家用電動護理床設計【三維UG】【醫(yī)療床-病床】

喜歡就充值下載吧。。資源目錄里展示的文件全都有，，請放心下載，，有疑問咨詢QQ:414951605或者1304139763 ======================== 喜歡就充值下載吧。。資源目錄里展示的文件全都有，，請放心下載，，有疑問咨詢QQ:414951605或者1304139763 ======================== 湘潭大學興湘學院 畢業(yè)論文（設計）鑒定意見 學號：2010962933姓名： 王炳根 專業(yè)：機械設計制造及其自動化 畢業(yè)論文（設計說明書） 頁 圖 表 張 論文（設計）題目：家用電動護理床 內(nèi)容提要： 該護理床主要用于家庭病人的護理，具有背板升降、腿板升降以及整床升降功能。家用電動護理床是遵循人體護理需求和人體工程學原理而設計，實現(xiàn)了生活不能自理的患者所需要的幾大功能： 1、 整床升降功能，根據(jù)使用者的需要能夠把整床的高度進行調(diào)整，讓使用者感到舒服。 2、 坐起功能，根據(jù)使用者的需要可以把背部的床板調(diào)整到之間的任意位置。能夠?qū)崿F(xiàn)使用者睡累的情況下坐起，這有利益患者的康復，能夠促進患者血液循環(huán)，對患者的身體健康有著良好的影響。 3、 曲腿功能，能夠讓使用者在坐起時腿感覺到舒服，防止腿一直處于一種狀態(tài)而導致麻木。 該護理床的設計遵循以下幾個原則： 1、安全性原則 由于護理床對老年人和病人的身體進行直接的接觸與操作，而且相對于健康人來說，這類人群的身體更容易收到損傷，所以護理床在安全性方面的要求很高。無論是護理床的結構還是控制系統(tǒng)的設計，安全性始終是最優(yōu)先考慮的一個原則。比如，在結構設計方面，不應存在任何干涉情況，結構的剛度和強度方面都要留有充足的余量，要考慮到各種極限情況。 2、人性化、舒適性原則 現(xiàn)今社會，人們不僅追求商品的高質(zhì)量，高穩(wěn)定性，而且對商品的人性化、舒適性設計有了更高的要求，因此家用電動護理床應該根據(jù)人體生理學原理，更多地從人的生理結構、心理情況、行為習慣等方面加以考慮。比如各部分結構要與人體的尺寸匹配；設計中力求加速度最小化等等。 3、功能多樣化原則 在家用電動護理床的使用過程中，不同使用者往往對護理床有著各種各樣不同功能的要求，比如能夠坐起，整床能夠升降，能夠曲腿等功能要求。 4、標準化原則 護理床機械零件的設計與選擇、控制系統(tǒng)的設計、零部件之間的相對位置關系和尺寸匹配，都有相關的行業(yè)標準。參照標準設計，不僅能在最大程度上滿足使用要求，而且有利于增強互換性，降低成本。 5、輕量化原則 由于家用電動護理床是在家里使用，搬移的概率非常大，在設計時一定要考慮到床重量，方便搬移，在保證護理床使用安全的同時要從輕設計，這樣可以節(jié)省材料。尤其是在資源短缺的今天，這點尤為重要，而且還以降低成本。 指導教師評語 指導教師： 2010年 5月 日 答辯簡要情況及評語 答辯小組組長： 2010年5 月 日 答辯委員會意見 答辯委員會主任： 2010年 5月 日 Res Eng Des (1989) 1:69-73 Technical Note Research in E gineedng eslgn 1989 Springer-Verlag New York Inc. On the Role of Geometry in Mechanical Design Vadim Shapiro Herb Voelcker* The Sibley School of Mechanical and Aerospace Engineering, Cornell University, Ithaca, New York, USA A complete design usually specifies a mechanical system in terms of component parts and assembly relationships. Each part has a fully defined nominal or ideal form and well defined material properties. Tolerances are used to permit variations in the form and properties of the components, and are used also to permit variations in the assembly relationships. Thus the geometry and material properties of the system and all of its pieces are fully defined (at least in principle). Henceforth we shall focus on geome- try and, for reasons that will become evident, will not deal with materials despite their obvious impor- tance. Mechanical systems specified in the manner just described meet functional specifications that ap- peared initially as design goals. The process of de- sign can be thought of as generating the geome- tryMthe breakdown into components with coarsely specified geometry, and then the detailed specification of the component forms and fitting re- lationships. Design seems to proceed through si- multaneous refinement of geometry and function I. An important line of design research seeks sci- entific models for this refinement process and sys- tematic procedures for improving and perhaps auto- mating it. At present we have tools for dealing with two widely separated stages of the refinement process. For single parts, function is usually specified through loads on pieces of surface (e.g. a force distribution over a support surface, a flow rate through an orifice, a radiation pattern over a cool- ing fin); specification of the solid material that pro- vides a carrier for the pieces of surface may be viewed as a constrained shape optimization pro- cess. Also with the Computer Science Department, GM Research Laboratories, Warren, Michigan, USA * Reprint requests: The Sibley School of Mechanical and Aerospace Engineering, Cornell University, Ithaca, NY 14853, USA At the higher level of unit functionality, where one deals with springs, motors, gear boxes, heat exchangers, and the like, geometry usually is ab- stracted into real numbers if acknowledged at all, and function is cast in terms of ordinary differen- tial or algebraic equations (for heat flow, motor torque as a function of field current, and so forth). Systems of such equations describe the composite functionalism of networks of functional units. There is a big gap between these islands of un- derstanding, and intermediate stages of abstrac- tion are needed which acknowledge the partial ge- ometry and spatial arrangement topology of subassemblies. Broadly speaking, geometry is far- ing badly in contemporary design research; many investigators either sweep it under the carpet or deal with it syntactically, e.g. through features defined in ad hoc ways. Clearly we need more sys- tematic ways to address the relationship between geometry and function, and we suggest below some initial steps toward this goal. Energy Exchange as a Mechanism for Modeling Mechanical Function Mechanical artifacts interact with their environ- ments through spatially distributed energy ex- changes, and we argue below that mechanical