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西安文理學(xué)院本科畢業(yè)設(shè)計(jì)（論文）中期檢查表
題 目
可傾式回轉(zhuǎn)工作臺(tái)設(shè)計(jì)
學(xué)生姓名
張陽(yáng)
學(xué) 號(hào)
08102080217
專業(yè)名稱
機(jī)械設(shè)計(jì)制造及其自動(dòng)化
指導(dǎo)教師
邊培瑩、呂榮生
檢查時(shí)間
2012.4
班 級(jí)
08機(jī)械（2）班
畢 業(yè) 設(shè) 計(jì)（論文） 進(jìn) 展 情 況
通過(guò)對(duì)可傾式回轉(zhuǎn)工作臺(tái)相關(guān)資料的學(xué)習(xí)，以及對(duì)整個(gè)設(shè)計(jì)的了解，現(xiàn)基本完成以下設(shè)計(jì)工作：
1. 基本了解了可傾式回轉(zhuǎn)工作臺(tái)的工作原理及實(shí)現(xiàn)方法；
2. 設(shè)計(jì)了總體的傳動(dòng)方案和設(shè)計(jì)方案；
3. 了解不同的回轉(zhuǎn)設(shè)計(jì)與傾斜設(shè)計(jì)的要求，選擇最佳結(jié)構(gòu)實(shí)行設(shè)計(jì)；
4. 完成傳動(dòng)系統(tǒng)的設(shè)計(jì)，包括電機(jī)的選擇，軸的設(shè)計(jì)，齒輪的設(shè)計(jì)，工件臺(tái)的設(shè)計(jì)；
5. 初步確定了論文的提綱和核心。
下一步設(shè)計(jì)工作內(nèi)容是回轉(zhuǎn)傳動(dòng)部分設(shè)計(jì)及詳細(xì)計(jì)算，相關(guān)零件的設(shè)計(jì)以及相關(guān)零件圖的繪制。最后完成畢業(yè)論文撰寫。
指 導(dǎo) 教 師 意 見
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年 月 日
教研室意見
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年 月 日
西安文理學(xué)院,學(xué)生姓名：張陽(yáng) 學(xué) 號(hào)： 08102080217 指導(dǎo)教師：邊培瑩 呂榮生 專業(yè)班級(jí)：08級(jí)機(jī)械設(shè)計(jì)制造 及其自動(dòng)化2班,,可傾式回轉(zhuǎn)工作臺(tái)設(shè)計(jì),可傾式回轉(zhuǎn)工作臺(tái)是指在機(jī)床工作臺(tái)工作時(shí)除了有X、Y、Z三個(gè)直線進(jìn)給軸之外，還有一個(gè)可傾式進(jìn)給軸和一個(gè)回轉(zhuǎn)進(jìn)給軸，即繞X軸傾斜的A軸和以Z軸旋轉(zhuǎn)的C軸。,,簡(jiǎn)介,課題意義,可傾式回轉(zhuǎn)工作臺(tái)提供了一種動(dòng)作結(jié)構(gòu)緊湊、操作方便、在較小的空間尺寸范圍以軸旋轉(zhuǎn)傾斜實(shí)現(xiàn)多面加工，解決了在各類型數(shù)控機(jī)床上進(jìn)行四軸或五軸加工的問題，實(shí)現(xiàn)了對(duì)零件的分度加工和連續(xù)曲面加工。同時(shí)該工作臺(tái)的設(shè)計(jì)也可縮短生產(chǎn)準(zhǔn)備時(shí)間，增加切削加工時(shí)間的比率，從而提高生產(chǎn)效率。 結(jié)構(gòu)的研究對(duì)一個(gè)國(guó)家的航空、航天、軍事、科研、精密器械、高精醫(yī)療設(shè)備等行業(yè)的發(fā)展有著舉足輕重的影響力。,,,回轉(zhuǎn)部分設(shè)計(jì)圖,,回轉(zhuǎn)部分設(shè)計(jì),工作臺(tái)需要回轉(zhuǎn)是通過(guò)油道1進(jìn)油使活塞2向上運(yùn)動(dòng)，同時(shí)推動(dòng)推力球軸承4使中心軸5向上運(yùn)動(dòng)，從而工作臺(tái)也向上移動(dòng)，實(shí)現(xiàn)上端齒盤6和下端齒盤7的松開，為實(shí)現(xiàn)回轉(zhuǎn)動(dòng)作做好準(zhǔn)備。當(dāng)工作臺(tái)回轉(zhuǎn)完成后，需要下降使工作臺(tái)夾緊時(shí)，油液會(huì)從油道8進(jìn)入活塞缸上腔，使活塞2向下移動(dòng)，中心軸5帶動(dòng)工作臺(tái)下降。使上端齒盤6和下端齒盤7嚙合，實(shí)現(xiàn)工作臺(tái)的夾緊定位。,,擺動(dòng)部分設(shè)計(jì)圖,,擺動(dòng)部分設(shè)計(jì),工作臺(tái)需要傾斜時(shí)，齒條2與齒輪1咬合，齒條2進(jìn)行徑向運(yùn)動(dòng)，帶動(dòng)齒輪1轉(zhuǎn)動(dòng)，齒輪1與擺動(dòng)架3由螺栓連接，擺動(dòng)架3與底座6通過(guò)深溝球軸承相連，由于底座固定所以齒條2的直線運(yùn)動(dòng)轉(zhuǎn)變?yōu)辇X輪1的擺動(dòng)。擺動(dòng)架跟著擺動(dòng)實(shí)現(xiàn)回轉(zhuǎn)工作臺(tái)的傾斜運(yùn)動(dòng)，可實(shí)現(xiàn)了工作臺(tái)90度傾斜。當(dāng)擺動(dòng)到加工位時(shí)，齒條2與齒輪1分離，實(shí)現(xiàn)定位加工。