;2. Diversification of regulation and control;3. To further improve the regulation performance, increase the efficiency of the power train;4. Development and mechanical, hydraulic, power transmission of the composite portfolio adjustment gear;5. Development of energy saving, energy efficient system function;6. To further reduce the noise;7. Application of Hydraulic Cartridge Valves thread technology, compact structure, to reduce the oil spill.液压系统液压传动和气压传动称为流体传动，是根据17世纪帕斯卡提出的液体静压力传动原理而发展起来的一门新兴技术，1795年英国约瑟夫•布拉曼(Joseph Braman,1749-1814)，在伦敦用水作为工作介质，以水压机的形式将其应用于工业上，诞生了世界上第一台水压机。

液压系统外文文献翻译中英文

外文文献翻译(含：英文原文及中文译文)英文原文Hydraulic systemW Arnold1 IntroductionThe hydraulic station is called a hydraulic pump station and is an independent hydraulic device. It is step by step to supply oil. And control the direction of hydraulic oil flow, pressure and flow, suitable for the host and hydraulic equipment can be separated on the various hydraulic machinery.After the purchase, the user only needs to connect the hydraulic station and the actuator (hydraulic or oil motor) on the mainframe with different tubings. The hydraulic machine can realize various specified actions and working cycles.The hydraulic station is a combination of manifolds, pump units or valve assemblies, electrical boxes, and tank electrical boxes. Each part function is:The pump unit is equipped with a motor and an oil pump, which is the power source of the hydraulic station and can convert mechanical energy into hydraulic oil pressure energy.V alve combination - its plate valve is mounted on the vertical plate, and the rear plate is connected with the same function as the manifold.Oil manifolds - assembled from hydraulic valves and channel bodies. It regulates hydraulic oil pressure, direction and flow.Box--a semi-closed container for plate welding. It is also equipped with an oil screen, an air filter, etc., which is used for cooling and filtering of oil and oil.Electrical box - divided into two types: one is to set the external lead terminal board; one is equipped with a full set of control appliances.The working principle of the hydraulic station: The motor drives the oil pump to rotate, then the pump sucks oil from the oil tank and supplies oil, converts the mechanical energy into hydraulic pressure energy, and the hydraulic oil passes through the manifold (or valve assembly) to adjust the direction, pressure and flow and then passes through the external tube. The way to the hydraulic cylinder or oil motor in the hydraulic machinery, so as to control the direction of the hydraulic motor, the strength of the speed and speed, to promote all kinds of hydraulic machinery to do work.(1) Development history of hydraulic pressureThe development history of hydraulics (including hydraulic power, the same below), pneumatics, and seals industry in China can be roughly divided into three stages, namely: the starting stage in the early 1950s to the early 60s; and the professional in the 60s and 70s. The growth stage of the production system; the 80-90's is a stage of rapid development. Among them, the hydraulic industry began in the early 1950s with thedevelopment of hydraulic machines such as Grinding Machines, broaching machines, and profiling lathes, which were produced by the machine tool industry. The hydraulic components were produced by the hydraulic workshop in the machine tool factory, and were produced for self use. After entering the 1960s, the application of hydraulic technology was gradually promoted from the machine tool to the agricultural machinery and engineering machinery. The original hydraulic workshop attached to the main engine plant was independent and became a professional manufacturer of hydraulic components. In the late 1960s and early 1970s, with the continuous development of mechanization of production, particularly in the provision of highly efficient and automated equipment for the second automobile manufacturing plant, the hydraulic component manufacturing industry witnessed rapid development. The batch of small and medium-sized enterprises also began to become specialized manufacturers of hydraulic parts. In 1968, the annual output of hydraulic components in China was close to 200,000 pieces. In 1973, in the fields of machine tools, agricultural machinery, construction machinery and other industries, the professional factory for the production of hydraulic parts has grown to over 100, and its annual output exceeds 1 million pieces. Such an independent hydraulic component manufacturing industry has taken shape. At this time, the hydraulic product has evolved from the original imitation Su product intoa combination of imported technology and self-designed products. The pressure has been developed towards medium and high pressures, and electro-hydraulic servo valves and systems have been developed. The application of hydraulics has been further expanded. The pneumatic industry started a few years later than hydraulics, and it was only in 1967 that it began to establish a professional pneumatic components factory. Pneumatic components began to be manufactured and sold as commodities. Its sealing industry including rubber seals, flexible graphite seals, and mechanical seals started from the production of common O-rings, oil seals, and other extruded rubber seals and asbestos seal products in the early 1950s. In the early 1960s, it began to develop and produce flexible products. Graphite seals and mechanical seals and other products. In the 1970s, a batch of batches of professional production plants began to be established one