'분류 전체보기'에 해당되는 글 96건
- 2016.11.02 Matlab Wait message box
- 2016.10.11 Matlab GUI Drag and Drop
- 2016.10.10 Modeling Elastomers using FEM: Do’s and Don’ts
- 2016.10.10 Tips & Tricks for FEA Modeling of Rubber and Elastomers - Part 2
- 2016.10.10 Tips & Tricks for FEA Modeling of Rubber and Elastomers - Part 1
- 2016.06.24 bsxfun
- 2016.06.06 폴더 이름 변경이 갑자기 되지 않을때...
- 2016.04.15 Create Function
- 2016.04.15 fzero
- 2016.03.30 Adress
function DragDropTest
%
% Example Drag and Drop in Matlab Figures from Windows Explorer or Other Apps
%
% DrapDropTest creates a simple figure which shows the implementation of dnd using activex.
% The microsoft RichtextCtrl.1 activex control is used to demonstrate dnd ability. The control
% has several events to which matlab can respond, in particular the OLEDragDrop Event.
%
% Type DragDropTest from the command line to test. Once the figure is
% running try dragging a text file into either of 2 areas on the figure.
% The upper portion will just populate a listbox with the names of files
% that have been dragged into the bar above it. The lower box displays the
% contents of any text file dragged into it. The bottom box also allows
% text to be dragged from a text editor such as wordpad.
%
% This example is not intended to be robust, so please feel free to use it,
% but make sure to check over the code in detail to make sure it doesn't
% break. I've just coded this quickly to demonstrate the property. Feel
% free to email me with questions comments.
%
% Raphael Austin
% raphael.austin@jhuapl.edu
%
% Last Updated: 9/10/2007
f=figure;
pos=get(f,'position');
color=get(f,'color');
%use this one to put a file name into a box
uicontrol('style','listbox','position',[pos(3)*.1 250 pos(3)*.8 100],'tag','FileNameList');% create a listbox to show filenames
ProgID='RICHTEXT.RichtextCtrl.1';
h1 = actxcontrol(ProgID, [pos(3)*.1 355 pos(3)*.8 20],f,{'OLEDragDrop',@ShowFileNameOnDrop});
set(h1,'OLEDropMode','rtfOLEDropManual');
set(h1,'text','Drag file into this window to populate the list with filenames...')
uicontrol('style','text','string','File Name Loader','position',[pos(3)*.1 375 pos(3)*.8 20],...
'backgroundcolor',color,'fontweight','bold');
%use this one to drag text from a word pad document or explorer
ProgID='RICHTEXT.RichtextCtrl.1';
h2 = actxcontrol(ProgID, [pos(3)*.1 20 pos(3)*.8 180],f,{'OLEDragDrop',@ShowFileContentsOnDrop});
set(h2,'OLEDropMode','rtfOLEDropManual');
set(h2,'text','Drag text file into this window for preview...')
uicontrol('style','text','string','Text File Preview','position',[pos(3)*.1 200 pos(3)*.8 20],...
'backgroundcolor',color,'fontweight','bold');
end
function ShowFileNameOnDrop(varargin)
hObject=varargin{1};
Interface=varargin{3};
try
data=Interface.GetData(1);
catch
data=Interface.get.Files.Item(1);
end
set(hObject,'text',data);
list=findobj(gcf,'tag','FileNameList');
Str=cellstr(get(list,'string'));
Str(end+1)={data};
set(list,'string',Str);
end
function ShowFileContentsOnDrop(varargin)
hObject=varargin{1};
Interface=varargin{3};
try
data=Interface.GetData(1); %this works if its just text copied from one rtf into an rtf box
catch
data=Interface.get.Files.Item(1); %this works if its a file dragged from explorer over the rtf box
fid=fopen(data);
filecontents=fscanf(fid,'%c');
fclose(fid);
data=filecontents;
end
set(hObject,'text',data);
end
http://kr.mathworks.com/matlabcentral/fileexchange/16312-drag-and-drop
Elastomers are increasingly used in industrial applications and understanding their mechanical behavior is even more important than earlier. Tires being one of the largest application of rubbery materials, some of the other very common industrial applications include seals, bearings, dampeners, O-rings etc.
O-rings were invented in the 1890s and used to seal fluids. O-rings are almost present in all industrial and commercial applications and work on the concept of balancing the fluid pressure with the contact stresses. As the fluid pressure increases the O-ring is compressed in the direction normal to the fluid surface as shown in Fig. 01. Elastomers being incompressible, they expand in the transverse direction to increase the contact stresses and effectively seal the interface. The sealing does not fail as long as there is no mechanical failure of the O-ring. This is one of the primary reasons they are still widely used.
Fig 01: O-ring subjected to fluid pressure. The fluid is stopped by the O-ring in (a). As the fluid pressure increases in (b) and (c), the O-ring is pushed in to increase the contact stress and seals the interface.
