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Contents
2- Buckling
107 1-INTRODUCTION 108 2-SLENDERNESS RATIO 109 3-END CONDITIONS 110 4-EULER'S FORMULA 113 5-COLUMN WITH ONE END FIXED AND THE OTHER
FREE 114 6-CRITICAL STRESSES 115 7-LIMITATION OF EULER'S FORMMULA 117 8-FACTOR OF SAFETY 117 9-EMPIRICAL FORMULAE 120 10-MAXIMUM FIBER STRESS 131 11-COLUMN WITH INITIAL CURVATURE 135 12-LATERALLY LOADED COLUMN 139 13-PROBLEMS
3- statically indeterminate structures
147 1-INTRODUCTION 149 2-FORCE METHODS ( flexibility Approach) 150 3-DISPLACEMENT METHODS (stiffness approach )
Page 1- Deflections 1 1-INTRODUCTION
2-DEFINITIONS
33-THE DIFFERENTIAL EQUATION OF THE ELASTIC
LINE 7 4-THE DOUBLE INTEGRATION METHOD
21 5-MOMENT- AREA METHOD 28 6-ELASTIC – LOAD METHOD 39 7-THE CONJUGATE BEAM METHOD 51 8-THEORY OF REAL WORK 61 9-METHOD OF VIRTUAL WORK 66
10-EVALUATION OF INTEGRAL dxMM 10 84 11-DEFLECTION OF TRUSSES 89 12-CASTIGLIANO' S SECOND THEOREM 93 13-MAXWELL'S LAW OF RECIPROCAL DEFLECTIONS;
BETTI' S LAW 95 14-INFLUENCE LINE FOR DEFLECTION 97 15-PROBLEMS
151 4-DEGREE OF STATIC INDETERMINACY 151 4.1-Degree of Indeterminacy For Beams (Line Structures)
153 4.2-Degree of Indeterminacy for Plane Frames
155 4.3-Degree of Indeterminacy of Plane Trussed
4- METHOD OF CONSISTENT
DEFORMATIONS 159 INTRODUCTION
160 ONCE STATICALLY INDETERMINATE STRUCTURES
171 TWICE STATICALLY INDETERMINATE STRUCTURES
176 3-TIME STATICALLY INDETERMINATE
182 CASE OF n- STATICALLY IN DETERMINATE
STRUCTURES 186 SETTLEMENT OF SUPPORTS
187 CHANGES OF TEMPERATURE
194 BEAM ON ELASTIC SUPPORTS
209 FORCED DEFORMATIONS
227 TRUSSED BEAM AND TRUSSED FRAME
235 DEFLECTION OF STATICALLY INDETERMINATE
STRUCTURES (REDUCTION THEORY) 248 ANALYSIS OF STATICALLY INDETERMINATE TRUSSES
252 DEFLECTION OF INDETERMINATE TRUSSES
258 GENERAL REMARKS CONCERNING SELECTION OF
REDUNDANTS
260 CHOICE OF MAIN SYSTEM IN CASE OF SYMMETRY
AND ANTISYMMETRY
263
ANALYSIS OF STATICALLY INDETERMINATE
STRUCTURES USING CASTIGLIANO SECOND
THEOREM; THEOREM OF LEAST WORK 268 TORSION OF FIXED BEAM
5-Influence lines of statically indeterminate beams
and frames 278 1-INTRODUCTION
279 2-INFLUENCE LINES FOR DETERMINATE BEAMS BY
MULLER-BRESLAU PRINCIPLE
286
3-MULLER-BRESLAU’S PRINCIPLE FOR
INDETERMINATE STRUCTURES
308 4-INFLUENCE LINE OF TRUSSED BEAM
322 5-INFLUENCE LINE FOR FRAME
324 6-ANALYSIS OF STATICALLY INDETERMINATE
FRAMES 341 7-MAXIMUM EFFECT USING INFLUENCE LINE
343 8-PROBLEMS
6- INFLUENCE LINES OF STATICALLY
INDETERMINATE TRUSSES 346 1-INTRODUCTION
346 2- THE DISPLACEMENT DIAGRAM
347 3- WILLIOT DIAGRAM
357 4- WILLIOT-MOHR DIAGRAM
362 5- INFLUENCE LINES FOR STATICALLY
INDETERMINATE TRUSSES 370 6- PROBLEMS
7- MOMENT DISTRABUTION METHOD
374 1-Introduction
376 2-Sign Convention.
