DEFLECTIONS AND LOAD DISTRIBUTIONS IN LINEAR ELASTIC ...
Transcript of DEFLECTIONS AND LOAD DISTRIBUTIONS IN LINEAR ELASTIC ...
- - WAPD-TM-182
AEC RESEARCH AND DEVELOPMENT REPORT
DEFLECTIONS AND LOAD DISTRIBUTIONS IN LINEAR ELASTIC STRUCTURES-CTAC AND MODE CODES
JANUARY 1960
CONTRACT AT-11-1-GEN-14
BETTIS ATOMIC POWER LABORATORY, PITTSBURGH, PA., OPERATED FOR THE U. S. ATOMIC ENERGY COMMISSION B Y WESTINGHOUSE E L E C T R I C CORPORATION
DISCLAIMER
This report was prepared as an account of work sponsored by an agency of the United States Government. Neither the United States Government nor any agency Thereof, nor any of their employees, makes any warranty, express or implied, or assumes any legal liability or responsibility for the accuracy, completeness, or usefulness of any information, apparatus, product, or process disclosed, or represents that its use would not infringe privately owned rights. Reference herein to any specific commercial product, process, or service by trade name, trademark, manufacturer, or otherwise does not necessarily constitute or imply its endorsement, recommendation, or favoring by the United States Government or any agency thereof. The views and opinions of authors expressed herein do not necessarily state or reflect those of the United States Government or any agency thereof.
DISCLAIMER
Portions of this document may be illegible in electronic image products. Images are produced from the best available original document.
WAPD-TM-182
U C - 8 0 : Reactors -Genera l
T I D - 4 5 0 0 (15th Ed.)
y *
A DEFLECTIONS A N D LOAD DISTRIBUTIONS I N LINEAR 1
ELASTIC STRUCTURES-CTAC A N D MODE CQDES
Car l M. Fr iedr ich
January 1960
Contract AT-1 1-1 -GEN-14
Price $1.50
Available from the Office of Technical Services,
Department of Commerce, Washington 25, D. C.
N V I t
This document i s an interim memorandum prepored primarily for internal reference ond does not represent a final expression of the opinion of Westinghouse. When this memorandum is distributed externally, it is with the express understanding thot Westinghouse makes no representation os to completeness, accurocy, or usability of informa- tion contoined therein. I .
BETTIS ATOMIC POWER LABORATORY PITTSBURGH, PENNSY LVANlA
OPERATED FOR THE U. 5. ATOMIC EN'ERGY COMMISSION BY ,. , :, WESTINGHOUSE ELECTRI'C CORPORATION
STANDARD EXTERNAL DISTRIBUTION
UC-80: Reactors-General , TID-4500. .15th Edition
SPECIAL EXTERNAL DISTRIBUTION
Manager . Pi t t sburgh Naval Reac to r s Operations Office, AEC Carnegie Institute of Technology, C. Zorowski Westinghouse Patent Department, E a s t Pit tsburgh, D. J. Smith Westinghouse Resea rch .Laborator ies , N. C. .Small
No. Copies
585.. .,
Total 591
cL[CAL NOTICE
T h i s r e p o r t was prepared as an account o f Government sponsored work. N e i t h e r . t h e Un i t ed S ta tes , nor t h e Commission, n o r any person a c t i n g on beha l f o f t he Commission:
A. Makes any w a r r a n t y o r r e p r e s e n t a t i o n , exp ressed o r i m p l i e d , w i t h r e s p e c t t o t h e accuracy, comple teness, o r u s e f u l n e s s o f t h e i n f o r m a t i o n c o n t a i n e d i n t h i s r e p o r t , o r t h a t t he use o f any i n f o r m a t i o n , appa ra tus , method, .or process d i s c l o s e d ' i n t h i s r e p o r t may n o t i n f r i n g e p r i v a t e l y owned r i g h t s ; o r
0. Assumes any l i a b i l i t i e s w i t h r e s ~ e c t t o t h e use o f , o r f o r damages r e c u l t i n g f r om the use o f any i n fo rma t i on , apparatus, method, o r process d i s c l o s e d i n t h i s r epo r t .
As used i n . the above, "person a c t i n q on b e h a l f o f t h e Commissionn inc l~rdc ts any employe o r c o n t r a c t o r o f t h e Commiss ion, o r employe o f such c o n t r a c t o r , t o t h e e x t e n t t h a t such employe n r c n n t r a c t n r of t h e Commicsion, g r oqp loye o f auch c r ~ r ~ t ~ - i l ~ : t ~ ~ r ~ ~ r e l r a r e s , d l s s e m l - nates , o r p r o v i d e s access t o , any i n f o r m a t i o n ,pursuant t o h i s employment o r c o n t r a c t w i t h t he Commission, o r h i s employment w i t h such c o n t r a c t o r .
CONTENTS
I. INTRODUCTION
11. FORCE, DEFLECTION, AND ENERGY
A. Force
B. Working Deflection
Reciprocal Theorem
Castigliano's Theorem
Structure Position
C. Strain Energy
Beam Energy
Cantilever Beam
Simple Support Beam
Transformat ion f r o m Cantilever t o Simple Support
111. SYSTEMATIC CALCULATION
A. Cantilever
Influence Coefficients
Energy
B. Simple Support
CTAC Rule
Flexibility
IV. APPLICATION OF CTAC
A. Structure i n WAPD-115
Given Data
Flexibility of a Subdivided F r e e Body
Total Flexibility
Redundant Load Calculation
Systematic Load Calculation
B. SO207 Code (CTAC and MODE)
Discussion
Arrangement of Decks
CTAC without MODE
CTAC and MODE
MODE Alone
Input Cards
Trans fe r C a r d s
Data Card F o r m a t
CTAC Data Deck (Input)
MODE Data Deck (Input)
Output Cards
Output Card Format
CTAC Output Deck
MODE Ch~tput. neck
Sample Problem Using Structure in WAPD-115
Printout of Cards
Resul ts
Sample Prob lem C a r d s
ACKNOWLEDGMENT
REFERENCES
Page No.
1
2
2
. 2
2 -
3
4
6
6
6
7
8
10
10
10
11
11
11
1 3
13
13
13
1 5
16
18 . .
19
2 1
2 1
2 1
2 1
2 1
22
iii
Since t h e s t r e s s a n a l y s i s o f a comp l i ca ted s t a t i c a l l y i n d e t e r - m i n a t e s t r u c t u r e i n v o l v e s t h e h a n d l i n g o f many s i m u l t a n e o u s e q u a t i o n s , t h e SO207 code f o r t h e IBM-650 was d e v e l o p e d a t B e t t i s t o s o l v e t h i s problem by t h e use o f m a t r i x t r a n s f o r m a - t i o n s . The code .has two p a r t s , each w i t h a t i t l e : f a ) the CTAC code g i v e s s t r e s s e s , d e f l e c t i o n s , and r e a c t i o n s ; and f b l t h e MODE code c a l c u l a t e s n a t u r a l f requencies and modes o f v i b r a t i o n . As an a i d t o users o f the code, a rev iew i s g i v e n o f t h e e l a s - t i c i t y and m a t r i x t r a n s f o r m a t i o n t h e o r y u t i l i z e d i n t h i s code.
DEFLECTIONS AND LOAD DISTRIBUTIONS IN LINEAR ELASTIC STRUCTURES-CTAC AND MODE CODES
C. M. F r i ed r i ch
I. INTRODUCTION
The determination of fo rces and deflections for.complicated statically indeterminate s t r u c t u r e s
involves the handling of many simultaneous equations. In o r d e r to keep t rack of the var iables and
equations in success ive s t eps of calculations, a sys temat ic routine is needed.
One such routine was developed by Gabriel Kron (Ref 1 ) f o r e l ec t r i ca l engineering problems.