In this article, we discuss a series of tips for modeling elastomeric materials using the Finite Element Method (FEM) to improve the accuracy and reliability of obtained solutions.
Choosing the right material model for the elastomers
Elastomeric and rubbery materials typically demonstrate:
- Isotropic and elastic behavior without any permanent set (like plasticity)
- Nonlinear stress-strain behavior as shown in Fig 02.
- Different tensile and compressive behavior and comparatively softer in tension
- Nearly incompressible behavior with Poisson ratio around 0.4999
Fig 02: Typical nonlinear stress-strain behavior observed in elastomers
Most of these characteristics are captured well through Hyperelastic models and depending on the material behavior a suitable model should be selected. The material parameters are obtained through experiments like uniaxial & biaxial tensile test, uniaxial compression test, planar & simple shear and volumetric test. A more detailed discussion on the selection of hyperelastic material model can be found on the SimScale blog.
Tip 01: Using the parameters highlighted in this blog article, choosing the right hyperelastic material model is half the job done well.
Meshing the structure
At present, SimScale allows for the meshing of the structures with Tetrahedrons. Hence, in this article, we will limit the discussion to meshing 3D structures with tetrahedrons. A general overview on meshing & meshing tutorial is available in the SimScale documentation. Presently, SimScale allows tetrahedral meshing with following options:
- Automatic
- Parametric
- Tetrahedral with local refinement
As shown in Fig. 03, all these cases allow for the specification of mesh order: first or second. Using a first-order generates a mesh with four-noded tetrahedral elements and second-order a mesh with ten-noded tetrahedral elements. For more detailed tips on meshing for structural mechanics problems, watch out for upcoming articles.
Fig 03: Order of interpolation
Tip 02: For most elastomeric structures second order would be the safe choice. However, in some cases, a first-order mesh could also be sufficient and save significant computational time.
Considering geometry & loading
The dimensions of the structure also play a pertinent role in the accuracy of solutions obtained. Many of the applications of elastomers, like conveyor belts, have one or more dimensions (like length & breadth) much larger than the others (thickness).
For example, as shown in Fig. 04, if the thickness and breadth of the structure are much larger than its length, then it can be considered as a beam. Similarly, if the thickness is much smaller than both length & breadth, then the structure can be considered as a plate or shell. If all the dimensions are comparable, then the structure can be considered to be a full solid. Irrespective of the structure type, solid elements are being used to mesh the structure. Thus, is becomes important to understand the form of a structure being considered so that effective meshes can be generated.
Fig 04: Illustration of beam, plate, shell & solid structures
It is important to first identify the category of the structure. For solid structures, the automatic tetrahedral meshing can be directly used and both the first and second order could yield good results. However, the complexity arises for structures that resemble beams / plates / shells.
Secondly, in addition to geometry, it is also important to identify the type of loading these structures are subjected to. For example, the O-ring illustration shows that the loading on the elastomer structure is of bending-type in nature.
When the structures are of the form of beams-plates-shells, they can be considered as thin structures. These thin-structures demonstrate a locking effect (well known as shear locking) especially when a first-order mesh is used and structure is subjected to bending loads. The easiest way to circumvent the shear locking is through mesh refinement or using higher-order elements. A more detailed discussion on the shear locking is dealt in detail in our upcoming blog article on meshing tips for structural mechanics problems.
Tip 03: If you are using a solid structure, first-order might still work. If the structure can be classified as one of the thin structures and/or subjected to bending loads, then second-order mesh is strongly recommended.
Dealing with incompressibility in elastomers
Most elastomers and rubbers have a Poisson ratio of almost 0.5. Physically, this means that when the material undergoes elongation in the x-direction, then there is enough compression in the other two directions such that the initial and final volumes remain same. Note that a Poisson ratio of 0.5 is equivalent to saying that the Bulk modulus is infinity.
Fig 05: Relation between bulk modulus a young’s modulus. As Poisson ratio reaches 0.5, bulk modulus tends to infinity
Or otherwise, this means that it would take an infinite amount of energy to compress the material. To get a feel of the idea, one could consider water. Water is a perfect example of an incompressible material. If one would fill a can with water and try to compress, it can be seen that the volume of water remains unchanged. So one could say that the bulk modulus of water is almost infinity. Since infinity cannot be used numerically, a very large bulk modulus is used to signify Poisson ratio tending to 0.5.
When the bulk modulus is considered such that the Poisson ratio is larger than 0.4, most normal elements show a locking effect. This is commonly known as volumetric locking. Unlike the earlier discussed shear locking, volumetric locking cannot be circumvented through mesh refinement. Volumetric locking is not only common to elastomers but also pertinent to any elastoplastic material.