after another in the systems of the former Ministry of Combustion, the Ministry of Agriculture, and the Ministry of Agricultural Machinery, formally forming the industry, which laid the foundation for the development of the seal industry.In the 1980s, under the guidance of the national policy of reform and opening up, with the continuous development of the machinery industry, the contradiction between the basic components lags behind the host computer has become increasingly prominent and caused the attention of all relevant departments. To this end, the former Ministry of Machinesestablished the General Infrastructure Industry Bureau in 1982, and unified the original pneumatic, hydraulic, and seal specialties that were scattered in the industries of machine tools, agricultural machinery, and construction machinery, etc. The management of a piece of office, so that the industry in the planning, investment, the introduction of technology and scientific research and development and other aspects of the basic parts of the bureau's guidance and support. This has entered a period of rapid development, it has introduced more than 60 foreign advanced technology, of which more than 40 hydraulic, pneumatic 7, after digestion and absorption and technological transformation, are now mass production, and has become the industry's leading products . In recent years, the industry has intensified its technological transformation. From 1991 to 1998, the total investment of national, local, and corporate self-raised funds totaled about 2 billion yuan, of which more than 1.6 billion were hydraulic. After continuous technological transformation and technological breakthroughs, the technical level of a group of major enterprises has been further improved, and technological equipment has also been greatly improved, laying a good foundation for forming a high starting point, specialization, and mass production. In recent years, under the guidance of the principle of common development of multiple ownership systems in the country, various small and medium-sized enterprises with different ownership have rapidly emerged and haveshown great vitality. With the further opening up of the country, foreign-funded enterprises have developed rapidly, which plays an important role in raising industry standards and expanding exports. So far China has established joint ventures with famous manufacturers in the United States, Germany, Japan and other countries or directly established piston pumps/motors, planetary speed reducers, hydraulic control valves, steering gears, hydraulic systems, hydrostatic transmissions, and hydraulic components. The company has more than 50 manufacturing enterprises such as castings, pneumatic control valves, cylinders, gas processing triplets, rubber seals, and mechanical seals, and has attracted more than 200 million U.S. dollars in foreign capital.(2) Current statusBasic profileAfter more than 40 years of hard work, China's hydraulics, pneumatics and seals industry has formed a complete industrial system with a certain level of production capacity and technical level. According to the statistics of the third n ational industrial census in 1995, China’s state-owned, privately-owned, cooperative, village-run, individual, and “funded enterprises” have annual sales income of more than 1 million yuan in hydraulic, pneumatic, and seal industrial townships and above. There are a total of more than 1,300 companies, including about 700 hydraulics, and about 300 pneumatic and sealing parts. According to thestatistics of the international industry in 1996, the total output value of the hydraulic industry in China was about 2.448 billion yuan, accounting for the 6th in the world; the total output value of the pneumatic industry was about 419 million yuan, accounting for the world’s10 people.2. Current supply and demand profileWith the introduction of technology, independent development and technological transformation, the technical level of the first batch of high-pressure plunger pumps, vane pumps, gear pumps, general hydraulic valves, oil cylinders, oil-free pneumatic components and various types of seals has become remarkable. Improve, and can be stable mass production, provide guarantees for all types of host to improve product quality. In addition, certain achievements have also been made in the aspects of CAD, pollution control, and proportional servo technology for hydraulic pneumatic components and systems, and have been used for production. So far, the hydraulic, pneumatic and seal products have a total of about 3,000 varieties and more than 23,000 specifications. Among them, there are about 1,200 types of hydraulic pressure, more than 10,000 specifications (including 60 types of hydrodynamic products, 500 specifications); about 1350 types of pneumatic, more than 8,000 specifications; there are also 350 types of rubber seals, more than 5000 The specifications are now basically able to adapt to the general needs ofvarious types of mainframe products. The matching rate for major equipment sets can reach more than 60%, and a small amount of exports has started.In 1998, the domestic production of hydraulic components was 4.8 million pieces, with sales of about 2.8 billion yuan (of which mechanical systems accounted for 70%); output of pneumatic components was 3.6 million pieces, and sales were about 550 million yuan (including mechanical systems accounting for about 60%) The production of seals is about 800 million pieces, and the sales volume is about 1 billion yuan (including about 50% of mechanical systems). According