This routine of ma t r ix t ransformat ions was adapted by ~ o r ~ e Langefors (Ref 2) for e l a s t i c s t ruc tu re
problems. Kron (Ref 3) later. extended Langeforsl adaptations to take c a r e of nonlinear plastic de -
formation. A thorough and detailed discussion with applications on energy principles of s t ruc tu re
analysis, including the effects of temperature and nonlinear s t r e s s - s t r a i n relations, was made by
J. H. Argyr i s (Ref 4).
Thc purpooco of t h l ~ repor t are:
1) T o give a simplified explanation of the ma t r ix t ransformat ion method f o r l inea r e l a s t i c s t r u c -
t u r e s (preceded by a review of e lementary concepts and theorems in e las t ic i ty which a r e used
i n the method). .
2) T o show the application of this method i n determining influence coefficients of s t r u c t u r e s that
may be redundant.
3) T o show how this method is applied in the CTAC code ( f i r s t par t of the Wolontis-650. code
S0207).
4) TO show'how the MODE code (second part 'of code SO2071 can be used to determine the modes
of'.vihration of a n e las t ic , s t ruc tu re .
11. FORCE, DEFLECTION, AND ENERGY
A. Force
The basis of any engineering analysis of a complicated structure is the free body diagram of
each component. Every force o r moment shown on the f ree body diagram is actually a system of
forces and/or moments which a re in equilibrium with each other.
conventional foundation shading lines on a free body diagram a r e used to indicate the remainder
of the force system acting on the body to retain it in equilibrium. For example, the forces shown
. . acting on the structures in Fig. 1A a re actually the force systems shown in Fig. 1B.
The fundamental process of analysis involves the subdividing of the free body diagram of a com-
plicated structure into two or more free bodies of simpler geometry, a s shown in Fig. 2. Care must
be taken to have the force system on each subdivided body in self-equilibrium and to have the force
systems on the subdivided free bodies actually equivalent to the force system on the original free
body, in regard to force and moment distribution throughout the body.
A. FORCES ON STRUCTURES 8. ACTUAL FORCE SYSTEMS
0 . SUBDIVIDED FREE BODIES
- - - v L
v v
M + V ( L I + L 2 ) v v + +
M
M M+ VL
v M+VL2
v
F l q . I Free trody t q ~ ~ r 1 rhr i~r rn f i g . 2 S u b d i v i s i J i i of F ree B o d i e s
In this treatment a force o r force system may be labeled by one of the forces or tinoments in the
system. Thus, a "force" may actually be a true force o r even a bending moment or a torque.
B. Working 'Deflection
Reciprocal Theorem
Considering three forces F1, F2, arid F 3 acting on a s tructurr , i f the structure is assumcd
linear-elastic, the working deflection of each force is a linear function of all forces. That is ,
DF, = A1 1 F 1 +A12 F2 +A13 Fg *
D ~ 2 = A21 F1 ' A22 F2 ' A23 F3 '
and
D ~ 3 = A31 F1 ' A32 F2 ' *33 F3
where
DFi = working deflection of F i .
A.. = influence deflection coefficient, equal to the working deflection of Fi produced by the 1.l
unit load F . = 1, and J
i , j = subscripts having values .1, 2, or 3.
A very important relationship concerning these influence coefficients can be determined by
changing the order of load applications and comparing final s t rain energies. The change in s train
energy when loads change on the linear elastic structure is , by definition of working deflections,
du l = F; d D k l + F; d D ; F ~ + F; d D k 3 , (2)
where U = strain energy of the structure and a prime i s used to denote the value of any quantity
during a change. Substitution of the deflections of Eqs (1) and (2)' gives
d ~ ' = F,: (Al1 d F; + A12 d.F; + A13 d I?;)
+ F; (AZl'd F; + A22 d F; t AZ3 d F;)
+ F; d F; + d F; + d F;) (3)
F i r s t , allow a force, say F;, to increase from zero to full vaiue F1 while the other forces
remain zero. The strain energy of the structure becomes
Next, allow another force, say F;, to increase from. zero to full value F2 while the other forces
remain unchanged. The s train energy of the structure is increased to become
If the order of load application were reversed, the total s t rain energy would be
Since'the final strain energy of a linear-elastic structure depends only on the final shape of the s t ruc-
ture a s determined by the working deflections and the final working deflections depend only -on the
final forces.according to Eqs ( l ) , then the s train energy should be independent of the order of load
applications. Equating the energies of Eqs (4 ) and (5) leads to.'the resuit that A21 = A12.
This very important result states that the working deflection of one force produced by a unit
value of a second force equals the working deflection of the second force produced by a unit value of
the f i rs t force. This relationship is known a s the Reciprocal Theorem. In general,
A . . = A , . 13' J1
for al l values of i and j.
Cagtiglianols Theorem
A useful generalization of .the energy integral can be obtained by application of the Reciprocal
heo or em., cbrresponding to Eqs ( l ) , the generalized deflection equation is
- x . A . . F . D ~ i - , j 1j j
and the generalized s train enei-gjr equation i s
U = j (Zi Fi d DFi) . Substitution of DFi from Eq (7) gives
Now, by using Eq ( 6 ) ,
- A . i F i d F . t F. dFil - 2 1~ 1~ J J
= ~ E . A . . d (Pi F:) ; 1J 1J J
o r af ter integrating and using E'q (7) .
1 1 . u = - Z . . A . . F ; F . = - C F. D . - 2 IJ 1J 1 J 2 . i ': F i ' (8)
A very important relationship can be obtained by differentiation of the s train enerby U with
respect to a force, say F1. Expansion of Eq (8) in te rms containing f i rs t gives
t h y ( + A I i F ~ + A ~ ~ F ~ F ~ * A ~ ~ F ~ F i + A ~ ~ F i F ~ t A ~ i ~ ~ ~ ~ i ) i *
s o that differentiation with respect to F1 gives
Since A. . = Aji , according to the Reciprocal Theorem; 1J
which, according to Eqs (1) o r Eq. (7). is simply Dp.l;. thus,
This resul t is known a s 'castiglianols Theorem. The pa'rtial. derivative of the s train energy of a
linear elastic system. with respect to a force equals'the woi-kin'g deflection of that force. In general,
Structurc Position
The working deflection of a force acting on a structure is actually the total working deflection
of .all components of the force systemt acting on the structure. F o r example, c ~ n e i d e r the spring
shown in Fig. 3. Suppose that while the left end moves through a distance x l , the spring force in-
c reases from 0 to full value F1 . If the spri'ng constant is K1, the total s t retch of the spring sl is
equal to F l / K l and the total movement of the right end of the spring i s xl + s l .
Tlie wdrk WL done by the left force is - L ;* -/F1 F; dx;. . 0
A. ORIGINAL POSITION
8. FINAL POSITION
F i g . 3 Changed P o s i t i o n o f a S p r i n g
and the work WR done by the r ight force is
The s t r a in ene rgy U in the sp r ing is equal to the total work done on the s t ructure . Thus,
U ,= W.L t WR
which is independent of the final position of the spring. Since sl ,= Fl /K1. then
Then, according to E'q (a), the deflection influence coefficierlt of F1 is
A l l = l / K 1 ,
s o that the working deflection of F1 i s , according t o Eq (7),
DF1 = A l l Fl = ( l / K 1 ) F 1 = s1 I
Thus, the working deflection of the fo rce s y s t e m ' F 1 is s imply the s t r e t c h of the spr ing, a s is
expected.
In general , working deflections of force sys tems acting on a l inear e l a s t i c s t ruc tu re a r e inde-
pen'hent of the final position of the s t ruc tu re and dipend only on the final deformation of the s t ruc tu re .
C. Strain Energy
Beam Energy
The influence coefficients for one sys tem of fo rces can be 'determined f rom the <nfil.uence coef-
f ic ients of a n equivalent s y s t e m of forces by consideration of the s t ra in energy i l l Lhe :s't.ructure.
Calculations involved in th i s p rocess will be ca r r i ed out for a cantilever beam and a s imple support . beam in o r d e r to clarify the development of the necessary formulas.
The s t r a i n energy fo r a uniform beam under the usual engineering approximations ,(Ref 5) is
where
L = length of a beam, in.
x = distance along beam, in.