376 3-Stiffness
380 4-Carry over factor
381 5-Distribution factor
383 6-Fixed End Moment
387 7-Non-Prismatic Members
391 8-A continuous Beams with simply supported ends
395 9-Beams with end overhanging
10-Beams with a settlement supports.
383 11-Frame without sideways symmetry & anti-symmetry
416 12-Structures subjected to sideways.
464 13-Temperature Effect
474 14-Frame with n- degrees of Freedom.
494 15-Influence lines by moment distribution
496 16-Case of continuous beam
497 17-Procedures
500 18-Examples
509 19-Problems
APPROXIMATE ANALYSIS OF STATICALLY
INDETERMINATE STRUCTURES516 1-INTRODUCTION
517 2-Trusses
522 3-Building Frames Subjected to Vertical Loads
527 4-Portal Frames
533 5-Portal Method
539 6-Cantilever Method
548 7-Problem
551 8-References
1 DEFLECTIONS
1._INTRODUCTION
The computation of elastic deformation for structures, either the linear
deformations of points or the rotational deformations of lines (slopes)
from their original position, is of great importance, not only in the design,
construction of structures but also in the analysis and solution of statically
indeterminate structures. In structural design the dimensions of beams
and girders are sometimes governed by the allowable deflections. It must
be noted that, if the deflections of beams or frames is excessive, some
problems will be produced as cracking of plaster, drainage problems,
damage of walls. Most important, the stress analysis for statically
indeterminate structures is based largely upon an evaluation of their
elastic deformations under load. By a statically indeterminate structure
we mean a structure in which the number of unknown elements involved
is greater than the number of static equilibrium equations available for
solution of the equations. The elastic deformations liable to accure in the
structure resulting in the external loads, temperature variation and
differential settelements between supports cause various deformations,
but such elastic deformations vanish when the loads disappearent as
shown in Fig. 1.
The following assumptions are made for the computation of
deformations:
1. Bernoulli's law is valid, plan sections before deformations remain
plane after the deformations.
2. The materials obey Hook's low.
E =
2 Chapter (1) - Deflections
3. The depth/span ratio is very small, i.e. the external loads act on the
non-deformed member.
Numerous methods of computing elastic deformations have been
developed. Among them the following are considered;
1. The double integration method.
2. The conjugate beam method (Moment area, elastic load methods)
3. The method of virtual work
4. Castigliano's theorem
The first two methods are used for beams and frames, whose members
subject to bending strain, while the method of virtual work is used for all
types of strain; bending, axial and shear.
Figure (1)
Chapter (1) - Deflections 3
2. DEFINITIONS
Deflection
Is the displacements of various points from their original positions.
Stiffness
Is the resistance of a structural element to deflection.
The deflection of a member (beam) depend on;
1- The value of loads acting on the beam.
2- The stiffness of the member, which depend on the type of material and its
modulus of elasticity (E).
3- The dimensions of elements (span, cross section)
3. THE DIFFERENTIAL EQUATION OF THE ELASTIC
LINE
3.1 Curvature of elastic line (from mathematic)
The mathematical definition for curvature is the rate at which a curve is
changing direction. To derive the expression for curvature, we shall
consider a curve such as the one shown in Fig. 2
4 Chapter (1) - Deflections
The average rate of change of direction between points P1 and P2 is S
.