,,液壓動(dòng)力部分設(shè)計(jì),在液壓缸的兩側(cè)油路上都串接液壓?jiǎn)蜗蜷y（液壓鎖），活塞可以在行程的任何位置上鎖緊，不會(huì)因外界的原因而顫動(dòng)，而其鎖緊精度只受液壓缸的泄漏和油液壓縮性的影響。為了保證鎖緊迅速準(zhǔn)確，換向閥采用了H型中位機(jī)能。這種液壓系統(tǒng)能很好的滿足液壓式可傾式回轉(zhuǎn)工作臺(tái)的要求。 CB-B4液壓油泵的選擇,,主要零部件設(shè)計(jì)計(jì)算,工作臺(tái)：T型槽、襯套、螺孔分布 端齒盤：工作臺(tái)尺寸 中心軸：工作臺(tái)、端齒盤配合 中心軸承：推力球軸承 活塞：軸心轉(zhuǎn)軸 齒輪：力、傳動(dòng) 齒條：90度擺動(dòng),,其他零件設(shè)計(jì),密封圈：齒條 活塞封閉塊：活塞桿直徑 推桿導(dǎo)向塊：擺動(dòng)實(shí)現(xiàn)角度配合 擺動(dòng)架：與傳動(dòng)整體配合 底座：擺動(dòng)架,結(jié)束語(yǔ),通過(guò)這次畢業(yè)設(shè)計(jì)的磨練，我學(xué)到了很多東西。這是一次系統(tǒng)的知識(shí)考察。專業(yè)課程知識(shí)綜合應(yīng)用的實(shí)踐訓(xùn)練，這是我們邁向社會(huì)，從事職業(yè)工作前一個(gè)必不可少的過(guò)程。一步步走下來(lái)，讓我的思維模式更加嚴(yán)謹(jǐn)。 在此要感謝我的輔導(dǎo)老師邊老師，感謝她耐心的指導(dǎo)與督促，在我設(shè)計(jì)過(guò)程中時(shí)刻對(duì)我批評(píng)與建議讓我進(jìn)步很大。 感謝我的同學(xué)，感謝他們給了我許多的幫助。,附錄
外文文獻(xiàn)
A MODULAR MODELING APPROACH FOR THE DESIGN OF RECONFIGURABLE MACHINE TOOLS
Tulga Ersal
Graduate Student Research Assistant Department of Mechanical Engineering University of Michigan, Ann Arbor tersal@umich.edu
Jeffrey L. Stein
Professor Department of Mechanical Engineering University of Michigan, Ann Arbor stein@umich.edu
Loucas S. Louca
Lecturer Department of Mechanical and Manufacturing Engineering University of Cyprus lslouca@ucy.ac.cy
ABSTRACT
A new generation of machine tools called Reconfigurable Machine Tools (RMTs) is emerging as a means for industry to be more competitive in a market that experiences frequent changes in demand. New methodologies and tools are necessary for the efficient design of these machine tools. It is the purpose of this paper to present a modular approach for RMT servo axis modeling, which is part of a larger effort to develop an integrated RMT design and control environment. The components of the machine tool are modeled in a modular way, such that the model of any given configuration can be obtained by assembling the corresponding component models together based on the topology of the machine. The component models are built using the bond graph language that enables the straightforward development of the required modular library. These machine tool models can be used for the evaluation, design and control of the RMT servo axes. The approach is demonstrated through examples, and the benefits and drawbacks of this approach are discussed. The results show that the proposed approach is a promising step towards an automated and integrated RMT design environment, and the challenges in order to complete this goal are discussed.