There are several approaches available in the literature:
- Selectively reduced integration (B-Bar method)
- Uniformly reduced integration (or more commonly just known as reduced integration)
- Enhanced strain formulation
- Mixed formulations
First, it would be important to understand the cause of this volumetric locking before finding a solution. Considering a simple example of a loaded structure made of elastomer in 2-D, as shown in Fig 05, the cause of volumetric deformation is observed. The mesh is made of two triangles (or could be one quadrilateral either) with linear interpolation (first-order mesh). A small force (or alternatively displacement) is applied on the free node (node number 01) along the direction of 45-deg.
Fig 05: Illustration of volumetric locking
Since the material is volume preserving and the elements use linear interpolation (i.e. lines 1-2 and 1-4 need to be straight), the only direction the free node can move is along the circle shown in red color. However, this would mean moving perpendicular to the effective reaction force and such a motion cannot be allowed. Eventually, the only possible solution is the trivial solution of nodal displacements being zero (or very small numerically). This is clearly disastrous!
One of the simplest ways to solve the problem is using second (or higher) order elements. When second-order elements are used, the edges do not need to be straight anymore. This would facilitate motions that could lead to non-zero nodal displacements and still conserve the volume. However, as the Poisson ratio approaches 0.499, 0.4995 etc, even the second-order elements do not behave well. To understand this behavior of second-order elements, it is important to understand the mathematics behind the interface.
In problems involving elastomers (or nonlinear FEM), matrix equations [K]{u} – {f} = {R} are solved such that {R} tends to zero. The stiffness matrix [K] is first computed locally for each element and then assembled to a bigger global system. Locally, in each element, [K] is computed at fictitious points commonly known as Gauss (or integration) points. The above problem with second-order elements is caused since the volumetric strain is being enforced to be zero at all of these integration points. The total energy from volumetric strain can be approximately written as a product of Bulk modulus x (volumetric strain)^2. Since the bulk modulus is very large, even a small volumetric strain can lead to large extra addition to the energy. This renders the total equation system to behave very stiff and the solvers more often converge to the trivial solution (of zero displacements).
An alternative and very commonly used approach, also incorporated in SimScale, is using reduced integration with second-order elements. This means that the deviatoric strains are computed as earlier but the zero volumetric strain is enforced only at certain points. Though this might sound to be inaccurate, reduced integration has been observed to be extremely robust and yield quite accurate solutions across a wide range of Poisson ratio.
Note that first-order tetrahedrons use only one integration point and thus a reduced integration with these elements is not possible.
Tip 04: If the Poisson ratio is less than or equal to 0.4, first order elements can be used. For Poisson ratio’s even up to 0.45, second-order tetrahedrons could work well. For much higher Poisson ratios, it is strongly recommended to use second-order elements with reduced integration.
Force vs. displacement boundary condition for modeling elastomers
One of the common causes of non-convergence is unbalanced residuals. When modeling elastomers, the system of equation being solved is nonlinear, i.e. [K(u)] {u} – {f} = {R}. Here the stiffness matrix [K(u)] is a function of the unknowns {u}. Thus, small displacements / forces are applied in small increments to reach the desired value.
Using smaller time steps (i.e. smaller force increments) can significantly improve the convergence properties. Alternatively, if possible, displacement controlled boundary conditions are most likely a safe option. As shown in Fig 05, where a very highly nonlinear problem is considered, for every displacement there is a unique solution of the force. However, the same is not true vice-versa.
Fig 05: Nonlinear force-displacement curve showing that for a particular force there can be multiple displacements (or non-unique solution). But for each displacement, there is only one force (or a unique solution).
This means that when a force boundary condition is applied, it need not lead to a unique displacement. Such non-uniqueness can easily lead to a lack of convergence. Alternatively, using a displacement boundary condition can likely lead to better convergence. In such cases, advanced techniques like line search etc are employed to improve the overall convergence of the system. Watch out our SimScale blog for the upcoming article related to solvers for structural mechanics problems that will delve more into areas like line search etc.
Tip 05: If possible, use displacement boundary conditions.
Convergence issues
There are several reasons why a simulation can fail and show a lack of convergence. Some of the very common ones pertaining to elastomers include, but not limited to,
- Material instability
- Time step size
- Inelastic effects
Material instability
The material parameters are generally obtained by fitting the experimental data. The fitting is limited by the maximum stretch to which the data is available. If the model is used beyond this limit, the model might not be unconditionally stable.
For example: Say if the data was only available for a stretch to 30% and the model parameters were fitted with this. When a simulation is done using this model where the strains are much larger (> 30%), it is possible that the nonlinear behavior beyond 30% is not accurately captured.
Secondly, depending on the number of tests used for fitting, it is possible that the material demonstrates an instability when subjected to a different type of loading. For example: Say material parameters for Mooney-Rivlin model are fitted using only uniaxial tests. When a biaxial simulation is done, it is possible that the results show significant instabilities.
A possible solution to this would be to test the material model with uniaxial, biaxial, shear, volumetric tests for up to failure limits. Using these simulations, possible points of material instabilities can be identified a priori.