to the statistics of the annual report of the China Hydraulic and Pneumatic Sealing Industry Association in 1998, the production and sales rate of hydraulic products was 97.5% (101% of hydraulic power), 95.9% of air pressure, and 98.7% of seal. This fully reflects the basic convergence of production and sales.Although China's hydraulic, pneumatic and sealing industries have made great progress, there are still many gaps compared with the development needs of the mainframe and the world's advanced level, which are mainly reflected in the variety, performance and reliability of products. . Take hydraulic products as an example, the product varieties are only 1/3 of the foreign country, and the life expectancy is 1/2 of that of foreign countries. In order to meet the needs of key hosts, imported hosts, and majortechnical equipment, China has a large number of imported hydraulic, pneumatic, and sealing products every year. According to customs statistics and relevant data analysis, in 1998, the import volume of hydraulic, pneumatic and seal products was about 200 million U.S. dollars, of which the hydraulic pressure was about 140 million U.S. dollars, the pneumatics were 30 million U.S. dollars, and the seal was about 0.3 billion U.S. dollars. The year is slightly lower. In terms of amount, the current domestic market share of imported products is about 30%. In 1998, the total demand for hydraulic parts in the domestic market was about 6 million pieces, and the total sales volume was 4 billion yuan; the total demand for pneumatic parts was about 5 million pieces, and the total sales volume was over 700 million yuan; the total demand for seals was about 1.1 billion yuan. Pieces, total sales of about 1.3 billion yuan. (3) Future developments1. The main factors affecting development(1) The company's product development capability is not strong, and the level and speed of technology development can not fully meet the current needs for advanced mainframe products, major technical equipment and imported equipment and maintenance;(2) Many companies have lagged behind in manufacturing process, equipment level and management level, and their sense of quality is not strong, resulting in low level of product performance, unstable quality,poor reliability, and insufficiency of service, and lack of user satisfaction. And trusted branded products;(3) The degree of professional specialization in the industry is low, the power is scattered, the duplication of the low level is serious, the product convergence between the region and the enterprise leads to blind competition, and the prices are reduced each other, thus the efficiency of the enterprise is reduced, the funds are lacking, and the turnover is difficult. Insufficient investment in development and technological transformation has severely restricted the overall level of the industry and its competitive strength.(4) When the degree of internationalization of the domestic market is increasing, foreign companies have gradually entered the Chinese market to participate in competition, coupled with the rise of domestic private, cooperative, foreign-funded, and individual enterprises, resulting in increasing impact on state-owned enterprises. .2. Development trendWith the continuous deepening of the socialist market economy, the relationship between supply and demand in the hydraulic, pneumatic and sealed products has undergone major changes. The seller market characterized by “shortage” has basically become a buyer’s market characterized by “structured surplus”. Replaced by. From the perspective of overall capacity, it is already in a trend of oversupply, and in particular,general low-grade hydraulic, pneumatic and seals are generally oversupply; and like high-tech products with high technological content and high value and high value-added products that are urgently needed by the host, Can not meet the needs of the market, can only rely on imports. After China's entry into the WTO, its impact may be greater. Therefore, during the “10th Five-Y ear Plan” period, the growth of the industry’s output value must not only rely on the growth of quantity. Instead, it should focus on the structural contradiction of the industry and intensify efforts to adjust the industrial structure and product structure. It should be based on the improvement of quality. Product technology upgrades in order to adapt to and stimulate market demand, and seek greater development.2. Hydraulic application on power slide(1) Introduction of Power Sliding TableUsing the binding force curve diagram and the state space analysis method to analyze and study the sliding effect and the smoothness of the sliding table of the combined machine tool, the dynamics of the hydraulic drive system of the sliding table—the self-regulating back pressure regulating system are established. mathematical model. Through the digital simulation system of the computer, the causes and main influencing factors of the slide impact and the motion instability are analyzed. What kind of conclusions can be drawn from those, if we canreasonably design the structural dimensions of hydraulic cylinders and self-regulating back pressure regulators ——The symbols used in the text are as follows:s 1 - flow source, that is, the flow rate of the governor valve outlet;S el —— sliding friction of the sliding table;R - the equivalent viscous friction coefficient of the slide;I 1 - quality of slides and cylinders;12 - self-adjusting back pressure valve core quality;C 1, c 2 - liquid volume without cylinder chamber and rod chamber;C 2 - Self-adjusting back pressure valve spring compliance;R 1, R2 - Self-adjusting back pressure valve damping orifice fluid resistance;R 9 - Self-adjusting back pressure valve valve fluid resistance;S e2——initial pre-tightening force of self-adjusting back pressure valve spring;I 4, I5 - Equivalent liquid sense of the pipeline;C 5, C 6 - equivalent liquid capacity of the pipeline;R 5, R7 - Equivalent liquid resistance of the pipeline;V 3, V4 - cylinder rodless cavity and rod cavity volume;P 3, P4—pressure of the rodless cavity and rod cavity of the cylinder;F - the slide bears the load;V - speed of slide motion;In this paper, the power bond diagram and the state space splitting method are used to establish the system's motion mathematical model, and the dynamic characteristics of the slide table can be significantly improved.In the normal operation of the combined machine tool, the magnitude of the speed of the slide, its direction and the load changes it undergoes will affect its performance in varying degrees. Especially in the process of work-in-process, the unsteady movement caused by the advancing of the load on the slide table and the cyclical change of the load will affect the surface quality of the workpiece to be machined. In severe cases, the tool will break. According to the requirements of the Dalian Machine Tool Plant, the author used the binding force curve diagram and the state space analysis method to establish a dynamic mathematical model of a self-adjusting back pressure and speed adjustment system for the new hydraulic drive system of the combined machine tool slide. In order to improve the dynamic characteristics of the sliding table, it is necessary to analyze the causes and main influencing factors of the impetus and movement of the sliding table. However, it must pass the computer's digital simulation and the final results obtained from the research.(2) Dynamic Mathematical ModelThe working principle diagram of the self-adjusting back pressure speedregulation system of the combined machine tool slide hydraulic drive system is shown in the figure. This system is used to complete the work-cycle-stop-rewind. When the sliding table is working, the three-position four-way reversing valve is in the illustrated position. The oil supply pressure of the oil pump will remain approximately constant under the effective action of the overflow valve, and the oil flow passes through the reversing valve and adjusts the speed. The valve enters the rodless chamber of the cylinder to push the slide forward. At the same time, the pressurized oil discharged from the rod chamber of the cylinder will flow back to the tank through the self-regulating back pressure valve and the reversing valve. During this process, there was no change in the operating status of both the one-way valve and the relief valve. The complex and nonlinear system of the hydraulic drive system of the self-adjusting back pressure governor system is a kind of self-adjusting back-pressure governor system. To facilitate the study of its dynamic characteristics, a simple and reasonable dynamic mathematical model that only considers the main influencing factors is established. Especially important [1][2]. From the theoretical analysis and the experimental study, we can see that the system process time is much longer than the process time of the speed control valve. When the effective pressure bearing area of the rodless cavity of the fuel tank is large, the flow rate at the outlet of the speed control valve is instantaneous. The overshoot is reflected in thesmall change in speed of the slide motion [2]. In order to further broaden and deeply study the dynamic characteristics of the system so that the research work can be effectively performed on a miniature computer, this article will further simplify the original model [2], assuming that the speed control valve is output during the entire system pass. When the flow is constant, this is considered to be the source of the flow. The schematic diagram of the dynamic model structure of this system is shown in Fig. 2. It consists of a cylinder, a sliding table, a self-adjusting back pressure valve, and a connecting pipe.The power bond graph is a power flow graph. It is based on the transmission mode of the system energy, based on the actual structure, and uses the centralized parameters to represent the role of the subsystems abstractly as a resistive element R, a perceptual element I, and a capacitive element. Three kinds of role of C. Using this method, the physical concept of modeling is clear, and combined with the state-space analysis method, the linear system can be described and analyzed more accurately. This method is an effective method to study the dynamic characteristics of complex nonlinear systems in the time domain. According to the main characteristics of each component of the self-adjusting back pressure control system and the modeling rules [1], the power bond diagram of the system is obtained. The upper half of each key in the figure represents the power flow. The two variables that makeup the power are the force variables (oil pressure P and force F) and the flow variables (flow q and velocity v). The O node indicates that the system is connected in parallel, and the force variables on each key are equal and the sum of the flow variables is zero; 1 The nodes represent the series connection in the system, the flow variables on each key are equal and the sum of the force variables is Zero. TF denotes a transformer between different energy forms. The TF subscripted letter represents the conversion ratio of the flow variable or the force variable. The short bar on the key indicates the causal relationship between the two variables on the key. The full arrow indicates the control relationship. There are integral or differential relationships between the force and flow variables of the capacitive and perceptual elements in the three types of action elements. Therefore, a complex nonlinear equation of state with nine state variables can be derived from Fig. 3 . In this paper, the research on the dynamic characteristics of the sliding table starts from the two aspects of the slide's hedging and the smoothness of the motion. The fourth-order fixed-length Runge-Kutta is used for digital simulation on the IBM-PC microcomputer.