func- tionalism can be modeled in terms of these exchanges. The initial cast of the argument draws heavily on seminal work by Henry Paynter 2. We shall regard mechanical artifacts as systems that range from single solids or fluid streams, which usually are the lowest level of natural system that exhibit important properties of mechanics, to com- plex assemblies of solids and streams. A closed boundary, which may be physical or conceptual, is a distinguishing characteristic of a system: the sys- tem lies within (and partially in) the boundary, the environment lies outside, and interaction occurs 70 Shapiro & Voelcker: Geometry in Mechanical Design through the boundary. We distinguish the follow- ing: S : the physical system under discussion; 8S : the boundary of S; V : a spatial region containing S whose complement is the environment; 8 V : the boundary of V. S may coincide with V, and 8S and 8 V are closed surfaces (usually 2-mainfolds) in E 3. We distinguish S from V because S may be partially or wholly un- known (recall that this note is about design) but boundable by a known V. The principle of continuity of energy applies at all levels of system abstraction. If no energy is gen- erated by the system, then O_f dV fsv Pnd(SV)= fv Ot + fvgdV. (1) The surface integral on the left describes the total energy flux (instantaneous power) through the boundary; P is a generalized Poynting vector de- scribing the instantaneous rate at which energy is transported per unit area, and n is the normal at a point in the boundary 8 V. On the right, Oe/Ot is the (volumetric) density of energy stored in the system, and g is the rate of energy loss or dissipation. A system interacts with its environment by ex- changing energy through its physical boundary: for example, by radiating energy stored in the system over a portion of its area, or by providing support to an external mating part and thereby inducing stor- age of deformation energy in the system. The sub- sets of the physical boundary over which such ex- changes occur will be called (following Paynter) energy ports. If s is the physical boundary subset (piece of surface) associated with the i tu port, then P nd i fv dV+fvgdV (2a) where sl C 8S. (2b) Thus the total energy flux through the boundary is a sum of signed fluxes through the ports. We note that a boundary subset si may belong to several ports, and that body forces, such as those induced by gravitational and magnetic fields, may be accom- odated by taking S as the associated port. Geometrical and Functional Refinement in the Limit The left side of Eq. (2a) specifies energy exchanges through the systems ports and requires that the flux vector(s) and port geometries be known. The terms on the right cover internal energy (re)distribution and/or dissipation. The physical effects implied by these terms depend on the energy regime(s) and the geometry of the system; there may be rigid body motion, elastic or plastic deformation, temperature redistribution, and so forth. Mathematical evalua- tion requires the solution of 3-D boundary- and/or initial-value problems. Very marked simplifications ensue if one as- sumes that 1) the ports are spatially localized and idealized so that the integrals on the left of Eq. (2a) may be evaluated individually to yield terms Pi, and 2) internal energy storage and dissipation are simi- larly localized in disjoint discrete regions, thereby permitting the right-hand integrals to be decom- posed into sums of local integrals which may be evaluated individually. With these assumptions, Eq. (2a) may be rewritten Z e, = 2-07 + Gk i j k (3) where Pi is the power through the i h discrete port, Ej is the instantaneous energy stored in the jth dis- crete region, and Gk is the dissipation rate in the k th discrete region. A limiting form of this refinement (or discretization, or-in Paynters terminology- reticulation) is a Dirac-delta limit wherein the ports shrink to spots of zero area and the volumetric regions shrink to point masses, idealized resistors, and the like. Equation (3) is the basis for Paynters energy bond diagrams, or bond graphs. It describes a sys- tem that may transfer, transform, store, and dissi- pate energy through elements whose geometry has been refined into a few real numbers-the spatial positions of the discrete ports and lumped regions (which generally are not carried in bond-graph rep- resentations), and integral characterizations of the discrete ports and regions (for example the value, in kilograms, of a point mass). This higher view enables one to analyze the dynamics of the idealized (discretized) system, but one can deduce little about the geometry of feasible distributed (i.e., real) systems from such analyses; essentially all ge- ometry