E = tensile modulus of elasticity, lb-in. -2
Es = shear modulus of elasticity, lb-in. - 2
EI = bending stiffness of beam, Ib-in.
EsAs = shear st iffness of beam, lb
EA = tensile st iffness of beam, lb
Ael M = bending moment a t x , in. -1b
V = shear force at x. l b
F ig . 4 Cant i lever Beam F = tensile fo rce a t x , lb
Bending in one plane, s h e a r in the s a m e plane, and tension a r e the only deformations considered in
Eq (10 ) .
Cantilever Bear11
Consider a cantilever beam loaded with force sys tems F, , V , , and MI a s shown in Fig. 4. The
load distribution along this beam is then
and
Substitution of these re la t ions into the beam energy equation gives
wirlch, after iiitcgratisn, be collies
The cantilever orientation consis ts of having the left end of the beam on and tangent t o the r e f e r -
ence line f r o m which deflections a r e measured. With this orientation, the force cofnponents a t the
left end undergo no deflection and do no work.
The working deflection of the force sys tem M1 in Fig. 4 is s imply the slope 8 a t the right end; 1 the working deflection of the force sys tem V1 is the deflection yl at the right end; and the working
deflection of the force sys tem F1 is the elongation sl of the beam. Therefore , application of
Castigliano's Theorem, Eq (9) , to the canti lever beam energy, Eq (12), gives
and
Simple Support Beam
Next, consider a s imple support beam loaded with force s y s t e m s Fa, Mb, M a s shown in C
Fig. 5. The load distribution along.the beam is
and
The s imple support orientation consists of having the ends of the beam on the reference line
f r o m which deflections a r e measured. With this orientation, the shea r loads a t each end undergo
no deflection and do no work.. Thus, the working deflection of the force sys tem Mc is thes lope Bc
a t the right end , the working deflection of the force sys tem Mb is the slope 0 a t the left end, and b the working deflection of the force sys tem Fa is the elongation sa of the beam.
Instead of evaluating the energy in tegral and then differentiating, the p rocess can be r e v e r s e d
in calculating working deflections by Castigliano's Theorem. Thus, f r o m Eq (9) and Eq ( l o ) ,
F i g . 5 S i m p l e Suppor t Beam
F r o m Eq (14),
s o that
aM - - - 0, and - aF - 1 - , - 0 , - - aFa . a ~ , aFa
L s lo [ o t o +(A) (Fa)( l)] d x = (&)Fa
Similarly,
L
Mb aMb 0
4" {(A) [-. (l - z ) ' M C (?)I (' -?)
+ ( ) [(t) (.h - ..)I ( ) + ( ) (F.)(O)) dx
and €I is found the same way. T.he three working deflections thus evaluated a r e C
and
Transformation from Cantilever to Simple Support
By comparison of Figs. 4 and 5, the cantilever beam and the single support beam a r e seen to
have the same loading distributions if
and
Then, the cantilever deflections can be found in te rms of the simple support loads by putting the
loads of Eqs (16) in the cantilever deflections of Eqs (13). After simplification, the equations
and (a) Fa -
Then, sulistitution of deflections f r o m E q s (17) and fo rces f r o m E q s (16) into the energy equation
(8) gives
1
Differentiation with r e spec t to the force s y s t e m s gives
and
which a r e the s a m e a s in E q s (15). Thus , by using the canti lever deflection fo rmulas of Eqs (13)
and the fo rce relationships of Eqs (16) in an ene rgy equation, the working deflections of the s imple
support beam have been obtained.
This t ransformat ion f r o m the influence coefficients of the canti lever f o r c e ' s y s t e m to the influ-
ence coefficients';of the s imple support force sys tem'shows that the canti lever and s imple .support
beams a r e real'ly the s a m e structurC with the s a m e loading. The only r e a l difference is the change
of the reference line f rom which deflections a r e measured , a s shown i n Fig. 6, to correspond with
the change i n fo rce sys tem notation.
According t o E q s (17c) and (19a), s l = sa. This is t rue in Fig. 6 if deflections a r e s m a l l com-
pared to s t ruc tu re dimensions s o that L >> s l , and if s lopes a r e s m a l l s o that s i n 8 8 and
cos 8 r 1, where 8 = 8 ea, o r Ob. A s shown.in Fig. 6,
A. DEFLECTIONS RELATIVE TO 6. DEFLECTIONS RELATIVE TO CANTILEVER REFERENCE LlNE SIMPLE SUPPORT REFERENCE
LlNE
F i g . 6 E q u i v a l e n c e o f C a n t i l e v e r and S i m p l e S u p p o r t Beam
and
substitution of the v a l ~ e s ~ f r o m Eqs (17) .into these equations gives
and
which a r e the same a s obtained in Eqs (15). Thus, the use of strain energy in transforming influ-
ence coefficients from one force system to another equivalent force system is checked by direct use
of geometry.
111. SYSTEMATIC CALCULATION
A. Cantilever
Influence coefficients
In order to keep calculations involving many variables in simultaneous equations under control,
a systematic procedure involving matrices: will be used. . consider thc cantilever deflections bf
Eqs (13) rewritten with all.influence coefficients present:
In matrix form, thcoc equations bccolrlt:
or simply
where
.(PI = = force ,matrix.of cantilever ,:
+Elementary properties of matr ices a r e discussed in Ref 6 .
= deflection mat r ix of canti lever, and
= flexibility ma t r ix of canti lever.
Let (D ).. = element in row i and column j of matr ix (D ). The equations a r e s o a r ranged that P 1J P
(Dn)il is the working deflection of fo rce (P)il f o r i = 1, 2; and 3. With this ar rangement , the f l ex i -
biiity ma t r ix (A ) is symmetr ical , a s rcquired.by Eq (6). D
Energy
According to Eq (81, the canti lever ene rgy is
1 U = 7 + V1yl + F1sl) ;
o r in ma t r ix fo rm,
T where (U) = = the energy mat r ix of 1 r o w a n d 1 column, and (P ) is the t ranspose of (P).
Substitution of the canti lever deflection mat r ix (D ) f r o m Eq (20) into Eq (21a) gives P
Equations (21a) and (21b) a r e matr ix equivalents of E q (8).
B. Simple Support
CTAC Rule
The canti lever ma t r ix deflection equation (20) and the energy equation (21b) can be used to
determine the ma t r ix deflection equations f o r the ,simple support beam, once the relationship between
the force sys te lns is put in ma t r ix fo rm ' Equation (16) i~ equivalent to:
where
(Q) = = force matr ix f o r s imple support beam,
and
(C) = = connection matrix relating cantilever forces (P) 'to 's'imple
support fo rces (Q).
Substituting Eq (22) into Eq (21a) gives
o r , since the transposed product of two mat r ices i s the product of the transposes of the two matr ices
in r eve r se order .
1 T T (U) = 7 x (Q ) x (C x (Dp) . (23)
. . Let
= simple support dcflcctio~i 111tll1.i~ ~ u ~ . ~ . e s p u r ~ d i n g to the simple support
force nlaL1-ix (Q),
s o that, a s in Eq (21a),
Comparison of this matrix equation with Eq (23) shows that
Next, substitution of (D ) from Eq (20) gives P
(Dq) = (c") x (Ap) x (P) ,
and substitutionof (P ) from Eq (22) gives
, tDq) = (cTl x (Ap) x (C) x (Q) ..
Let (A ) be the simple support flexibility matrix relating (D ) and (Q) in the equation Q '2 (Dq) = (AQ) x (Q) . (244
Then, f r o m E~S' (2%) and ( 24~1 ,
'I'his is the most important equation of all- Lhe "CTAC1' equation. It gives the flexibility of a
sys tem of forces acting on a linear-elastic structure in te rms of (1) the flexibility of an equivalent
second system of forces and (2) the connecti'on matrix relating the second system to the f i rs t .
In more simple notation, let A be the flexibi.lity matrix of a force matrix P, and C be the cor -
rection matrix relating P to an equivalent force matrix P1. Then, the-flexibility matrix A' of P ' i s
simply
where P = CP1.