Time step size
The second possible reason for the lack of convergence can be time step size. If a manual time step is used and if the time step is too large then it can lead to a lack of convergence. SimScale allows for auto time-stepping and it is recommended to use auto-stepping.
Fig 06: Screenshot for auto time stepping
As shown in Fig. 06, a retiming event is used to kick-in to reduce the time step. When the time step is too large and leads to non-convergence, this kicks in a retiming event. In such a case, the time step is reduced and the simulation restarts from the last converged time step. This significantly reduces the failure of simulations. There are several options available for time step calculation type and “Newton Iterations Target” option is a good place to start.
Inelastic effect
In this article, we have considered the elastomers to be purely hyperelastic and we will discuss the effects of inelasticity in an upcoming blog article
Tip 06: Check the material parameters thoroughly for instability before using it under general loading conditions. Auto time stepping is a great option to prevent failure of simulations!
Overall, summarizing the type of problem or procedure, types of element recommended and to avoid are:
- Bending & thin structures: second-order (recommended), first-order (avoid)
- Nearly incompressible (Poisson ratio > 0.45): second-order with reduced integration (recommended), second-order with fully integrated (avoid)
- Very large deformation: second-order (recommended), first-order (avoid)
- Boundary condition: displacement (recommended), force (avoid)
- Timestepping: auto (recommended), manual (avoid)
Last week, in Part 1 of this post, I discussed three tips to consider when solving a detailed stress analysis of an O-ring or seal, including: material testing, material law selection, and testing of the selected material law . This week, I'll discuss four more tips for enhancing the accuracy and convergence of your simulation!
4) Element Formulation: Selecting the best element formulation is another key modeling decision, especially when analyzing parts in compression where element locking is of concern. Mike Bak’s blog “Dealing with Incompressibility” provides excellent guidance to follow for these types of analyses.
5) Mesh: With hyperelastic materials, the deformed element shapes are more important than the initial element shapes. Plan for the deformation by skewing the undeformed mesh to distort into more of a regular pattern. Lower order elements are more stable, and often an all-triangular lower order mesh is recommended to overcome excessive element distortion. A finer mesh might not always be better, since small elements in the areas of peak strain often become more distorted than with a coarser mesh and thus are more susceptible to element failure. Consider rezoning if excess element distortion cannot be avoided in the undeformed mesh. Figure 3 above illustrates an axisymmetric seal simulation where automated progressive rezoning is used to capture the significant seal distortion and provide the accurate refined mesh in the final stages of the simulation.
6) Load control: Use a displacement controlled solution if possible, and force a large number of sub-steps since cumulative unbalanced residuals are a common cause of non-convergence. By using small load steps, one can minimize these errors and accurately track the large deflections and material nonlinearities.
7) Adjust the volume compatibility constraint: This is typically an analysis control parameter that allows for some error in volumetric compatibility. In ANSYS, the default for the Vtolparameter is 1e-5. Adjusting this parameter on the ANSYS SOLC command to a value as low as 1e-2 can sometimes be the key in overcoming convergence issues when large compressive strains are encountered.
What challenges have you overcome when modeling rubber materials? I would love to hear other tips and tricks for solving these complex analyses.
https://caeai.com/blog/tips-tricks-fea-modeling-rubber-and-elastomers-part-2
Are you having problems solving a detailed stress analysis of an O-ring or seal? This post provides a series of tips for enhancing the accuracy and convergence of your simulation.
Materials such as rubber or elastomers are typically modeled with Hyperelastic constitutive models because they typically exhibit the following characteristics:
- By definition, the material behavior is elastic, where there is no permanent set, and the material loads and unloads up and down the same stress-strain curve.
- The relationship between stress and strain is highly nonlinear and typically softer in tension vs. compression. The tension portion of the stress-strain curve often has an initial softening slope before significant stiffening, while the compressive part of the curve is quite a bit stiffer. (See Figure 1 above.)
- There is little volume change in the material and thus it acts as either fully or nearly fully incompressible. This would be equivalent to setting Poisson’s ratio to 0.499.. in a linear elastic model, which creates an incompressible material response.
- The material response is isotropic and isothermal (stress vs. strain and thermal expansion coefficients are the same in all directions)
Obtaining both an accurate and converged solution in any nonlinear analysis is a challenge. Here are my top three tips, in order of importance, specifically associated with modeling hyperelastic materials. I’ll reveal four more tips in Part 2 of this post, so stay tuned!
1) Material Testing: Accurate material test data is a must when simulating the large strain response of rubber and elastomer materials. At least two material tests from the list below are needed to get good calibration between test and computer model.
- Uniaxial Tension
- Uniaxial Compression
- Biaxial Tension (Circular or rectangular specimen)
- Planar Shear
- Simple Shear
- Volumetric Test (Button specimen)
The test data should represent, as closely as possible, the in-situ material properties. Because, manufacturing processes, such as the rate of injection molding, can change the final material characteristics.