(3) Slide advanceThe swaying phenomenon of the slide table is caused by the sudden disappearance of the load acting on the slide table (such as drilling work conditions). In this process, the table load F, the moving speed V, and thepressure in the two chambers of the cylinder P3 and P4 can be seen from the simulation results in Fig. 4. When the sliding table moves at a uniform speed under the load, the oil pressure in the rodless cavity of the oil cylinder is high, and a large amount of energy is accumulated in the oil. When the load suddenly disappears, the oil pressure of the cavity is rapidly reduced, and the oil is rapidly reduced. When the high-pressure state is transferred to the low-pressure state, a lot of energy is released to the system, resulting in a high-speed forward impact of the slide. However, the front slide of the sliding table causes the pressure in the rod cavity of the oil cylinder to cause the back pressure to rise, thereby consuming part of the energy in the system, which has a certain effect on the kicking of the slide table. We should see that in the studied system, the inlet pressure of the self-adjusting back pressure valve is subject to the comprehensive effect of the two-chamber oil pressure of the oil cylinder. When the load suddenly disappears, the pressure of the self-adjusting back pressure valve rapidly rises and stably exceeds the initial back pressure value. It can be seen from the figure that self-adjusting back pressure in the speed control system when the load disappears, the back pressure of the cylinder rises more than the traditional speed control system, so the oil in the rod cavity of the cylinder absorbs more energy, resulting in the amount of forward momentum of the slide It will be about 20% smaller than traditionalspeed control systems. It can be seen from this that the use of self-adjusting back-gear speed control system as a drive system slider has good characteristics in suppressing the forward punch, in which the self-adjusting back pressure valve plays a very large role.(4) The smoothness of the slideWhen the load acting on the slide changes periodically (such as in the case of milling), the speed of the slide will have to fluctuate. In order to ensure the processing quality requirements, it must reduce its speed fluctuation range as much as possible. From the perspective of the convenience of the discussion of the problem, assume that the load changes according to a sine wave law, and the resulting digital simulation results are shown in Figure 5. From this we can see that this system has the same variation rules and very close numerical values as the conventional speed control system. The reason is that when the change of the load is not large, the pressure in the two chambers of the fuel tank will not have a large change, which will eventually lead to the self-regulating back pressure valve not showing its effect clearly.(5) Improvement measuresThe results of the research show that the dynamic performance of a sliding table with self-regulating back pressure control system as a drive system is better than that of a traditional speed control system. To reduce the amount of kick in the slide, it is necessary to rapidly increase the backpressure of the rod cavity when the load disappears. To increase the smoothness of the sliding table, it is necessary to increase the rigidity of the system. The main measure is to reduce the volume of oil. From the system structure, it is known that the cylinder has a large volume between the rod cavity and the oil discharge pipe, as shown in Fig. 6a. Its existence in terms of delay and attenuation of the self-regulating back pressure valve function, on the other hand, also reduces the rigidity of the system, it will limit the further improvement of the propulsion characteristics and the smoothness of the motion. Thus, improving the dynamic characteristics of the sliding table can be handled by two methods: changing the cylinder volume or changing the size of the self-regulating back pressure valve. Through the simulation calculation of the structural parameters of the system and the comparison of the results, it can be concluded that the ratio of the volume V4 between the rod cavity and the oil discharge pipe to the volume V3 between the rodless cavity and the oil inlet pipe is changed from 5.5 to 5.5. At 1 oclock, as shown in the figure, the diameter of the bottom end of the self-adjusting back pressure valve is increased from the original 10mm to 13mm, and the length of the damper triangle groove is reduced from the original lmm to 0.7mm, which will enable the front of the slide table. The impulse is reduced by 30%, the transition time is obviously shortened, and the smoothness of the slide motion will also be greatly improved.中文译文液压系统W Arnold1. 绪论液压站称液压泵站,是独立的液压装置。