INTRODUCTION
The ever-growing competition forces manufacturers to respond more quickly to changes in demand. As a result, manufacturers have to deal with short product life cycles, short ramp-up times and frequent changes in product mix and volumes, without compromising product quality and cost.
Being the heart of a manufacturing system, improved machine tools hold the key in meeting the above mentioned requirements. The shortcomings of conventional machine tools, which can be classified as dedicated and flexible, are being felt more today than in the past: With their design focus being a single part, dedicated machines lack the flexibility and scalability that the flexible machines offer. On the other hand, flexible machines cannot achieve the robustness, the cost-effectiveness and the throughput levels of dedicated machines[1].
A new generation of machine tools is being developed in the Engineering Research Center for Reconfigurable Manufacturing Systems at the University of Michigan, Ann Arbor, as part of an effort to overcome the insufficiencies of current manufacturing systems. These machine tools are called ‘Reconfigurable Machine Tools (RMTs)’ [2], and they combine the advantages of their dedicated and flexible counterparts. They are designed around a part family and their structure, in terms of both hardware and software, can be changed quickly and cost-effectively to achieve the exact functionality and capacity desired [3].
Containing several configurations to provide the needed flexibility and scalability, RMTs intrinsically lead to more complex machine tool design problems. Methodologies and tools that would help facilitate the design of RMTs could highly benefit and encourage the employment of reconfigurable
manufacturing systems [4-6].
One important aspect of the RMT design problem is developing dynamic models for the design, evaluation and control of servo axes. What makes the problem of modeling RMTs unique is that even though there is a single machine tool, there exist several configurations, which separate models have to be developed for. Developing dynamic models for all possible configurations could be a cumbersome and time-consuming task if ad hoc methods are utilized. Moreover, without a systematic methodology modeling would require a lot of expertise and would be prone to errors, which would degrade the efficiency of using models in the design.
In this paper we present a methodology that could help make the RMT modeling task less time demanding, less error-prone and less challenging. The key idea of this methodology is to take advantage of the modular structure of the RMTs and adopt modular modeling concepts into the RMT modeling methodology. First, the physical components of an RMT are modeled in a modular way using the bond graph modeling tool [7]. The bond graph model is encapsulated in a schematic representation with defined connection ports. Then, the schematic component models are assembled by following the topology of a given configuration to obtain the model of the configuration. The configuration model can be easily integrated with the modules of non-energetic components such as interpolators and controllers, which can be conveniently represented with block diagrams; however this is beyond the scope of this paper.
BACKGROUND
The RMT concept was introduced by Koren and Kota [2], and since their introduction, the design of RMTs has been an active research area. Methodologies and tools for designing RMTs [4] as well as evaluating structural stiffnesses [5] and tool tip errors [6] of de sign alternatives have been developed.
However, the problem of developing a system level modeling methodology for RTMs has not been addressed yet. Traditionally, machine tool models depict the machine tool as a group of servomotor and feed drive assemblies that aremodeled as first or second order systems [8,9]. Chen and Tlusty, however, showed that the structural dynamics of the feed drive could affect the system performance once high-speed machine tools are considered [10]. Many researchers identified the necessity to use higher order models for high-speed machine tools to cope with structural dynamics in order to be able to design the control system successfully [11-13].These publications clearly indicate that modeling a machine tool is not a trivial task and care must be taken when deciding on the complexity of the model, but they do not provide a systematic way of modeling and, therefore, remain application specific approaches.
There have been research efforts to help the design and control of machine tool feed drives by automatically providing simulation models. Wilson and Stein developed a software program called Model-Building Assistant to automatically
synthesize a minimum order model of the machine tool drive system for a given frequency range of interest (FROI) [14]. The complexity of the model, which includes a flywheel, a torsional shaft, a ballscrew , a ballnut, a DC motor, a torsional coupling, a belt-drive and a gear-pair as components, is automatically
increased until the eigenvalues of the system fall beyond the specified FROI. This work was a proof of concept for a model deduction algorithm and can not be applied to any real machine tool system. However, such algorithm can be used to determine the appropriate model complexity after the development of the system model.