The limiting value of this ratio as S approaches zero is called curvature
(K) and the radius of curvature (R) is the reciprocal of the curvature, we
have,
K = R
1
=
S
SLim
= S d
d
but
tan = x d
y d
x d
d tan =
2
2
x d
y d
or
(1 + tan 2 )
x d
d =
2
2
x d
y d
Then:
2
2
x d
y d = (1 + (
x d
y d)
2)
x d
d
where
x d
d =
2
2
2
dx
dy 1
xd
yd
also s d
x d =
dx
ds
1
Chapter (1) - Deflections 5
s d
x d =
2
1
2
22 dy
1
dx
dx
=
2
12
1
1
dx
dy
hence,
R
1 =
S d
d =
x d
d
s d
x d
R
1 =
2
32
2
2
dx
dy 1
xd
yd
(1)
For a loaded beam with its longitudinal axis taken as the X-axis, we
may set dy/dx in formula (1) equal to zero if the deflection of beam is
small. Then we obtain;
R
1 =
S d
d
2
2
x d
y d (2)
R
h
M
h
ds
d
M
1
1h-d
h-d
1
1
Figure (3)
6 Chapter (1) - Deflections
3.2. Curvature from elastic bending:
In general, except for very deep beams with a short span, the
deflcetion due to the shearing force is considered, In order to develop a
formula for the curvature due to elastic bending, let us consider a small
element of a beam shown in Fig. 3. Owing to the action of bending
moment M, the two originally parallel sections 1-1 and 1\ - 1
\ will change
directions. This angle change is denoted by d. If the length of the
element is dS and the maximum bending stress, which occur at the
extreme fibers, is called , the total elongation at the top or bottom fiber
is h. d which equals to . ds/E, E being the modulus of elasticity. Thus,
E = /
h. d = E
ds .
or s
d
d =
h
E
=
R
1
Replacing with I
h.M, I being the moment of inertia of the cross
sectional area of the beam about the axis of bending, gives.
R
1 =
s
d
d =
EI
M (3)
which expresses the relationship between the curvature and bending
moment. Now equating eqs. (2) and (3), we obtain the approximate
curvature for a loaded beam as;
2
2
x d
yd =
EI
M (4)
Note that eqn. (4) involves four major assumptions;
1. Small deflection of beam
2. Elastic material
3. Only bending moment considered significant
Chapter (1) - Deflections 7
4. Plane section remaining plane after bending
The curvature, established in the coordinate axes of Fig. 2, clearly has
the same sign as M, but the sign may be reversed if the direction of the y
axis is reversed. In that case, we have
2
2
x d
y d = -
EI
M (4
)
This Eqn.4
is the differential equation of elastic line. In our next
computation we consider Eqn. 4.
4. THE DOUBLE INTEGRATION METHOD:
This method is so named because the successive integrations of the
second order differential equation;
2
2
x d
y d =
EI
M
resulting the equation of elastic curve, the values of deflection, can be
obtained as follows
1- Consider The Case of Simple Beam;
From fig.4;
w t /m
C
y
y
x
Figure (4)
8 Chapter (1) - Deflections
2
2
x d
yd = -
EI
M
M = 2
Wx - x .
2
WL 2
2
2
xd
yd = -
2
Wx - x .
2
WL 2
EI
1
= dx
y d
=
1
32
C 6
Wx -
4
x.WL
EI
1
EI = 1
32
C 6
4
x.
WxWL (1)
EI y = 21
43
C X . C 24
Wx
12
X .WL (2)
To get C1 & C2, from boundary conditions :
At x= 0, y = 0 C2 = 0
And At x= L, y = 0 C1 = WL3/24
At x= L /2, = 0
Hence
= EI
1
24
WL
4
x.WL -
6
Wx
323
= EI
W
24 L Lx 6 - x 4 323
y = EI
1 x.