Flexibilitv
As a check, the CTAC equation (Eq 25) will be evaluated f o r the s imple support beam. Thus ,
Substitution into Eq (24c) gives
- -
This is equivalent to the three simultaneous equations
and
which check Eq (15). Thus, the CTAC procedure does lead to the co r rec t resul t .
IV. APPLICATION O F CTAC
A. Structure in WAPD-115
Given Data
The is to determine the influence coefficients and modes of vibratidn of the s t ruc tu re
used a s an example in WAPD-115 ( ~ e f . 7 ) and shown i n Fig. 7. Geometric and flexibility coefficients
a r e given in the following table.
. TABLE O F GEOMETRIC AND FLEXIBILITY COEFFICIENTS *
F i g . 8 Separated Free B o d i e s
Region No.
Do
Di 2 2 A = n(Do - D i ) / 4
2 I = n(Do - ~ 4 ) / 6 4
As = A / 2 o r 3A/4
L
W = (0 .284 pci )AL
6 EI = (30 x 10 ps i ) I
6 E A = ( 1 2 x 10 psi)As s S
L/EsAs
L I E 1
L~ / ~ E I
F i g . 7 Geometry of Sample Prob lem
1 . 2
12
11
18.06
299.2
9 .03
10
51.29
8976
108 .4
0 .09225
0.001.114
0 .005,570 --
3 , 4
12
8
62.83
816.8
31.42
5
89 .22
24,504
377.0
0.01326
0 .000,204
0.000, 510
L~ / ~ E I
( ~ ~ 1 3 ~ 1 ) + L/EsAs
0.03714
0 .1294
5 , 6
6
0
28.27
63.62
21.20
7 . 5
60. 22
1908.6
, 254.4
0.02948
0.003', 930
0.01474
. 0.'001,700
0.01496
0.03018
0.04903
0.07368
0.10316
in. / l b
in. / l b
7 , 8
7 . 5
0
44 .18
155.3
33. 14
7. 5
94. 10
4659
397.7
0.01885
0. 001,610
0.00604 -
Units
in.
: in.
in. 2
in. 4
in. 2
in.
lb
6 10 lb-in. 2
in6 ib
in. / l b
l ~ - ~ / l b - i n .
1 0 - ~ / l b , ---.
The loads, including the statically indeterminate end reaction F between the two cylinders, 5 may be put into the single. force matrix:
Flexibility of a Subdivided F r e e Body
cons ide r region No. 1 a s a separate f ree body with cantilever loads V1 and M a s shown in 1 Fig. '8. These loads can be put into the force matr ix:
The cantilever equations fo r region No. 1 a r e
and
D~~ = (&) I M1 t (& t A) V1 = (5. 57 x 1 0 - ~ / l b ) ~ ~ + (129. 4 x in. / lb)Vl , EsAs
s o that the flexibility mat r ix for (PI) on body No. 1 is
1. 114 in.
129. 4 in.
By inspection of Figs. 7 and 8, the moment a t the right end of body No. 1 is seen to be
M1 = (15 in. ) F 2 + (20 in. )F5 ,
and the Shear load on body No. 1 is
V1 = F1 + F2 + F 3 .
In expanded fo rm, the equations become
M1 = (0)F1 + (1 5 in. )F2 + (0 )F3 + (0 )F4 + (20 in. )F5
and
Vl = ( l ) F 1 + (1)F2 + (0 )F3 + (0 )F4 + (1 )F5 ,
s o that
where (C1) =
The flexibility matrix of (F) produced by deflections of body No. 1 is then, by 'the CTAC rule,
(AF1) = (cT) x ( A I ) x (CII . . , . Fi 20 in. 1
.1.14 in. .5. 57
129. 4 in.
This is the flexibility matrix giving the deflections of the forces in (F) resulting from the flexibility
of body No. 1.
Total Flexibility ,
In the s a g e way, the deflections due to body No. 2 can be determined. As before, le t
The connection equations for (P2) in t e r m s of (F) a r e
M2 = (5 in. )F2 + (10 in. )F5 and
s o that
Carrying through the multiplications of
(AF2) = (cT) x (A2) X (C2)
gives
x in. / l b .
The total flexibility of (F) due to both body No. 1 and body No. 2 is
(AF1, 2) = (AFs1) + (AF2)
x in. / lb i
The final flexibility matr ix for a l l eight pr imi t ives (bas ic beam s t ruc tu res ) is found to be
x in. / l b .
It is to he not.arl t,hat a.l.1. of the flexibility matrices a r e symmet r i ca l , in agreement with . the Recipro-
ca l Theorem.
Redundant Load Calculation
The working deflection DF5 is the net working deflection of F5 on.both 'canti1ever.b-eams in the
s t ruc tu re . Since the re .is no net deflection between the beams connected a t the end, should be
ze ro . Thus ,
0 = DF5 E (DFI5i ' xi (AF)5i .(F)il . , !. . .: , *,,\::. ,< , ,
= (0. 2408F1 t 0. 94471F2 - 2. 95355F3 - 0. 43481F4 t 5. 654975E5) x in. $lb . This equation is used to obtain the nonworking (redundant) fo rce F5 i n t e r m s of the working (non-
redundant) f o r c e s F1 to F4. Solving f o r F5 gives
By use of th is equation, the net working deflections of the o'ther f o r c e s F1 to F4 can be 'obtained;
f o r example ,
= [ U . 1295F1 + 0. 21295F2 t ( 0 ) F 3 t (0)F4
+ 0.2408(-0.042, 582F1 - 0. 167, 058F2 t 0. 522, 292F3 t 0.076, 890F4)] x 1.0-~ in. / l b
= (0. 119, 246F1 t 0. 172, 7,2ZF2 + 0. 1 2 5 , 7 6 8 ~ ) + 0. 018, 5 1 5 ~ ~ ) x l o m 6 in. / Ib . Similar ly ,
DF2 = (0. 172,722F1 t 0.617, 239F3 t 0 . 4 9 3 ~ 4 1 4 ~ ~ t 0.072, 639F4) x in. / l b ,
and s o forth. The' resul t ing flexibility ma t r ix for the net working deflection is thus determined.
Le t
(w) = be the working force ma t r ix ,
and
be the corresponding deflection mat r ix .
Then, the flexibil i ty ma t r ix in the equation
(DW) = (AW) x (W)
x in. / lb
This checks Eq (5) in WAPD-115 to slide rule accuracy.
Systematic Load Calculation
A systematic way to calculate (AW) i s to use the concept of partitioned matrices. The original
flexibility matrix equation for the statically determinate free bodies is
+ L v '+ - ( D ~ ) ~ (A F)NW ( A ~ ) ~ ~ ( F ) N
It is . to be noted that double lines these matrices into working (W) and nonworking (N) blocks.
and that these blocks can be used in separated matrix equations; that is ,
can be expressed a s
a d
Setting (DFIN = (0 ) gives
To solve for the redundant loads multiply each term by the inverse matrix of (AFINN; thus
I T (u) = iAFINN X (AFINW X ( F I W + (AFINN X (AFINN X (FN) n .
s o that
A s a check, t h i s m a t r i x equation wil l be so lved numerically. F i r s t ,
giving the i n v e r s e
t
(AF)NN = ( (AF)55 I = [ 5.654.975 x in. / l b I ,
Then,
x 1 0.2408 1 0.94471 1 -2.95355 1 -0.43481 1 x in. / l b
which checks Eq (26).
Substi tut ion of E q (29) into E q (28a) g ives
(DFIW = (AF)WW x (FIW + (AFIWN x - (AFINN x (AFINW x (FIW i
I
[ I I = [(AFIWW - (AFIWN x (AFINN x (AFINW I x .
Since
then,
(AW) = (AF)WW - (AFIWN X X .(AFINW~
Numerica l ly ,
(AW) =
x in. / l b
x 1 -0. 042,582 1 -0. 167,058 1 t o . 522,292 1 t o . 076,890
which checks Eq (27).