Gautier et al. have developed a software package called SICOMAT (Simulation and Control analysis of Machine Tools) which helps with the modeling, simulation, modal analysis and controller tuning of one or two decoupled or two coupled machine tool axes [15]. Their models describe the dynamics of the mechanical system by a number of masses and springs. This work makes the modeling of a machine tool process more systematic, and is therefore a valuable tool to the modeling engineer; however, it lacks the generality, modularity and flexibility that the RMT design methodology demands. The RMT modeling methodology Figure1 shows the envisioned RMT modeling environment. It is desired to automate the task of RMT modeling, where the model of a given RMT configuration is automatically assembled from a library of modular component models. This way, all the candidate designs, which are generated either manually or automatically [4], can be modeled quickly and the models can be used to evaluate the candidates in terms of their servo axis dynamic performance and help with their design. As Figure1 also implies, the modular component model library is a key part for the automated RMT modeling environment. Therefore, the first step of the proposed methodology is to develop modular models for the components that are used to generate the RMT configurations. This paper puts the emphasis on mechanical parts and discusses their modeling in a modular way, because the energy interaction between the mechanical components makes their modular
modeling more intriguing. Modular modeling of components that only exchange signals, e.g. interpolators and controllers, presents a relatively simpler problem and are not discussed here. To promote modularity and to be able to deal with the energy interactions between the components and their environment rather easily, bond graphs are utilized as the modeling language. Bond graphs provide a power-based graphical representation of a physical system. Moreover, bond graphs describe different energy domains in a unified way, which is a relevant advantage for RMT modeling, since their servo axes may include components from different energy domains, such as mechanical, electrical or hydraulic. Bond graphs are only one level in the hierarchy of model representations used in this work. Underneath the bond graph level the mathematical equations represent the physical phenomena captured by the bond graph and this mathematical representation is the lowest level in the hierarchy. In the highest level bond graphs are encapsulated in a schematic representation, which not only allows for a compact representation, but also shows the connection ports where the model can interact with its environment. Figure 2 illustrates this hierarchy of model representations.
In this paper all the models are shown in the schematic level, because the goal of this paper is not to discuss their derivation, but rather to show what can be done once those models are obtained. A detailed description of the models used in this paper can be found in [16].In order to be able to cope with any spatial motion that the mechanical components may go through in different configurations, models that capture the three-dimensional dynamics are used. Moreover, the initial assumption is made that in the mechanical domain all components can be adequately represented as rigid bodies.
Figure 3 shows the schematic representation of a generic rigid body with N connection ports, which is one of the main model modules in the library. The ports correspond to points of interest on the rigid body, where the physical interactions with the environment occur. Bonds (lines with half arrows) are used to indicate that a port is a power port, i.e. the body can exchange energy with its environment through those ports, whereas active bonds (lines with full arrows) indicate signal ports, i.e. only information is transferred through these ports. The model library also contains three-dimensional joint models that can be used to describe the relative motions between the component models. These joint models are also developed in a modular way with ports, where they can be connected to other model modules. The library offers two ways to express the constraints: (1) stiff springs and dampers can be used to implement more realistic constraints or to approximate ideal constraints;(2) Lagrange multipliers can be introduced to express the constraints ideally. For a discussion of joint models the reader is also referred to [16].Once the model library is populated with some basic modular rigid body and joint models, the modeling procedure can be carried out as follows: The RMT components are broken down into subcomponents and each subcomponent is associated with a model in the library. If none of the model modules in the library can describe the subcomponent adequately, a new model has to be developed for that subcomponent and added to the library. Then, the models are assembled by following the topology of the components and using the necessary joint models. Once a component model is obtained, it can be stored in the library for reuse. Finally, the component models are assembled by following the topology of a given configuration to obtain the model of that configuration. The process is illustrated in Figure 4 as a flowchart and demonstrated in the following section through examples.
EXAMPLES
The following two examples give an overview of the proposed modeling methodology. The first example shows the modeling of a slide and the second example employs that slide model to develop a model for a RMT. The purpose of these examples is to give a general idea about how the modularity of the components can be exploited in the modeling procedure, rather than to explain the details of how each (sub)component can be identified and modeled. Therefore, the details of the model modules, such as their level of complexity, are not discussed.
Modeling a Slide A slide is a basic component of most machine tools, including RMTs. Different RMT configurations can beobtained by adding/removing slides to/from the configuration or by rearranging the existing slides in the configuration. Therefore, it is useful to demonstrate the modeling procedure of a slide. Consider the slide shown in Figure 5. It is assumed that the
components are identified as shown in the figure. For the purposes of this example, all the subcomponents except the motor can be modeled as rigid bodies with various number of connection points. The motor dynamics can be broken down into two domains: the three-dimensional rigid body dynamics of the housing and the electromechanical dynamics that drive the relative rotational motion between the rotor and the stator. A model has been developed for the motor that captures the dynamics in both domains and its schematic representation is given in Figure 6.