液压马达外文文献翻译、中英文翻译

液压马达外文文献翻译、中英文翻译外文资料In recent years, the hydraulic motor with brachytely and big torsional moment has great changes, the new structure continuously appears. But, all these hydraulic motors can be divided into two broad categories of single and multi-role according to the role of the number of plunger in each turn. The motors also can be divided into radial and horizontal direction according to the arrangement of the plunger. And the radial motors can be divided into different types according to structure and the summon power way of the plunger.No matter single and multi-role, the plug-hole of radial-piston hydraulic motor is equated by circle, arrayed radial. The plunger displaced by the impulse of pressure oil, then the volume of the cylinder changed, the summon power formed the rotation of the motor, all of these above are the mechanism of action of the motors.The rotor of the single role hydraulic motor has a circle of rotation, each plunger worker once reciprocation. The principal axis is eccentric axis in all the radial-piston hydraulic motors. The multi-role hydraulic motor had a guide rail curve, whose numbers are the action times. The rotor had a circle of rotation, the plunger worker many times reciprocal at the same time. The radial motors can be divided into several categories of plunger, ball blocker, blade.The structure of the single-role motors is simpler, the machine element number of it is less, the technology is better, and the cost is less. But the structure dimension of the single-role motor is longer than the multi-role motor in the samedisplacement each turn (or output torsional moment), and the single-role motor also have fluctuation of the output torsional moment and rotary speed.The homonymyhigh-pressure column tune of the single-role motor had major radial unbalance force that causes the brachytely stabilization of the motor became worse. Only increasing the capacity of the bearing, it can meet the requirements of the operating life of the bearing at the same time.Generally speaking, the speed of single-role motors is higher than the multi-role in the same displacement because of the work feature of the single-role motors. The structure of the multi-role motors is complicated than single-role, the number of machine element is bigger as well. Some machine element needs some special equipment to process them. The heat treatment of the guide rail is more difficult. And the selection of the texture parameters in design is more difficult and harder. The cost is higher without a doubt.But the multi-role motor output larger torsional moment and had lighter weight of unit power in the same working pressure. The radial force of hydraulic motor can completely equilibrate and had higher started torsional moment efficiency as long as selecting the suitable plunger number and action number. In abstract the pulsation work of output torsional moment would be zero if one select guide rail curve reasonable and assign argument to the principle of non-pulsation in design. All of these can made it’s low speed stab ility better.People manufactured many new types of hydraulic motor in recent years. The structure of old motor refreshes and develops continuously. The motor’s life and pe rformance are raised but the cost is dropped as well. Various kinds of brachytely big torquehydraulic motors utilized more than 60 main frame extensively because theirstrong competitive ability.Multi-role within the curve of the radial piston hydraulic motor is divided into transmission plunger, beam transmission, wheel transmission .The most used are Beam transmission and Wheel Transmission motor .the france Crane Park motor produces the most ,the Rated working pressure is 30 MPa in all the Low Speed and High Torque motors Crane Park motor has the highest working pressure Recently , end assignment wheel motors is developed ,and the function was greatly improved . In recent years, Accompanied by Ball Cypriot Vice static and dynamic pressure bearing theory developed, Multi-role Radial ball plug Hydraulic Motor Developed quickly , such as Japan’s HMA series . Which are widely used in engineering and architecture. The hydraulic motor with brachytely and big torsional moment , commonly can be designed into Rotating shell or Axis rotation ,they are named shellmotor . shell motor that build in the Wheel rim is called Wheel motor ,which direct drive the wheels ,can replace the gear drive and make up the Hydraulic drive axle .In the 1970s , engineering Machine ,architecture Machine, mine Machine and Watercraft Deck Machine etc all use sap pressure technology .The element that advance the hydraulic motor with brachytely and big torsional moment has sharply increased to 40s . Variety species and main engine application has developedgreatly .but most for the main engine factory. Because losing the main knowledge of kinematic pair .The using were still remain in mapping ,imitation and Experience in analog designmanufacture were still in Groping .so although we have many Developers ,there are still no one hydraulic motor passed the appraisement . the hydraulic motor with brachytely and big torsional moment .However，Imitation and digestion of foreign products, can provides us a useful design and manufacturing experience. From 1974, Multi-role inner curve oil hydraulic motor Spot Turn NJM and Cranked shell model NKM etc were worked out and designed .There are some species in Spot Turn series , after experience according to JB 2148-77 standard and pass the qualification ,we can produce in quantity in fixed-point .In NJM hydraulic motor, guide rail is Sectional Type , according to discharge capacity, the succession has 16 discharge capacity species .this kind of motor has a good efficiency ,and the experiencing duration of life has exceeded 5000h.中文译文近年来，低速大扭矩液压马达有了较大的发展，新结构不断出现。

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中国地质大学长城学院本科毕业设计外文资料翻译系别工程技术系专业机械设计制造及其自动化学生姓名彭江鹤学号 05211534指导教师王泽河职称教授2015 年 5 月 4 日液压传动系统作者：Hopmans, ArthurH.摘要液压传动是由液压泵、液压控制阀、液压执行元件和液压辅件组成的液压系统。

液压泵把机械能转换成液体的压力能，液压控制阀和液压辅件控制液压介质的压力、流量和流动方向，将液压泵输出的压力能传给执行元件，执行元件将液体压力能转换为机械能，以完成要求的动作。

关键词：液压传动；气压传动；传动系统；许多液压传动先前已经设计出允许操作者无限变化输出的变速器，或甚至逆转的传动装置的输出作为相对于输入。

通常情况下，这已经通过使用一个旋转斜盘是要么由操作者手动或操作液压动机来改变通过旋转泵头部具有轴向移动的活塞流动的液压流体的。

液压流体从泵头活塞的流动，依次转动的马达头通过激励相应的一组活塞在其中违背一固定凸轮的，因此，旋转安装在电动机头的输出轴。

通常情况下，在现有技术的变速器已被被设置有各种功能，例如齿轮减速，刹车设定装置等。

不幸的是，这些功能通常是提供外部发送的和显著增加整个装置的体积和质量。

申请人确定，这是很期望具有其中基本上所有的这些需要或希望的功能，可以在内部提供的发送，同时还产生一个非常有效的和非常有效的传输的综合传输。

特别是，这种类型的变速器上经常使用的设备，如“零转动半径”剪草机之类的其中一个潜在的危险情况面对操作者，旁观者和设备本身，如果设备我们允许继续被推进应的操作者释放控制，由于当操作者无意中从装置抛出或变得受伤。