2) Material Law Selection: There are many materials laws available to simulate hyperelastic materials using finite elements. Some of the more common laws include Mooney-Rivlin, Ogden, Yeoh, Blatz-Ko, Arruda-Boyce. Selecting the best material law plays an import role in the success of your analysis. Select a material law with the best curve fit over the range of expected stresses and strains. This topic has been discussed in a previous CAE Associates Blog post. Selecting the best material law can be a bit of trial and error process using test data curve fit compatibility and solution robustness (see item 3 below) as selection criteria.
I would suggest starting with the simpler laws first, such as the two term Mooney Rivlin, and also be cognitive of the expected strain levels in your simulation. For example, if you don’t expect any strains to exceed 30%, there is no reason to look to match strains at 300%, since these will never be encountered in the real problem. Some FEA codes have automated curve fitting capabilities that can be used to quickly test a number of different laws and automatically determine the necessary law coefficients. ANSYS Workbench’s engineering data curve fitting is illustrated in Figure 2, where four laws are compared with each being the better fit to test data, depending on the anticipated simulation response.
![]() |
3) Test the Material Law: The one element test case should be used to determine the robustness of the material model by imposing tension, compression and shear loads on both regular and irregular single element shapes. When comparing to test data be sure to convert the test data from engineering to true stress / log strain for direct comparison with FEA results. Comparing the convergence efficiency between multiple material models on the single element model can be the deciding factor when more than one material law might fit the test data adequately by saving significant CPU time and convergence headaches with the real model.
Watch for Part 2 of this post. Tips 4 - 7 will include some great information about element formulation, meshing and loading. If you have any of your own tips, please share them below in the comments!
https://caeai.com/blog/tips-tricks-fea-modeling-rubber-and-elastomers-part-1
Syntax
C = bsxfun(fun,A,B)
Description
C = bsxfun(fun,A,B)
applies the element-by-element binary operation specified by the function handle fun
to arrays A
and B
, with singleton expansion enabled. fun
can be one of the following built-in functions:
fun = @(A,B) A.*sin(B); A = 1:7; B = pi*[0 1/4 1/3 1/2 2/3 3/4 1].'; C = bsxfun(fun,A,B)
폴더를 찾을 수 없다는 둥... 권한이 없다는 둥..
갑자기 폴더 이름 변경이 되지 않을때..
HKEY_LOCAL_MACHINE\SOFTWARE\Microsoft\Windows\CurrentVersion\Explorer\FolderDescriptions\
에서 아래 항목 삭제 후 재부팅
{2112AB0A-C86A-4ffe-A368-0DE96E47012E}
{491E922F-5643-4af4-A7EB-4E7A138D8174}
{7b0db17d-9cd2-4a93-9733-46cc89022e7c}
{A302545D-DEFF-464b-ABE8-61C8648D939B}
{A990AE9F-A03B-4e80-94BC-9912D7504104}
Create Function Handle
You can create function handles to named and anonymous functions. You can store multiple function handles in an array, and save and load them, as you would any other variable.
What Is a Function Handle?
A function handle is a MATLAB® data type that stores an association to a function. Indirectly calling a function enables you to invoke the function regardless of where you call it from. Typical uses of function handles include:
Pass a function to another function (often called function functions). For example, passing a function to integration and optimization functions, such as integral and fzero.
Specify callback functions. For example, a callback that responds to a UI event or interacts with data acquisition hardware.
Construct handles to functions defined inline instead of stored in a program file (anonymous functions).
Call local functions from outside the main function.
You can see if a variable, h, is a function handle using isa(h,'function_handle').
Creating Function Handles
To create a handle for a function, precede the function name with an @ sign. For example, if you have a function called myfunction, create a handle named f as follows:
f = @myfunction;
You call a function using a handle the same way you call the function directly. For example, suppose that you have a function named computeSquare, defined as:
오늘부터 address가 들어간 표현을 연습합니다. address 역시 원어민들이 하루에도 여러 번 쓰는 표현입니다. 먼저 address는 발음을 잘하셔야 합니다. address는 명사로 '주소, 연설' 동사로는 '주소를 쓰다, 말을 걸다’라는 의미로 쓰이죠. address가 명사로 쓰일 경우에는 첫 음절이나 둘째 음절에 강세가 올 수 있지만, 동사일 경우에는 둘째 음절에 강세가 있지요. 구체적으로 동사로 ‘address someone as ~’라고 하면 ‘누구를 ~라고 부르다’라는 뜻의 숙어로 이때는 address의 둘째 음절에 강세가 옵니다. 즉, /어드뤠쓰/라고 발음을 하고, ‘my address is’라고 할 때처럼 address가 명사로 쓰이면 /애드레스/라고 발음을 해야 자연스럽죠.
영영사전을 통해서 address의 의미를 먼저 정리해 봅니다.