must be induced. Apparently we have gone too far, i.e., have thrown away too much geometry. Shapiro & Voelcker: Geometry in Mechanical Design 71 O :;.O) O O (a) .,. -o. (O) : 0 ) (b) (c) (d) Fig. 1. Design of a simple bracket. Toward an Appropriate Role for Geometry We would like to step back from the limiting refine- ment just discussed, where all notions of form have been lost, and include in the problem some continu- ous geometry-but not the full-blown field problem covered by Eq. (I) unless this is unavoidable. We shall suggest below three principles governing the interaction of form and function that we believe will yield geometrically well defined (but not necessarily optimum) designs. A simple but common example drawn from practice-design of a bracket-will motivate the discussion (Fig. 1). The design begins with three holes of known di- ameter and configuration that are to be carried by an unknown solid (Fig. la); these mate with other parts (two screws and a pivot pin). Bosses are created to contain the holes (Fig. lb) because of concern about interference with other components passing between the holes. Finally the holes and bosses are bound together into a single part as in Figs. lc and ld, with the final shape being governed by criteria for clearance, strength, weight, and aes- thetic and manufacturing simplicity. Two simple but important inferences may be drawn from the example. Firstly, the initial holes (plus some implied constraint surfaces in the third dimension) are the brackets energy ports; they are fully specified geometrically and specify by implica- tion what the bracket is to do-maintain the relative position of ports whose geometry admits rotational motion. In principle the associated energy regimes (force, torque:elasticity) can be fully specified as well, but in practice they are often only implied or understood. Secondly, the remaining geometry is discretionary but constrained by requirements that the holes be bound into a connected solid, that Fig. 2. Position-fixing character of the bracket. the solid not interfere with other components, and so forth. We note that, at the single-component level of the bracket, shape optimization usually does require solution of the full 3-D field problem covered by Eq. (2a). From this example and others we induce: Principle 1. A systems function is determined by its energy ports, which are generally subsets of its physical boundary, and the energy regimes oper- ating on those ports; both should be fully defined. The remaining geometry of the system is discretion- ary provided that 1) it admits at least one physical realization of the system that satisfies the port spec- ifications, and 2) other external constraints, e.g. on overall size, are met. Principle 2. Energy exchanges within a system al- ways may be represented independently of geome- try, e.g. via bond graphs. Figure 2 shows the position-fixing capabilities of the bracket represented (nonuniquely) by ideal springs attached to the locally rigid ports. This rep- resentation of the brackets partial functionalism as- sumes ideally elastic behavior, and this assumption should be checked, e.g. by finite-element analysis, as the brackets final shape is being determined. Figure 3 shows a slightly more complicated sys- tem-an indicator that senses pressure via an orifice (port) of known geometry, and displaces a rotary indicator correspondingly. The output indicator is a port because we require that it be able Input Output V/ Support Port Fig. 3. A pressure measuring system. 72 Shapiro & Voelcker: Geometry in Mechanical Design to do work on the environment, e.g. overcome specified restraining torques over a defined range of travel, and hence its geometry must be defined. The system also has a third support port. The systems primary function is represented internally by a pres- sure/torque transformer and a rotary spring which are shown as bond graph elements in the style of Ulrich and Seering 3, but this representation is not unique; it may be replaced with other, arbitrarily elaborate arrangements of idealized elements hav- ing the same input/output functionalism plus other paths that terminate internally. Equation (4) provides the rationale for Principle 2. The essential idea is that the port i P n dsi = 2 -ot- + Z Gk (4) i j k flow on the left of Eq. (2a) may be handled inter- nally (the right-hand integrals in Eq. (2a) in many ways. If we are assured by Principle I, or simply assume, that internal solutions exist, then we may reticulate the internal geometry and deal with inte- gral quantities as in Eq. (3). Principle 3. Principles 1 and 2 must hold for all subsystems defined on combinatorial decomposi- tions of a system. Principle 3 provides means for