因此，“故障自动刹车”机制经常被设置为传输自动地返回到中立配置在这种情况下，使得该装置不会继续供电，如果控制被释放。

先前传输这种类型的一般依靠某种外部设备，比如其目的是为了在操作者控制轴返回到中立位置应操作者释放所述轴的反操作偏压弹簧。

这种类型的外部设备，可以容易地由用户或篡改损坏。

这种回归函数中性到传输本身的整合允许在外部零件的减少可被损坏或不适当取出并大大降低，以支持传输的各种功能所需的外部结构。

在这种类型的用于割草机的使用和类似的传输经常遇到的另一个问题是，操作时会略生涩或有弹性，因为操作者通常无法顺利地控制从一个速度到另一个的过渡，往往试图使突然变化。

从这些生涩的操作震动有一种倾向，穿更重的机器和操作上也是如此。

因此，理想的是抑制这种传输的输出，以防止这种不平稳的运动。

不仅是它是期望能够有一个返回到中立的功能，如desribed以上，但还希望为操作者有积极的感觉为中立位置时，不论操作者从空档移动到前进或从中立扭转。

此功能在本文中称为积极中性功能，并且在一般情况下，该功能需要操作者在从发送到任何一个正向或反向方向的中立姿势变换扩展更多的能量或运动相比，量能量消耗或运动需从一个速度转移到另一个在一个特定的方向。

与上面提到的其它特征，最好是需要提供此功能的结构的发送本身内掺入。

为了方便和简单起见，优选的是，发送直接从马达传动系接收电力而没有穿过齿轮减速装置。

不幸的是，大部分的输出要求是这样的，输出旋转速度必须大大降低相比，直接从马达所采取的输入转速。

因此，还希望该传输包含一个内部的齿轮减速系统允许大量减少输出速度比输入速度，即使当具有轴向移动的活塞驱动输出电动机的类型的液压传动装置的取向，以提供最大输出速度。

应注意的是，在一些比最大功率低输出速度时，几乎所有的可变输出传动装置本身提供的一些齿轮，由于一种或另一种电源旁路的减少，但没有已知的申请人的现有技术的变速器的提供大幅的内部的齿轮减速在全输出）。

某些使用这种类型的变速器的车辆包括制动器从而有效地防止车辆在电动机驱动的传输被停止移动。

这些制动器通常手动应用和要求的结构安装在车辆上的大量。

特别是，这种类型的驻车制动器通常包括：一个操作者的杠杆臂与相关联的键的杠杆臂连接到制动机构，这反过来，锁定驱动轮，传动轴或类似物。

再次，为了简化该结构和集成的制动功能到传输，它被认为是理想的申请人构建的发送，将有内部结构来自动接合驻车制动时的马达驱动的传送被停止。

虽然这种类型的驻车制动器是非常有利的，它也有必要提供一种具有倍率结构这将允许操作者选择性地覆盖制动这样的制动器;例如，当操作员希望对车辆推到不同的位置时，马达将无法启动。

此外，有利的是具有这种类型，它允许操作者选择性地接合时，电动机被操作的制动器的制动系统。

这允许操作者从车辆在电机，而不必担心车辆滚动下坡等的运行卸除。

申请人还认为有希望的是提供一种移植块地安装在泵头部和马达头其中将纳入必要流动通道的发送之间，止回阀等，以非常有效地和简单地提供用于流的流体围绕传动和消除需要用于连接泵头部和马达头软管。

移植块还设置有一个流体流旁路到允许操作者推动相关联的车辆没有流体锁定车辆的车轮的液压动作。

一个统一的传输本文中所描述的类型的进一步优选的特征包括，对于某些实施方案中，车辆车轮可以直接在传输的输出轴安装，而在车辆的相对侧透射驱动轮由单个输入驱动共同轴，还同时提供一个齿轮减速，如上所述，内部的传输。