(동사)
1. to write or print on an item of mail details of where it is to be delivered (주소를 쓰다)
2. to say something to somebody, or make a speech to an audience (연설하다)
3. to set about doing some task (~을 준비하다)
4. to face up to and deal with a problem or issue (문제나 이슈를 다루다, 처리하다)
(명사)
1. the number, street name, and other information that describes where a building is or where somebody lives (주소)
2. a formal speech or report (연설)
3. a number that specifies a location in a computer’s memory (컴퓨터 기억장치 내에 있는 정보 위치를 알려주는 번호)
함께 address가 들어간 문장을 봅니다.
1. Would you please fill this form, giving your full name and address?
해설: address는 ‘주소’를 의미합니다. fill this form은 ‘이 서류를 작성하다’라는 뜻입니다.
번역: 이 서류에 귀하의 주소와 성명을 기입해 주십시오.
2. You have to get a request for address change.
해설: address change는 ‘주소 변경’이란 의미입니다. 주소변경 시에는 ‘Could I have a change of address form? (주소 변경 신고서 좀 주십시오.)’라고 하면 됩니다. 예를 들어 주소가 바뀌면 교통국이나 전화국 또는 수도국에 연락을 해서 ‘주소 변경 신고’를 해야 합니다.
번역: 주소 변경을 요청해야 합니다.
3. Don't forget to put your address on the letter.
해설: 요즘은 terror 사건이 많이 일어나기 때문에 post office에서 ‘발신인 주소’를 꼭 적으라고 하죠.
번역: 발신인 주소 적는 것 잊지 마세요.
4. Well, he might ask you your name, hobby, age, current address and so on.
해설: 여기서 말하는 current address는 말 그대로 현재 살고 있는 주소인 ‘현주소’를 말합니다. 전세계 도시인들은 여러 가지 이유로 current address가 자주 바뀝니다. current address를 종종 mailing address라고 하기도 합니다. 즉, ‘연락 받을 수 있는 주소’를 말하죠. 덧붙여 and so on은 ‘기타 등등’이라는 의미로, and so forth와 유사합니다
번역: 음, 아마 그는 당신의 이름과 취미, 나이, 현주소 등을 물어볼 거에요.
5. Excuse me, how do I address you?
해설: business 석상에서 또는 일반 회화에서 어떤 사람을 소개 받았을 때 상대에게 “어떻게 불러야 하나요?”라고 할 때는 How do I address you?라고 합니다. 예를 들어 상대의 이름이 Mr. William Hartmann이라고 할 때 그 사람에게 How do I address you?라고 하면 William Hartmann이란 사람은 “Just call me Bill. (그냥 Bill이라고 불러 주세요.)”라고 할 수도 있지만 “Call me Mr. Hartmann”이라고 “하트만 씨라고 불러주세요.”라고 formal하게 대답할 수도 있죠. 참고로, ‘How do I address you?’는 ‘What would you like to be called?’ 또는 ‘What do you want me call you?’라고도 쓸 수 있습니다.
번역: 실례하지만, 어떻게 부를까요?
6. I'd like to send a bouquet of flowers to this address.
해설: 꽃 배달 서비스를 원할 때 쓰면 제격이네요.
번역: 이 주소로 꽃다발을 보내고 싶습니다.
7. I'll tell you his birthday and address for the future reference.
해설: 이 문장에서 중요한 표현은 ‘for the future reference’입니다. ‘앞으로 도움이 될 수 있다’는 의미로, reference는 ‘참고’ 또는 ‘참고서’라는 의미입니다.
번역: 앞으로 도움이 될 지 모르니 그의 생일과 주소를 알려 드릴게요.
8. You have to be very cautious in giving your address to strangers.
해설: strangers는 ‘낯선 사람’, be cautious는 ‘주의하다’ 또는 ‘신중을 기하다’라는 뜻입니다.
번역: 낯선 사람들에게 주소를 알려 줄 때는 특히 주의하셔야 합니다.
9. I don't know my address yet. But I'm going to stay at a hotel in Sydney.
해설: 이 내용은 공항 출입국관리소에서 쓸 수 있는 표현입니다. 입국
란난에 보면 address가 있는데, ‘입국 후 머물 장소’를 말합니다. 호텔에
머물게 되면 위의 문장처럼 표현하면 자연스럽죠.
번역: 아직 주소는 잘 모릅니다. 하지만 시드니 호텔에 머물려고 합니다
오늘은 이런 생각을 합니다. 잘 보면 우리나라 학생들은 영어로 대화를 할 때 너무 빨리 말하려는 경향이 있습니다. 또 많은 학생들이 ‘말을 빨리 해야 영어를 잘한다’라고 알고 있습니다. 하지만 그렇지 않습니다. 우리나라도 마찬가지겠지만 지식인이나 상류층 원어민들은 말을 천천히 하는 경향이 있습니다. 하지만 어린 여학생 (10대)들이나 생활이 바쁜 원어민들 (즉, 먹고 살기 바쁜)은 대개 말이 빠르죠. 국제 뉴스에 종종 등장하는 미국의 Secretary of State (국무장관)인 Colin Powell 씨의 영어를 들어 보시면 이해가 되실 겁니다. (미국이나 기타 영어권의 유명 교수들이 말하는 것도 주의해서 들어 보세요.)