the simultaneous refinement of geometry and function. It enables complicated systems to be decomposed recursively into functional subsystems provided that one de- fines the ports as one proceeds. The limiting combi- natorial refinement is single parts, and at this level one must solve the field problem of Eq. (2a) to ob- tain complete geometric specifications. Concluding Remarks The thoughts above are aimed at finding means to establish for geometry an appropriate formal role in a theory of mechanical design. It seems obvious to us that geometry should have such a role, but the work needed to establish it has barely begun. EpilogueRRemarks on Features This work grew out of a several-month effort to characterize geometric features in a formal man- nerwan effort that largely failed. The effort was motivated by the fact that mechanical design and manufacturing are often discussed and done in terms of features, but there are no agreed views on what features are or do 4. (Slots, fibs, webs, and shafts, are typical features; all involve geometry in one way or another.) We began with a conjecture: A geometric feature may be defined as a geometric idealization of a port for energy exchange in a defined regime. (This no- tion is appealing because it implies that a systems feature-set specifies all of the geometry needed to define the systems interactions with its environ- ment; the remaining geometry is determined by constraints and optimization.) We then proceeded to show that the conjecture is formally consistent in design, manufacturing, and inspection applications. In machining, for example, geometric features may be associated with the boundary of the removed material; the energetic process is machining itself, whose dynamics are reasonably well understood in a macroscopic sense. Clamping features may be de- fined primarily through elastic energy storage, in- spection features through the energetic exchange involved in the measurement process, etc. But as our explanations grew increasingly contrived and our difficulties with solid and other non-surface fea- tures mounted, we began to sense that features could not be defined in any universal system other than a purely syntactic system. Currently we believe that features are simply in- formation structures that represent, often in para- metric form, known solutions to local problems. While a syntactic structure can be imposed on them, their underlying semantics can vary widely and need not involve particular kinds of geometry, or indeed any geometry at all. However, if a feature is to be used properly, a feature-context must be suppliedmthe technical conditions and criteria that led to the solution the feature represents. Given the feature-context (e.g., as domain knowledge in a de- signers head) and appropriate reasoning power to adapt the solution to the current problem, features can be very effective; their popularity among hu- man designers attests to this. Recent work by Duffey and Dixon 5 illustrates that features can be used in automatic design when feature-contexts and appropriate reasoning power are provided. (The handling of features by Duffey and Dixon seems ad hoc, but ad-hocery may be intrinsic if our current permissive view of features is correct.) Features can be dangerous when used without their contexts and appropriate reasoning power, as nonsense designs produced by certain au- tomatic design systems illustrate. Finally, we wish to point out that the character- Shapiro & Voelcker: Geometry in Mechanical Design 73 ization of features as known solutions to local problems places strong constraints on schemes for combining features to make new features. A feature combination makes sense only if it can be shown to be a valid solution to a well defined local problem. But even determining the domain of the combina- tion problem as a function of its component do- mains may prove very difficult. Acknowledgments. The work reported here was supported in part by the General Motors Corporation under its corporate fel- lowship program, and by the National Science Foundation under grant MIP-87-19196. References 1. Alexander, C., Notes on the Synthesis of Form, Harvard Uni- versity Press, 1964 2. Paynter, H.M., Analysis and Design of Engineering Systems, MIT Press, 1961 3. Ulrich, K.T. and Seering, W.P., Conceptual Design: Syn- thesis of System of Components, 1987 ASME Winter Annual Meeting, PED Vol. 25 4. Report of the Workshop on Features in Design and Manufac- turing, February 26-28, 1988 University of California, Los Angeles 5. Duffey, M.R. and Dixon, J.R., Automating extrusion de- sign: a case study in geometric and topological reasoning for mechanical design, Computer-Aided Design, Vol. 20, No. 10, pp. 589-596, December 1988