Modeling the Arch-type RMT, which was developed by the NSF Engineering Research Center for Reconfigurable Manufacturing Systems at the University of Michigan, is the world’s first full scale RMT. It is a three-axis machine tool that is designed around a part family with five different surface inclinations ranging from -15° to 45° at 15° increments and has the flexibility of doing machining operations such as milling and drilling at any of those angles. The reconfigurability of the Arch-type RMT comes from the spindle unit, which can be configured at the five angles mentioned above by moving it along the curved guide way of the arch module and fixing it at any of the five locations on the arch module that are defined by mechanical stops. For the purposes of this example the base module is assumed to be identical to the ground and it has no effect on the dynamics of the machine tool. The worktable, the column and the spindle are essentially slides and their models are based on the slide model given above. The arch is modeled as a rigid-body with a connection port for each mechanical stop. Finally, the model of the Arch-type RMT is assembled by following the topology of the actual machine. Note that the figure shows the model for one of the configurations only. The models for the other configurations can be obtained by changing the connection port of the arch model.
Now that the model is assembled, the equations of motion can be derived from the graphical model automatically, and simulations can be performed. Although the mathematical model is ready, we cannot provide any simulation results in this paper due to the current lack of good estimates of system parameters. Simulations can be carried out easily once the parameter values are available.
DISCUSSION
In this paper, modular and hierarchical modeling concepts are identified as the key characteristics of the RMT modeling methodology. The modular structure of RMTs makes this modeling approach beneficial, because the models contain all the key characteristics of reconfigurability [17]:
1. Modularity: The (sub)components are modeled in a modular way
2. Integrability: The models can be integrated with other modules through their connection ports
3. Customization: The level of detail included in the model modules can be customized for individual components
4. Convertibility: Models can be easily converted from one configuration to another
5. Diagnosability: Model verification can be carried out easily on model modules
The approach presented in this paper allows for the separation of the modeling task into two steps:(1) Developing component models;(2) assembling the configuration model. While the first step still requires a significant modeling expertise, the second step is much more systematic, and can even be automated, which is left as a future work. Also, the two steps have different focuses: The first step focuses on the dynamics within a component, whereas the second step focuses on the dynamics between the components.
Compared to the existing approaches of servo axis modeling, where every different RMT configuration would potentially be a new modeling problem, the approach presented in this paper allows for a faster development of configuration models. Configurations can be assembled quickly using the model modules in the library, provided that all the components utilized in a given configuration have a corresponding model module in the library. Therefore, having a comprehensive model library is essential for this methodology to be efficient.
A three-dimensional multibody approach to modeling the mechanical components of the machine tool promotes modularity in the mechanical domain.
Thus, for example, the model of the machine tool slide can be used in any configuration without having a special slide model for circumstances where the base of the slide is constrained to move in more restricted ways. With a multibody approach, generic component models can be created without a-priori knowledge of the connectivity of the components. A drawback of the three-dimensional multibody approach is, however, that the generic models might be more complex than a certain configuration actually demands. For example, in a given configuration a component can be limited to a planar motion only, in which case a three-dimensional model would be overcomplex. The model should be simplified; otherwise unnecessary complexity is retained in the model and reduces the computational efficiency of the model. The proposed modular modeling methodology would benefit from the integration with a model order reduction algorithm. This will be the focus of future work.
Currently the bodies are considered rigid, which is not always an adequate approximation. In order to be able to study the effects of the structural dynamics, flexible body models should also be developed and included in the library.
Finally, it is worthwhile to note that commercially available software packages, such as ADAMS, DADS, EASY5, Dymola etc, could also be used for the purposes of RMT modeling. However, to take advantage of the unified power
based approach that the bond graphs provide and to make a future model reduction easier to implement, bond graphs are chosen as the modeling language.
SUMMARY AND CONCLUSIONS
A modular modeling approach is proposed as a RMT modeling methodology. The components are modeled in a modular way, so that the modeling task of a given RMT configuration merely involves assembling the corresponding model modules together. Two examples are given to illustrate the methodology, and advantages and disadvantages of this approach are discussed.
The outcomes of this work indicate that a modular approach to the problem of modeling RMTs can make the modeling process systematic and thus potentially more useful to practicing engineers if implemented in an automated modeling and design environment. However, there ar