결론입니다. 영어로 말을 할 때는 천천히 하세요. 빨리 말을 한다고 영어실력이 있는 것이 아닙니다. 논리적으로 문법에 맞게 천천히 점잖게 하세요.
10. The man on the right derogatorily addressed him as a dirty pig.
해설: 우리나라에서 ‘돼지꿈’은 길몽입니다. 하지만 원어민 사이에서 pig은 좋지 못한 의미로, ‘욕’에 가깝습니다. derogatorily는 ‘경멸적으로’라는 뜻이죠.
번역: 오른쪽에 있는 사람이 그에게 ‘더러운 돼지 새끼’라고 경멸적으로 말했어요.
11. I must have the wrong address.
해설: 외국 주소는 우리나라보다 훨씬 간단합니다. 예를 들면 ‘19 Cleveland st. Stones Corner Brisbane (Brisbane 시, Stone Corner라는 동네의 Cleveland가 19 번지)’ 처럼이요. 그래도 주소를 잘 못 찾을 것 같다면 ‘I must have the wrong address.’라는 표현을 익혀 두면 되겠죠?
번역: 제가 주소를 잘못 알고 있는 것 같군요.
12. Who’ll be the speaker in the opening address?
해설: 여기서 opening address는 ‘개회사’입니다.
번역: 개회사는 누가 하나요?
13. Please ascertain his present address.
해설: 여기서 ascertain은 ‘~을 확실하게 하다’ 또는 ‘~을 명백하게 하다’는 의미입니다.
번역: 그의 현주소를 확인해 주세요.
14. All future communications should be made to the new address mentioned above.
해설: 건물이나 사무실을 이전한 후에 이전 사무실에 붙여 놓을 수 있는 문구입니다.
번역: 차후 모든 연락은 상기 새 주소로 해 주기 바랍니다.
15. Lincoln's address on the battlefield of Gettysburg.
해설: 링컨 대통령이 Gettysburg에서 했다는 연설은 전세계적으로 유명한 내용이죠. 이때 address는 ‘연설’이라는 뜻입니다.
번역: 링컨 대통령의 게티스버그 연설
16. Take me to this address, please.
해설: taxi 기사 아저씨에게 주소를 보여주면서 쓸 수 있는 표현입니다. 이와 유사한 표현으로는 ‘Do you know where this address is?’라고 할 수 있죠.
번역: 이 주소로 가 주십시오.
저는 “영어를 영어권에서 배우는 것이 더 좋은가요, 아니면 국내에서 배우는 것이 더 좋은가요?”라는 질문을 자주 받습니다. 5~6년 전만 해도 ‘영어는 영어권에서 배우는 것이 훨씬 효과적이다’라는 생각이 지배적이었습니다. 하지만 많은 학생들이 영어권에 가도 큰 효과를 얻지 못하는 경우가 많고, 심지어 일부 유학생들은 방학을 이용해서 우리나라로 역유학을 와서 영어를 배운다죠? 그래서인지 ‘영어를 어디서 배워야 하나?’라고 갈등하시는 분들이 많은 것 같습니다.
제가 우리나라에서 영어를 강의하면서 (1995-2000) 느낀 점과 요즘 호주에서 영어를 강의하면서 느낀 점을 말씀 드리면, 나름대로 장단점이 있습니다. 예를 들어 우리나라는 영어교재가 정말 풍부합니다. 미국이나 호주 등에서는 TOEIC이나 TOEFL, 영어 회화책을 찾기가 매우 힘이 들죠. 하지만 영어권 나라에서는 책에서 배우지 못하는 ‘영어권 문화’를 배울 수 있고, ‘백인 공포증’을 자연스럽게 없앨 수 있습니다.
결론입니다. 영어교재와 영어방법론에서는 우리나라가 세계 제일이지만 현장학습으로는 영어권 국가가 좋습니다. 가능하면 둘 다 경험하는 것이 좋습니다.
계속해서 address입니다.
17. The governor delivered his address from the amphitheater.
해설: governor는 ‘주지사’이고, amphitheater는 ‘원형 극장’을 말합니다. 특히 ‘연설을 하다’라고 할 때 동사 deliver를 쓴다는 것에 주의하세요.
번역: 그 주지사는 원형 극장에서 연설을 했다.
18. The receiver’s name and address should be here.
해설: 편지를 자주 쓰지 않는 분들은 수신자 (receiver) 주소와 발신자 (sender) 주소 쓰는 곳을 모르는 경우가 종종 있습니다. 이럴 때 쓸 수 있는 문장입니다.
번역: 수신자 이름과 주소를 여기에 쓰세요.