6 r 10 in. / l b
B. SO207 Code (CTAC and MODE)
Discussion
A WOLONTIS-650 code has been developed to calculate the influence deflection coefficients
(flexibility ma t r ix ) fo r an e las t ic s t ruc tu re with up to 10 applied loads and up to 14 loads when the
s t ruc tu re is made statically determinate. An es t ima te is made of the shock response to a 1 -g load-
ing by using weights a s the applied loads, and the fundamental frequency is approximated by the
formula (Ref 8):
where
f = natura l frequency, cps,
g = 386 in. / s e c 2 , usually,
Wi = weight a t point i.
and
Yi = s t a t i c deflection of Wi.
This formula is good if a l l deflections a r e positive. Local fo rces and moments throughout the s t r u c -
ture can a l s o be determined. All th is is progi-ammed in SO207 deck 1 and is called the CTAC code.
In S0207, deck 2 is programmed the MODE code, which uses the i tera t ion procedure of
WAPD-115 to calculate a s many modes of vibration a s des i red. Local fo rces and moments for each
mode can a l so be determined.
Arrangement of Decks
CTAC without MODE: Successive CTAC problems can be run with the following a r r a n g e -
ment of ca rds . (Each arrangement must be specified on the back of the r eques te r c a r d . )
Specified Arrangement Actual Contents of Arrangement on Requester Card (Not Indicated on Requester Card)
SO207 deck 1 On fi le in 650 room
( CTAC t rans fe r c a r d
Input deck F i r s t CTAC data deck
1. ;st CTAC data deck
CTAC and MODE: The MODE code uses the data f r o m the CTAC code input and output to
calculate natura l frequencies, mode shapes , and mode amplitudes of an e la s t i c s t ruc tu re . If the
MODE problem immediately follows the corresponding CTAC problem, the arrangement of decks is
this:
Specified Arrangement Actual Contents of Arrangement ,
on Requester Card (Not Indicated on Requester Card)
50207 deck 1 On fi le in 650 rooin
Iriput deck 1
CTAC t rans fe r c a r d
F i r s t CTAC data deck - -
1 Las t CTAC data deck
(Continued)
Specified Arrangement on Requester Card
SO207 deck 2
Input deck 2
Actual Contents of Arrangement (Not Indicated on Requester Card) , - ..
On file in 6 50 room'
MODE data deck c o r -
responding to l a s t
CTAC data deck
MODE Alone: If the corresponding CTAC problem had been done on a separst:e. previous
occasion, the arrangement of c a r d s is:
Specified Arrangement on Requester Card
SO207 deck 1
Input deck 1
SO207 deck 2
Input. deck 2
h ~ u t Cards
Actual Contents of Arrangement (Not Indicated on Requester Card)
On fi le
CTAC data deck
CTAC output deck
MOUE t rans fe r ca rd
On fi le
MODE data deck
~ r a n s f e r Cards:
1) CTAC Trans fe r Card
Columns Contents
7-10 6850
77-79 xxx ( ~ r b i t r a r ~ 3 -digit problem identification)
2 ) MODE Trans fe r Card
Columns Contents -
7-10 5480
7 7 -79 xxx (Arb i t ra ry Y -digit problem identification)
Data Card Format : Each number (called a "word" on a ca rd) has a sign, t 0.r - , and 10
digits, taking up a total of 11 columns on a card. A "fixed" number is put a t the right end and is
preceded by ze ros ; fo r example, t23 (fix) is put on a c a r d , a s tUUUUUUUUZ3. A number that is not
fixed is considered to be in the floating f o r m i (a. bcdefgh) x 10 ij-50 and is put on a c a r d a s
iabcdefghi j ; fo r example, -23 is put on a c a r d a s -2300000051, and t o . 056 is put on a c a r d a s
t 5600000048. Standard WOLONTIS format c a r d s a r e used a.s shown on the following page.
Columns Contents
Location of f i r s t word of c a r d in 650
s torage drum.
Number of consecutive words on c a r d ,
1 to 6 . If a row of words is m o r e than
6 , the row is broken in groups of 6 o r
l e s s and the groups put on success ive
ca rds . F o r example, i f a row of 9
words is to be put on c a r d s s t a r t ing a t
location 101, 5 words could be put on a
ca rd with location 101 and 4 words
could be put.on the next ca rd with loca-
tion 101 + 5 = 106.
F i r s t word
Second word
Sixth word
I
CTAC Data Deck (Input) . .
F i r s t Word
TRA NO. 1
P(fix)
P(fix)
---
A1 1
*21
A ~ l
C1 1
C2 1
C ~ l
Second Word
W(fix)
TRA No. 2
Location of F i r s t Word
638
540
543
197
197 + N - -
197 - N + N'
246
246 t R - -
246 - R t NR
Number of Words in Row .
1.
3
3
N
N
N
R
R
R
Third Word
R(fix)
Explanation
TRA NO. 1 = t0203000745, i f t he re
is a load calculation f o r th is CTAC
problem.
TRA No. 1 = t0203000548, if the re
is no load calculation and if MODE
follows th is CTAC problem.
TRA No. 1 = t0203000685, if the re
is no load calculation and if MODE
does not follow this par t icular
CTAC problem. - P = total ni imber of e lementary
!primitive) striirt11re.s; 1 s 999.
W = total number of external loads
(weights) on s t ructure : 1 5 W 5 10.
R = total number of loads (FR) on
s ta t ica l ly determinate s t ructure ;
W 5 R 5 14. The f i r s t W loads of
R a r e the original external loads.
Next come H s e t s of c a r d s fo r P primit ives in o rde r f r o m P = 1 to
P = F.
P = number of primitive; 1 ' 5 P 5
'I'HA No. 2 = t0203000602, if p a r -
t ia l flexibility ma t r ix An due to P
pr imit ives is to be punched.
TRA No. 2 t0203000604 otherwise,
1\J = number of loads on primitive. . . , . --
Flexibility matrix A of primitive P
s t ruc tu re P. The f i r s t word of each
row must s t a r t a new card.
Connection mat r ix Cp giving
(Fp) = (Cp) x (FR). The f i r s t word
nf each row mus t s t a r t a new ca rd .
A12
AZ2 .
A ~ 2
12
C22
cNa .
etc.
e t c .
e t c .
e t c .
e tc .
etc.
CTAC Data Deck (Input), Cont.
Location of F i r s t Word
51 5
500
543
197 - -
197 - N + N '
246 - -
246 - R + NR
F i r s t Word
W1 g
P(fix)
A1 1
1
C ~ l
Number of Words i n Row
W
1
3
N
R
R
Second Word
W2
TRA No. 3
A 12
5 2
cR2
Thi rd Word
etc.
,
N(fix)
e t c .
e tc .
e tc .
~ x ~ l a n a t i o n
These c a r d s come a f t e r the P s e t s
of ca rds .
Weights (pounds fo rce )
Gravity = 386 in. / s e c 2
If there a r e to be load calculations
on some pr imit ives , the following
s e t s of c a r d s must be added to the
deck. Otherwise, they a r e not used.
There is one s e t of c a r d s for each
primitive, to be considered, and
these pr imit ives need not be the
s a m e a s before.
TRA, NO. 3 = t0203000769, if th i s is
not the las t primitive on w-hich load
calculations a r e made.
TRA No. 3 = t0203000548, if th i s is
the las t primitive considered, and
if MODE follows.
TRA No. -3 = t0203000685, if th is is
the las t primitive considered and if
CTAC follows o r if the end of the
las t problem.
Flexibility ma t r ix A . P
Conncction 'matrix C . P
MODE Data Deck (Input)
Explanation
E = relative e r r o r for conver- -6 gence in iterations (10 cor -
responds to an e r r o r in the 7th
digit of a number). T = total
number of iterations carr ied out
if resul ts do not converge, say 15.
Vo = maxlmum starting velocity,
ipo
fo = cutoff natural frequency,
CPS M = number of modes to be
calculated; 1 5 M 5 W.