24
WL
12
x.WL -
24
Wx
334
Chapter (1) - Deflections 9
ymax
y = EI 24
W Lx 2 - x 334 L
y maximum at = 0 or at x = 2
L
ymax = EI 843
WL 5 4
Example (1):
Get ymax. for the given beam shown in the Fig.5
E = 210 t/cm2
I = 12
50 25 3 = 260416.6 cm
4
Solution:
ymax = 260416.6 210 843 100
(500) 1 5 4
= 0.1488 cm.
= EI 24
WL
EI 2
1 L
3
2
8
32
WL
elastic
curve
25
50
a
L = 5 m
W = 1 t/m\
Figure (5)
b
a
10 Chapter (1) - Deflections
= 260416.6 210 24 100
(500) 1 3
= 0.000952 rad.
to draw the elastic line, calculate the values of y at different point
Example (2):
Find ymax for the given beam show in Fig.6. Also get the equation of
Figure (6)
Solution
Reactions
RA = 6
WL
RB = 3
WL
MX = x. 6
L . W-
3
x .
2
x. 2
L
W
= x. 6
L W-
L 6
. Wx3
Chapter (1) - Deflections 11
2
2
xd
yd = -
EI
M
= EI
1 x.
6
.WL -
L 6
Wx
3
2
2
xd
yd =
EI
W
6
..x L -
L 6
x
3
= dx
dy =
EI
1 C
12
x.WL -
L . 24
Wx 1
24
y = EI
1 C x . C
36
x.WL -
L 201
Wx 21
35
Boundary Conditions
at x = 0, y = 0 C2 = 0
at x = L, y = 0
L . 36
- 120
1
44
CWLWL
= 0
C1 = 120
WL -
36
WL
33
= 360
WL 7
3
i.e.
y = EI
1 x .
360
WL 7
36
x.WL -
L 201
Wx
335
ymax. at dx
dy = 0
i.e. WL . 360
7
12
x.L. W -
L 24
Wx 3
24
= 0
12 Chapter (1) - Deflections
x = 0.519 L
Hence
ymax = EI
WL .00650 4
If L = 5 m
W = 2 t/m\
E = 210 t/Cm2
I = 260416 Cm4
ymax = 260416 210 100
500 2 00665.0 4
= 0.152 cm.
Example (3)
Find the slope and deflection
equations for the given
cantilever beam shown in Fig. 7
Solution
M = - P (L – x)
2
2
xd
yd= -
EI
M
= + EI
P (L – x)
Figure (7)
= dx
dy =
EI
P C
2
x - X 1
2
L
y = EI
P C .x C
6
x -
2 21
32
Lx
x
Chapter (1) - Deflections 13
at x = 0 , y = 0, = 0 C1 = 0 , C2 = 0
i.e.:
= EI
P
2
x - x
2
L
y = EI
P
6
xX -
2
32
Lx
max . & ymax.. at x = L. i.e.
ymax .= EI 3
PL3
, max. = EI
PL
2
2
If p= 2t , L = 4m , EI = 3000 t.m2
Hence
max = 3000
2
2
4 - 4 4
2
= 0.00534 radian
ymax.. = 3000
2
6
4 -
2
4 4
32
= 0.014 m = 1.4 cm.
Example (4)
Find the expression of
slope and deflection.
Locate the position of
max. deflection for the
given beam shown in
Fig.8, EI = constant
Figure (8)
Solution
Part ac :… x a
M = x. L
b. .P
14 Chapter (1) - Deflections
2
2
xd
yd = - x.
LEI
b. .P
dx
dy = - 1
2
C 2
x .
LEI
b. .P
yac = - 21
3
C x . C 6
x .
LEI
b. .P
Part cb x a
M = P - x . b. .
L
P (x – a) =
L
a .P(L – x)
2
2
xd
yd = -
EIL
a .P(L – x)
dx
dy = - 3
2
C 2
x -Lx
L I E
a. .P
ycb = - 43
32
C x . C 6
x -.