19. US Government has insisted on addressing the matter of nuclear facilities in Iraq.
해설: insist on은 ‘~을 주장하다’는 의미입니다. 전치사 on을 쓴다는 것에
것에 주의하세요. ‘nuclear facilities’는 ‘핵시설’이라는 뜻입니다.
번역: 미국 정부는 이라크의 핵시설 문제를 다룰 것을 주장했다.
20. What's the best way to get to this address?
해설: 이 표현은 주소를 물을 때 사용하면 자연스럽습니다. ‘what’s the best way to ~ ?’라는 표현도 꼭 익혀 두세요. 예를 들어 ‘What’s the best way to cook Ramyon?’이라면 ‘라면을 가장 맛있게 끓이는 방법이 뭐에요?’라는 의미가 되죠.
번역: 이 주소로 가려면 어떻게 가야 하나요?
21. Would you care to address this rumor?
해설: 사실무근의 소문이 돌아 다닐 때 그 소문의 주인공에게 물어 볼 수 있는 질문입니다.
번역: 이 소문에 대해 말씀 좀 해 주시겠습니까?
오늘은 이런 생각을 해 봅니다. 제가 우리나라에서 5년간 영어를 강의하면서 느낀 점은 ‘우리나라에서는 무조건 미국 영어가 우선시 되고 있고, 영어실력은 TOEIC과 TOEFL 점수로 대변된다’라는 거였습니다. American English 등을 강조하다 보니 미국의 yangachee들이나 쓰는 저속한 street talk 표현 등을 모아서 만든 책 (책이라고 말하기도 뭐하지만)들이 시중 대형서점에서 버젓이 잘 팔리고 있고, 또 그 내용을 internet 영어 site에서 강의까지 하고 있더군요. 미국에서 오래 살았던 분들은 아시겠지만 사실 ‘street talk’은 일반적인 미국인들의 경우도 못 알아 듣는 경우가 종종 있습니다. 그리고 굳이 그런 말을 알아 들을 필요도 없지 않나요? 우리나라 말에도 그런 식의 표현들이 분명히 있을 겁니다. 하지만 일반인들이 그런 ‘뒷골목’의 우리말을 배울 필요가 있나요? 그리고 그런 저속한 우리말을 자주 쓰나요? 잘 생각해 봐야 합니다.
다음, 우리나라에서는 TOEIC 점수나 TOEFL 점수가 영어실력을 대변한다는 것 이 역시 문제가 있습니다. 예를 들어 미국 정규대학에서는 일반적으로 TOEFL 550 이상 (paper test 기준) 이상을 요구합니다. 이것은 TOEFL 550점 이상이면 대학에서 공부를 하는데 아무 지장이 없다는 것 외에는 아무 의미가 없습니다. 다시 말해서 TOEFL 600점이건 550점이건 똑같다는 거죠. 하지만 우리나라에서는 TOEFL 600점을 받은 사람이 550점을 받은 사람을 무시합니다. “내가 너보다 50점이나 위야.”라고 하면서요. 정말 웃기죠?
결론입니다. 미국 영어가 영어를 대표하는 것도 아니고, TOEIC이나 TOEFL 점수가 영어실력을 대변하지도 않습니다. 영어는 단지 한국어를 모르는 외국인들 만났을 때 그들과 의사소통을 하기 위한 국제적인 언어 도구일 뿐입니다.
오늘까지 address를 살펴 보겠습니다.
22. You have to write nothing but the address here.
해설: nothing but은 only의 의미입니다.
번역: 여기에는 주소만 쓰셔야 합니다.
23. You could bill me at the above address.
해설: ‘상기주소’를 above address라고 하면 자연스럽죠. 이력서나 서류 작성 시 같은 주소를 여러 번 반복해서 써야 하는 경우가 있습니다. 이런 경우 우리나라에서는 ‘상동’이라고 합니다. 영어로는 ‘As above’라고 하면 자연스럽습니다. 즉, As above라고 하면 ‘위에 명시한 주소와 같습니다’라는 의미가 되죠.
번역: 위의 주소로 계산서를 보내 주세요. (요금을 청구하시면 됩니다.)
24. Your letter of March 16 addressed to Mr. Steve Myer has been passed on to me for action.
해설: business letter에서 자주 볼 수 있는 표현입니다. 여기서 address to는 ‘~에게 보내진’이라는 뜻입니다. 그래서 ‘a letter addressed to Mr. A’라면 ‘Mr. A에게 보내진 편지’라고 해석하면 됩니다. be passed on to me는 ‘나에게 전달되다’, for action은 ‘일을 처리하다’라는 뜻입니다.
번역: 저에게 귀하가 스티브 마이어 씨에게 보낸 3월 16일 자 편지가 와서 제가 처리했습니다.
출처 : http://www.winglish.com/free/asp/common_default_com.asp?p_type=list&b_num=954&ref_num=954&step_num=0&ans_num=0&page=58&filename=&filesize=