The starting velocity V for each
mode of frequency f is deter-
mined by the formulas
Second Word
T
f o
F i r s t Word
E
vo
Location of F i r s t Word
337
I
3 27
Third Word
M(flx)
Number of Words in Row
2
3
TRA No. 3
A12
A~~
C1 2
NZ
------
P(fix)
*11
A ~ l
Cl 1
C ~ l
543
1Y7 - -
197 - N + N2
246 - -
246 - H + 1'48
3
N
N
R
H
V = V i f f 5 f o , 0
V = f o Vo/f i f f > f o .
N(fix)
etc.
etc.
etc.
etc.
If there a r e to he lnad c a l c l ~ l a -
tions on some primltlves, the
following s e t s of cards must be
used. These cards have pre-
cisely the same format ac In t h r
CTAC data deck.
Output Cards
Output Card Format: Most of, the o ~ t ' ~ u t is in the form of blocks of data (matrices). Before
each ma t r i i is printed out, three words in locations 997 to 999 give, respectively, the machine s tor -
age location of the first element of the matrix, the number of rows, and the number of columns.
If the structure is redundant, one .of the matr ices will contain the flexibility matrix AW of the
applied loads and the coefficients of the redundant forces in te rms of the applied loads. This matrix
is identified by ones along the lower right diagonal. For example, if a structure has R = 4 loads
when made statically determinate and W = 2 applied loads, this matrix will be in the form:
where the corresponding equations a r e
DF1 = A1lF1 + A12F2 a
D ~ 2 = A21 F1 + A22F2
F j = K.. F + K3LFZ , 31" 1
and
F4 = K41F1 t K42F2 + K43F3 .
. CTAC Output Deck . -1 F i r st Second Word 1 Word
Third Word
Fourth Word Explanation I
If TRA No. 2 for primitive P is
t0203000602, the following cards
a r e punched: . . .
00 1 (fix) .R(fix) Flexibility matrix AR of R loads- I due to P primitive.
If the structure is redundant ( (W < R ) , this matrix containing I 4 anrl coefficients I<. . is
13 I punched.
Flexibility matrix A W of applied
loads.
etc. Static deflectiot~s'of weights, in.
Ys = equivalent static deflection
= (ziwiY;) 1 (ZiWiYi),
2af = natural angular frequency I
f = frequency, cps I -
etc. If W <R, these rcdundant loads I produced by 1 g applied loads a r e I punchcd. I If load calculations were made
for a primitive, the following oct
of cards is punched for this
primitive. . ' 1 1 (fix) Matrix of priilritive loads ~ i i ~ d t i '
I g a pplicrl l.oa.13..
1 (fix) Matrix of primitive deflettiona 1 under 1 g applied load.
1
MODE Output Deck
Location of F i r s t Word
330
336
297
307
317
484
997
- - 997
543
997
997
Number of Words in Row
3
3
W
w . .
W
W
3
- - 3 .
3
3
3
F i r s t Word
2/nf
J
FIJ.
F;I J
F::
Y1 J
344 + WM (fix)
- - [ 344 t RM - M]
P(fix)
010(fix)
080(fix)
Second Word
J
E
FSJ
F; J
F"' 2 J
YZJ
l(f ix)
- - -------- l ( f ix)
TRA NO. .3
N(fix)
N(fix)
Th i rd Word
VJ
T
etc .
etc.
,etc.
e tc .
M(fix)
- - M(fix)
N(fix)
M(fix)
M(fix)
Four th Word
J(fix)
- - - -
Explanation
The following c a r d s a r e
punched f o r each mode calcu-
lated.
27rf = Nat ang f r eq , r p s J fJ = Nat frequency, cps
V = s t a r t ing velocity. i p s
J = mode; J = 1 to M.
T = number of i te ra t ions in J calculation of mode J.
FiJ = fo rce FI in mode J a f t e r
T i tera t ions , lb.
FYJ = f o r c e FI i n mode J a f t e r
T J - 1 i te ra t ions , lb.
F l l f = 2 1, (WI/g)(2rfJ) YIJ; lb-
YIJ = deflection of FIJ, in. .
If W < R, the following-dards
a r e punched.
Matrix of FW+l J, f i r s t redun-
.dant load. - -
Matrix of FRJ, l a s t redundant
load.
If load calculations were made
f o r a pr imi t ive , the' following
s e t of c a r d s a r e punched f o r
e a c h primitive.
Matrix of primitive .loads;
( F ~ ) ~ ~ .
Matr ix of primitive 'deflections:
( D ~ ~ ) ~ ~ .
Sample Problem Using Structure in WAPD- 11 5
Printout of Cards: The printout of the cards used in the determination of influence coeffi-
cients and modes of vibration s t a r t s on page 32. The SO207 input cards were sent to the IBM-650
operator with the following note on'the back of the requester card:
Order of Cards
SO207 deck 1 . ,
Input deck 1
SO207 deck 2
Input deck 2
Results: The CTAC output gives an estimated natural frequency of 223.50 cps, which com-
pa re s well with the f i r s t MODE frequency of 222.45 cps. Fo r a natural frequency of 223. 5 cps, the
shock acceleration factor corresponding to a unit starting velocity is
- 1 - 1 zrrfv = 2 (223.5 sec )(1 in. set ) = 3. 658 . N=- E (386 11,. s e c ~ a )
Thus, f rom the CTAC output,, the moment a t the left end of the outer cylinder is
M = (7688. 1 in. -lb)(3.638) = 27,969 in. -1b , 0
and the absolute sum of the four MODE resul ts i s
Mo = (27,315 t 1,118 -1. 4686 .t 375) in. -1b = 33,494 in. -1b . The MODE code gives a higher moment but, in the usual sh.ock calculations, the higher modes have . ,
smal le r s tar t ing velocities so that the resu l t s will be closer. . .
F r o m CTAC output, ' the mokent .a t the left end of the inner cylinder i s
Mi = (2936. 5 in. -1L)(3. 638) = 10,683 in. -1b ,
and the absolute sum of the four MODE resul ts is
M. = (9131 + 1537 + 4500 + 1978) in. -1b = 17,146 in. -1b . 1
As before, taking only two modes would give a 'closer check.
A direct comparison of mode calculations from WAPD-115 and from the code SO207 is.given in .
the table on the following page.
The odd numbered modes a r e not s o accurate in slide rule calculations because of small differ-
ences between large num:bers in the determination of CJ. Otherwise, the agreement is satisfactory.
Sample problem Cards: The actual c a rds used in the solution of the sample . " problem given
in WAPD-115 a r e found bn pages 32 through 43 of this report. . .
COMPARISON TABLE O F MODE CALCULATIONS
Source
F r o m WAPD- 1 15 (Slide - ru le accu racy )
F r o m SO207 (IBM-650 machine)
3
1776
1776
- 691
3 0
1067
116
. - 26
1
60
1779
- 676
15
1061 -
117
- 26
1
59
2
-134. 8
-135
-215
2 59
164
- 18
- 16
18
18
-148
-233
280
188
- 19
- 17
2 0
2 1
Mode J
C f o r V = 1 in. / s e c J J
F~~ = 'J e~~
(lb)
D~~~ = 'J a~~
( l o 6 in. )
F~ J
(lb)
J
6 . (10 i n . ) - . .-
4
-298. 2
-298
518
-644
823
- 11
11
- 14
2 7
-291
534
-662
808
- 11
11
- 13
25
1
121 .8
122
7 55
699
8 0
234
8 37
7 34
130
122
7 57
698
80
235
8 39
733
131
SO207 I N P U T . "
0 0 1 1 685 0 T R CARD CTAC Input
2 638 1 +C203000745
3 540 3 +COOOOOOC08 +0000000004 +0000300005
- 4 543 3- +COOOOOOC01 - +0203000602 +0000300002 F i r s t Primiti-.re
5 197 2 +1114000G41 +5570000041
6 199 2 +5570000041 +1294000043
7 246 3 +0000000000 +1500000051 + 0 0 0 0 ~ ~ 0 0 0 0 0
8 249 2 +0000000000 +2800000051
9 251 5 +1000000050 +1000000053 +0000300000 +0000000000 +1000000050
1 0 543 3 + ~ 0 0 0 0 0 0 0 2 +0Z 03000601 +0000000002 Second Pr imi t ive
1 1 197 2 +1114000041 +557000004 L
1 2 199 2 +5570000041 t 1294000043
1 3 246 5 +0000000000 +5000000059 +OOOOQ000CO +0000000000 +1000000051
1 4 251 5 +OD00000000 +1C00000050 +0000000000 +0000000000 +1000000050
15 543 3 +0300000003 + 0 2 0 3 0 0 0 6 0 ~ +0000000002 Third - Pr imi t ive
1 6 197 2 +2340000040 +5160000049
1 7 199 2 +5100000040 +1496000042
1 8 246 5 +0300000000 -0000000000 +0000000000 +0000000000 +5000000050
- 1 9 251 5 +0300000000 -1600000050 +0000000000 +0000000000 +1000000050 !