2
Lx
EIL
a. .P
Boundary Conditions
Part a-c:
at x = 0, yac = 0,
at x = a, yac = ycb
Chapter (1) - Deflections 15
Part c-b:
at x = L, yb = 0
at x = a, ac = cb
Hence:
C2 = 0, C4 = 0
and
C1 = C3 = 22 b - L . EIL 6
b. .P
Part a-c:
y = 222 b - L x . EIL 6
bx P
y = 222 b - L . 6
bx .x
EIL
P
= 222 x3 b - L . EIL 6
b .P
Part c-b:
=
2222 )(
33x-b L .
6
bax
b
L
EIL
P
y =
3223
x- b - L a -x b
L .
6
bx
EIL
P
In case of a = b = 2
L
ymax =EI 84
PL3
16 Chapter (1) - Deflections
Note
In case of beam with variable moment of inertia; the moment equation
were different for each part have the same I. each part should be
considered separately.
Example (5)
For the shown beam in Fig. 9
under the given loads it is required
to sketch the elastic line and
calculate the maximum deflection
EI = 10000 t.m2
Solution
To sketch the elastic line it is
sufficient to determine the values
of deflections at different points B
and D and the angle of rotation at
points A, C and D.
Similarly by the same method one
can get the following:
yB = 1.0246 cm
yD = 0.078 cm
A = 0.0021 radian (0.12)
C = 0.003 radian (0.172)
Figure (9)
To get ymax.
For part AB
ymax. at = 0 or dx
dy = 0
x = 6.94 m
ymax. = 1.0632 cm.
Chapter (1) - Deflections 17
Example (6):
For the given frame, it is required to sketch the elastic line due to given
load. (Fig. 10)
Figure (10)
Solution:
After drawing the M.D. the frame can be divided into 4 parts for each the
equation of bending moment can be easily written.
a) Equation of the bending moment,
part A-B M1 = 2 x1
B-C M2 = 1.33 x2 + 12
C-D M3 = 2.67 x3
D-E M4 = 0
18 Chapter (1) - Deflections
Differential equations of the elastic line. Part A-B;
EI 21
12
dx
yd = -2 x1,
EI 1
1
dx
dy = 1
21 C x- (1)
EI y1 = - 211
31 C x. C
3
x (2)
Part B – C (2EI)
(2EI) 22
22
dx
yd = -1.33 x2 – 12
EI dx
yd
22
22
= - .67 x2 – 6
EI dx
dy
2
2 = - .33 3222 C x6 - x (3)
EI y2 = - .11 42322
32 C xC 3x - x (4)
Part C – D (2 EI)
2EI dx
yd
23
32
= - 2.67x3
EI dx
yd
23
32
= - 1.33 x3
EI dx
dy
3
3 = - 0.67 5
23 C x (5)
EI y3 = - .228 63533 C xC x (6)
Chapter (1) - Deflections 19
Part D – E (EI)
EI dx
yd
24
42
= 0
EI dx
dy
4
4 = 7C (7)
EIy4 = 847 C X C (8)
To obtain the 8 constants C1 to C8 we consider the boundary conditions;
(1) at x1 = 0 y1 = 0
(2) at x1 = 6 x2 = 0, dx
dy
1
1 = dx
dy
2
2
(3) at x2 = 0 y2 = 0
(4) at x2 = 9 x3 = 9, 2dx
2dy =
dx
dy
3
3
(5) at x2 = 9 x3 = 9, y2 = y3
(6) at x3 = 0 y3 = 0
(7) at x3 = 0 x4 = 0, dx
dy
3
3 = dx
dy
4
4
(8) at x4 = 0 x1 = 6, y1 = - y4
By solving these equation one can sketch the following elastic line.
(y4)E
1
2
y1=y3
3
(y4)D
3
1 1`
y1 max.