这允许在部件高度有效的利用，并减少并为简化起见，在所得的载体。

可替代地，传输是足够柔韧的，对于一些实施例中，输入轴可以是成角度的相对于可以由泵头部和马达头变速器之间的移植块的修改来实现输出轴。

此外，积分电荷泵被确定为所希望的。

电荷泵由开关输入轴，其提供化妆液压流体到泵头部，同时允许循环流体用于冷却和过滤的驱动。

Hydraulic transmission systemMany hydraulic transmissions have been previously designed which allow an operator to infinitely vary the output of the transmission or even to reverse the output of the transmission as compared to the input. Normally, this has been accomplished by use of a swash plate which is either manually operated by the operator or hydraulically motivated to vary flow of hydraulic fluid through a rotating pump head having axially moving pistons. The flow of hydraulic fluid from the pump head pistons, in turn, rotates a motor head by motivating a corresponding set of pistons therein acting against a fixed cam and, consequently, rotates an output axle attached to the motor head.Typically, the prior art transmissions have been provided with various features such as gear reduction, brake setting equipment and the like. Unfortunately, these features are usually provided external of the transmission and significantly add to the volume and mass of the overall apparatus. Applicants determined that it was quite desirable to have an integrated transmission wherein substantially all of these necessary or desirable functions could be provided internally in the transmission, while also producing a highly effective and quite efficient transmission.In particular, transmissions of this type are frequently used on equipment such as "zero turning radius" lawnmowers and the like wherein a potentially dangerous situation confronts the operator, bystander and the equipment itself if the device us allowed to continue to be propelled should the operator release thecontrols, as when the operator is inadvertently thrown from the device or becomes injured. Therefore, a "deadman" mechanism is often provided for automatically returning the transmission to a neutral configuration in such a situation such that the device does not continue to be powered, if the controls are released.Previous transmissions of this type have generally relied on some kind of external device such as counter-operating biasing springs which are designed to return the operator control shaft to a neutral position should the operator release the shaft. External devices of this type can be easily tampered with by a user or damaged. Integration of such a return to neutral function into the transmission itself allows for a reduction in external parts which can be damaged or inappropriately removed and substantially reduces the external structure required to support various features of the transmission.Another problem frequently encountered in transmissions of this type for use in lawnmowers and the like is that operation tends to be somewhat jerky or bouncy, as the operator is usually unable to smoothly control the transition from one speed to another and often attempts to make abrupt changes. Vibration from such jerky operation has a tendency to wear more heavily on the machine and the operator as well. Consequently, it is desirable to dampen the output of such a transmission to prevent such jerky motion.Not only is it desirable to be able to have a return to neutral function, as desribed above, but it is also desirable for the operator to have a positive feel for the neutral position, whether the operator is moving from neutral to forward or from neutral to reverse. This feature is referred to herein as a positive neutral function and, in general, the feature requires that the operator extend more energy or movement in converting from the neutral orientation of the transmission to either a forward or reverse orientation, as compared to the amount of energy expended or movement required to transfer from one speed to another in a particular direction. As with the other features noted above, it is desirable that the structure required to provide this feature be incorporated within the transmission itself.For reasons of convenience and simplicity, it is preferable that the transmission receive power directly from the motor drive train without passing through gear reduction apparatus. Unfortunately, most output requirements are such that the output rotational speed must be substantially reduced as compared to the input rotational speed taken directly from the motor. Consequently, it is further desirable that the transmission incorporate an internal gear reduction system allowing for a substantial reduction in output speed as compared to input speed, even when the hydrostatic transmission of the type having axially moving pistons driving the output motor is oriented to provide the maximum output speed. (It is noted that at some lower than maximum output speeds, virtually all variable output transmissions inherently provide some gear reduction because ofpower bypass of one type or another, but none of the prior art transmissions known to applicants provide a substantial internal gear reduction at full output).Certain of the vehicles utilizing transmissions of this type include brakes which effectively prevent the vehicle from moving when the motor driving the transmission is stopped. These brakes are usually manually applied and require a substantial amount of structure mounted on the vehicle. In particular, parking brakes of this type have usually included an operator lever arm with an associated linkage connecting the lever arm to a brake mechanism which, in turn, locks the drive wheels, drive shaft or the like. Again, to simplify this structure and to integrate the braking function into the transmission, it was deemed desirable by applicants to construct a transmission which would have internal structure to automatically engage a parking brake when the motor driving the transmission was stopped.While a parking brake of this type is highly advantageous, it is also necessary to provide such a brake with an override structure which will allow the operator to selectively override the brake; for example, where the operator wishes to push the vehicle to a different position when the motor will not start. Further, it is advantageous to have a braking system of this type which allows the operator to selectively engage the brake when the motor is operating. This allows the operator to dismount from the vehicle while the motor is running without fear of the vehicle rolling downhill or the like.Applicants also deemed it desirable to provide a porting block mountable between the pump head and motor head of the transmission which would incorporate necessary flow channels, check valves and the like to very effectively and simply provide for flow of fluid about the transmission and to eliminate the need for hoses connecting the pump head and motor head. The porting block is also provided with a fluid flow bypass to allow an operator to push an associated vehicle without the hydraulic action of the fluid locking the wheels of the vehicle.Further desirable features of a unified transmission of the type described herein include that, for certain embodiments the vehicle wheels may be mounted directly on output shafts of the transmission, while transmission driving wheels on opposite sides of the vehicle are driven in common by a single input shaft, also while providing for a gear reduction, as described above, internal of the transmission. This allows for a highly efficient use of and reduction in parts and for simplicity in the resulting vehicle. Alternatively, the transmission is sufficiently flexible that for some embodiments, the input shaft may be angled relative to the output shaft which can be accomplished by modification of the porting block between the pump head and the motor head of the transmission. In addition, an integral charge pump was determined to be desirable. The charge pump is driven by the imput shaft which provides makeup hydraulic fluid to the pump head while allowing circulation of the fluid for cooling and filtering.。