t
.. %
4
0
m m
0
0
.O
.O
0
0
0
0
0
C'
c
0
Cl
0
.-I d
I I
0
0
0
0
C' 0
0
'A
0
0
* 0
0
0
0
o
m
0
0
0
0
0
0
0
0
0
0
0
d
+ +
0
0
.a
0
0
> 0
C
00
c 0
m m
0
0
0
0
0
0
0
0
0
0
In
0
N
0
N
4
I '
I
0
0
0
In
C 0
0
C
0
0
0 e
00
h
B
0
0
'G
0
F &
0
0
0
0
+ +
N
CO
N
o
00
0
C'
00
0
C'
C
OO
0
00
0
0
CO
O
G
CO
C
C
CO
O
o
00
0
0
00
0
+ +
++
C.
O.
0 0
00
00
00
00
00
0.
00
00
~
~0
00
00
00
00
00
C,
00
0
00
00
0.
04
00
00
40
0
04
00
00
m*
00
0m
r0
0
00
d0
00
m~
00
00
'4
00
O
Nm
O0
0m
H0
0Q
.m
d0
0
++
++
++
++
++
++
++
+
mN
Nm
ln
mN
Nl
nm
mN
Nm
ln
~.
~m
am
ma
m
ln
~N
Nl
nN
Nl
n'
~~
"N
N
0~
dN
Fl
49
OI
Od
Nm
~
Pd
P
d
Cd
FJ
.C
J
CJ
01
F
J
FJ
P
I V
l V
l F
l .F
l V
l
0
0
9-l.A
0
..rl h.
'FP
I 0
0
0
H
+ +
4
Ci
mm
o
0
0
.O
0
0
00
0
'0
O
CO
0
0
m o
-
40
+
. +
40
NO
O4
Nm
00
4N
mc
~0
0
44
00
04
40
00
~4
00
\
DG
C9
QO
QO
90
OU
C
00
00
00
00
00
00
00
C
CO
OO
OO
OO
0O
OQ
00
c3
C
00
90
0
~C
\D
QC
F~
~H
OQ
~.
~~
~O
O
Q.
OO
IO
)C
F~
O)
C~
OO
i
lc
ao
n~
uo
ci
rn
~u
co
~
om
dO
oC
H~
OO
O4
dO
C
+,
++
++
++
++
++
++
+
40
00
Om
4N
00
9.
4~
N0
0
04
40
00
,4
40
00
44
00
00
00
00
~0
00
0
0
0
0
0
m+
0
0
0
0
+
+
r\l U
0
m m
0
'0
0
C
0
0
0
0
0
a
0
0
0
0
0
0
0.
m
o
Ic
4
+ +
+
00
.9
0 0
35 543 3 +0300000007 ~ 0 2 0 3 0 0 0 6 0 4 +0000000002 Seventh Primitive
36 1 9 7 2 +1510000041 ;6040000041
Primi tjve ~6040000041
44 251 5 +0300000000 -0608000000 +0000000000 +000000~3000 -1000~00050
4 5 5 1 5 4 +132'5'800052 - i i ~ ~ 4 4 0 0 0 5 2 +1882000052 +1204403052 Weights
Load Calculation 48 197 3 + I 114000041 +5570000841 +0000C00000 (incl~ding the
foundation momen*) 49 200 3 +5.570000(341 +1294000043 . +0000C~r)0000
1
. . 54 543 3 +0000000005 +0203000548 +0000000003 Last Pr,imitive in Load
Calculation (including 5,5 197 3 +3930000841 +1474000Q42 +00Q000.0000 the foundation moment)
56 200 3 +1474000042 +1131680043 +0000000000
57 203 3 +0000000000 +000~000000 +0000000000
58 245 5 +0000000~~00 +0000000000 +1500000051 +0000000000 -2250000051
59 251 5 +0000000000 +0000000000 +1000000050 +0000000000 -1000000050
60 255 5 +0000000800 +COO0000000 +2250000051 +7500000050 -3000000051
. .
' 61 337 2 +1000000044. +1500000051 MOD3 Input
62 327 3 +1@00000050 +lObB080056 +0000000004
63 543 3 +0fi00000b01 +-0233000769 +0000000003 F i r s t Primit ive i n Load Calculst ion (same a s i n CTAC)
64 19.7 3 +1114000041 +55~70000841: +0800000000
70 543 3 +@~00000005 +0233000548 +0000000003~ Last E i m i t i v e i n Load Celculst ion (same a s i n CTAC)
71 197 3 +3930000041 +1474000042 +0000000000
SO207 DATA
0 0 1 1 540 4 +0000000!308 +0000000004 +0000000.C~05 +0000000001 CTAC Output
0 0 1 2 997 3 +0000000001 +0000000005 +0000030005 % due t o 1 pr imi t i re '
0 0 1 3 001 5 .+1294000043 +2129500043 +0000040000 +0000000003 +2408000043
0 0 1 4. OW 5 ' +2129500843 +5471500043 + 0 0 0 0 0 0 0 ~ ~ 0 +0000000000 +6585500043
0 0 1 5 011 5 +0000000000 +0~300000000 +0000000000 +0000000000 +0000000000
0 0 1 6 016 5 +0000000000 +0000000OCO +0000000000 +0000000000 +0000000000
0 0 1 7 021 5 +24080'00043 +6555500043 . +0000000000 . +0000000000 +7978000043
0 0 1 8 540 4 +0000000008 +0000000004 +OOQOO00005 +0000000002
0 0 1 9 997 3 . +0000000001 +0900000005 +0000000005 % due t o 2 primit ives
0 0 1 10 OC1 5 +129400CH)43 +2129500@43 +0000000000 +OOOOOOOOOO .+2408000043
0 0 1 11 006 5 +2129500043 +7501000043 +00'00000000 +0000000000 . +9272000043
0 0 1 12 011 5 +0000000000 +0300000000 +000000000C +0000000000 +0000000000 . .
0 0 1 13 016 5- +0000000000 +0000000800 +00000000OC +0000000000 +0000000000
0 0 1 14 021 , 5 +2408000043 +9272000043 + 0 0 ~ 0 0 0 0 0 0 C +0000000000 . +1150000044
- - ~ -
. .< . .
001 1 5 540 4 +'3000000(308 +CC80000004 +0000000005 +0000000008
0 0 1 1 6 99' 3 +3000000001 +0000000005 + 0 0 0 0 0 0 0 ~ 0 5 AR due to all primit ives
001 1 7 001 5 +8294000843 +2129500043 +0000000000. +0000030000. +2408000043
001 18 006 5 +2129500043 +7750600043 ' +0000000000 +0000030000 +9447100043
001' '19- 0.11.. 5 . . ' +3000000100 ' - ' +00~00000000 +2023962544 ' " . +3242630043 -2953550044 . ,
001 20 018 5 +3000000800 +OOOQO001CO +3242600043 +10316.30043 -43481 00043
001 21 021 5 +2408000443 +9447100@43 -2953550044 -4348100043 +5654975044 . .
001 22 997 3 + 3 0 0 0 0 0 0 ~ 0 1 +0000000@05 +0000000005 % ani K: j,
001 .23 001 5 +[I91462643 +1.7272.23843 +125,7679943 +185153684? +2.408000043
001 24 006 5 +872'7223843. +6i72384443 +493&147743 +7263858042 +9447100043
0 0 25 011 5 +1257679943 +49341.47843 .+4813460043 +9716209042 . -29.53550.044
001 26 016 5 +C851506842 +726385.8 042 +9716208042 . +697275+042 -4348100043
001 27 021 5 -.1258197448 -1670582149 +5222923149 +7688981848 -9999999949 - ' . . .
. .
. .- .. . . . . . . .
i I . .
-. . -..
001 28 540 3 +00000~10808 +0000000004 +0000000005
001 29 997 3 +0000000001 +OOOQ000004 +0000000004 45 001 30 001 4 +I191462643 +I727223843 +I257679943 +I851506842
001 31 005 4 +172721384? +6172384443 +4934147743 +7263858042
001 32 009 4 +I257679943 +4934 147843 +4813460043 +9716208042
001 33 013 4 +1851506842 +7263858042 +9716208042 +6972754042
001 34 501 4 +6894209545 +2?94671446 +2032377346 +4154479245
001 35 529 3 +I957346746 +1404299653 +2235012252 Frequency
001 36 519 1 +7337809751 Redundant Load
001 37 543 3 +0000000001 +9203000769 +0000000033
001 38 997 3 +0000000351 +0000000003 +0000000001
001 39 351 1 +4144161953 Load Calculation for Primitive No. 1
001 40 352 1 +3543981@52
001 41 353 1 +76881s2957
001 42 907 3 +0000000371 +0000000003 +0000000031
001 43 371 1 +6590593844
001 44 372 1 +6894209645
001 45 373 1 +0000000800
0 0 1 46 543 3, +3000000005 +0203000548 +0000000003
0 0 1 47 997 3 +3000000351 +000@000003 +0000000001
0 0 1 48 351 1 +I171992853 Load Calculation for Primitive No. $
0 0 1 49 352 1 +1148219D52
0 0 1 -50 3.53 ' 1- +19,3645.7153
0 0 1 5 1 997 3 +3000000371 +0C00000003 +0000000001
0 0 1 52 371 1 +5298406544
0 0 1 53 372 1 +>912020145
0 0 1 54 373 1 + 3 0 0 0 0 0 0 ~ 0 0
L
I
001 55 330 4 +I397707353 +2224520352 +1000000050 +0000000001 MODE Output
001 56 336 3 +7000000050 +1660000044 +1500000051
001 57 297 4 +I2176281252 +7572647152 +69776.37252 +7961363451. First Mode
+796'136'2351 001 58 '307. 4 +1217628252 +75726&6952 +69776'37352
001. 59 317 4 +12.17628:252 +7572646852 +6977637452 +796136.3451
00.1 60 ,484 4 +2345345446 +8385139946' +73256'06746 +I306085246
001 61 330 4 +5398087653 +a591323352 +1000000050 +0000000002
001 62 336 3 +1600000051 +lC00000@44 +i500000051
001 63 257 4 -14791053'52 -2328211152 +280.2711752. +1883'356652 Second Mode . .
001 64 3C7 4 -1479105352 -2328287652 +2802786152 +I883356652
001 65 3x7 4 -14790863'52 -2328143Q52 +2802635552 . +I883292252 '
001 66' 484 4 -1910021~545 -1728322945 +I972670045 +to71354345
001 67 330 4 +7572882253 +I265261653 +100000005C~ +0000000003
001 68 336.3 +1600000~51 +1~00000644 +1500000051
001 69 25-7. 4 ' +1778515057 -6769884352 +1524057551 . +lo61353153 . Third Mode
001 70 307 4 +1778515@53 -676917?852 +1524057551 +lo61353153
001 '71 317 4 +I778493653 -6761204852 +1530871451 +1061210053 ,
001 72 464 -4 +I166956146 -2556332445 +5474998445 ' +5930557045
. .
. .
- ~
001 73 33C 4 +1009491@54- +I686654853 +1000000050 +000000000L
001 74 336 3 +2000000@50 +lOOQO00044 +~1.500000051
001 75 297 4 -2908838852 +5340940252 -6623016752 +808154'145.2 Fourth Mode
001 76 307 4 -2908.838752 +534~940252 -6623016752 +8081541452
001 -77 3.1.7 4 - ..-2908840652 . -+5340191952 -6621871752. +8079938252
001 78 48-5 4 -1074087G45 +I133566645 -1 332734245 +2541078445
001 79 997 3 +0000000360 +000000001 +0000000004 'Redundrnf. Load
001 80 360 4 +2388659252 +2'060575052 +I267807252 -36061 38652
001 81 543 3 +Q000000~01 +0203000769 +00.80000003 Load Calculation for Prini.?iv.- No. 1
001 82 997.3 +0000000~10 +0~~0000003 , - +0000000004
001 83 010 4 +I613628954 +62~8349052 -7,605712053 +7991333051 I .
001 84 '016 4 +1117893553 -17b6740652 +1229207353, -1174037252
001 85 016 4 ' +2731522454 -1117905'753 +4686360653 -3749040052
001 86 997 3 +0000000~80 +00@0000@03 +0000000004
001 87 08@ 4 +2420249345 -2724124343 -1626078544 +236295554'¶
001 88 08b 4 +2345345546 -1910021345 +I166956046 . -107408"045 , .
001 89 088 4 +0000000000 ~+0000000000 +0000000000 +0000000000
b
I
-
0 0 1 9 0 ' 5 4 3 3 +0000006005 +0203000548 +00000000@3 . Load ~alclculation f o r Primit ive No. 5
0 0 1 9 1 997 3 . +OO~OOOOQ)10 +0000000003 +0000000004
0 0 1 92 010 4 ' + 5 0 9 1 9 7 3 ~ 5 3 -4322280052 -2623957653 -1820713253
001 93 OL4 4 +4588978052 +7421359051 -1 115401452. -3016578152
0 0 1 9 4 018 4 ' +91308081353 +153689'1453 +4499639653 +I977959053
,001 95 937 3 +0000000080 +0000000303 +0000000004
0 0 1 96 030 4 +2677560845 -6047477043 -1195625545. -1160228145
0 0 1 , 9 7 094 4 +1223955846 +I284633244 -5018361645 -5795942745
0 0 1 98 098 4 ,+000000!3000 +0008000000 +0000000000 +0000000000
. . . .
The actual preparation and "debugging" of the CTAC and MODE codes were done-with the able
assistance of Mr. W. D. Long.
. .
REFERENCES
1. G . Kron, Tensor Analysis of Networks, (New York: John Wiley and Sons, 1939).
2. B. Langefors, "Analysis of Elastic Structures by Matrix ~ r a n s f o r k a t i o n with Special Regard to
Semimonocoque Structures, I' Journal of Aeronautical Sciences, Vol 19 (July 19 52), p 451.
3. G . Kron,. "Solution of Complex Non-linear Plastic Structures by the Method of Tearing, Journal
of Aeronautical sciences',' Vo1,23 (June 1956), p 557.
4. J. H. Argyris, "Eriergy Theorems and Structural Analysis, I' Aircraft Eng. ,' Vol 26 (1954),
pp 347, 383, and 410; Vol 27 (1955), pp 42, 80, 125, and 145.
5. S. ~ imoshenko , Stse'ngth of Materials, Vnl T (Princeton: D. Van Nostrand Co. , Inc. , 1141), . .
6 . L. A. Pipes, Applied Mathematics for Engineers and'physicists, (New York: McGraw-Hill,
1946).
7. C. M. Friedrich, "Shock Calculations for an Elastic System with Distrihnterl Mass, Using the
Starting Velocity Concept, I' WAPD-115 (1 954).
8. L. S. Marks, Mechanical Engineers1 Handbook, Fourth Ed. (New York: McGraw-Hill , 1941);