20 Chapter (1) - Deflections
5. MOMENT- AREA METHOD
This method is used for any case of loading which cause bending
moment. It is more convenient when the deformation is caused by
concentrated rather than distributed loads. This method is based on a
consideration of the geometry of the elastic curve of the beam and the rate
of change of slope and the bending moment at a point on the elastic curve
0A
Ay
By
0B
AByB
A
AxBx
B A
mAEI
M
Figure (11)
Referring to above Fig. 11, consider a portion A B of elastic curve of a
beam that was initially straight and continuous in position A0B0 in the
unloaded condition. Draw the tangents to the elastic curve at points A and
B. The tangent at A and B intersect the vertical at origin 0 at A- and B
-.
The angle AB is the change in slope between the tangents at points A
and B. Consider a differential equation of the elastic curve:
Chapter (1) - Deflections 21
i.e. 2
2
dx
yd =
EI
M
Multiply by dx
i.e.
2
2
dx
yd dx =
EI
Mdx
Integrating the two sides, hence
dx d
2
2
B
A dx
y = dx
B
AEl
M
BA ds
dy-
ds
dy
=
A
B
EI
Monemt Bending of Area
AB = ABA
= EI
Am
Where Am is the area of bending moment diagram between points A and
B. Let a b the bending- moment diagram for portion AB after it is
modified by dividing every ordinate by EI of the beam at that point. Such
diagram is called the M/EI diagram. It is evident that the integral
dx d
2
2
B
A dx
ycan be interpreted as the area under the M/EI diagram between
A and B. Hence we may state:
5.1 First moment – area theorem
"The angle or change in slope in radians of the tangents of the elastic
curve between two points A and B is equal to the area under the M/ EI
diagram between these two points."
In fact the deformation and slopes are actually small. From equation (1)
22 Chapter (1) - Deflections
The left hand side represent the vertical ( yab) through the origin between
the tangents to elastic curve at points A and B and this distance is equal to
(Fig.12)
yab = cm x
EI
A.
The right hand side term in equation (2) is the static moment about axis
thought origin 0, of the area under the EI
Mdiagram between the points A
and B. therefore we may state:
5.2. Second Moment – area Theorem
"The deflection of any point B on the elastic curve from the tangent to
this curve at other A is equal to the static moment about an axis through
origin 0 of the under the EI
M diagram between points A and B" (Fig.13)
If the origin at point a
yab = the deflection of point
A . W. r. t. the tangent at B
yab = EI
Am xc
as shown in Fig.13.a.
By
ABy
mA
EI
M
Cx
Figure (13.a)
Chapter (1) - Deflections 23
2
2
dx
yd =
EI
M
ya – yb = EI
Mx d x
ya = x.
or
dxxdx
ydB
A
.2
2
= dxxEI
MB
A
.
i.e.
BAy
dx
dyx )( = c
m xEI
A.
(2)
0A
By
0B
ABy
Ax
Bx
AAy
AAx
mA
EI
M
cx
Figure (12)
24 Chapter (1) - Deflections
Similarly if the origin at B
yba = c xEI
Am
as shown in Fig.13.b.
Ay
BAy
mA
Cx
EI
M
Figure (13.b)
Note that this deflection is measured in a direction normal to the original
position of beam. The two theorems can be used directly to find the
slopes and deflections of beams simply by drawing the moment diagram
for the loads causing deformation and then computing the area and static
moments of all or part of the corresponding EI
Mdiagram. The procedure
is illustrated in the following examples,
Chapter (1) - Deflections 25
Example (7)
Calculate the max. deflection of the given simple beam Fig.14 and sketch
the elastic curve
Solution
ymax. at mid span from elastic curve.
ymax = 2
yba - yca
yba = 3
2 16 8 4
1
El
= 0.1137 m
x
y
yba
yca
maxy
Ao
maxM =16 t.m
83 x4
2EI = 3000 t.m
CBA
2 t /m
a) B.M.D.
b) Elastic Curve
Figure (14)
yca = 3
2 16 4 1.5
1
El = 0.0213 m
ymax = 2
1155.0- .0216 = 0.036 m
26 Chapter (1) - Deflections
Example (8)
Find Yc for the given beam shown in Fig.15 and find ymax
EI = 3000 t.m2
Solution
8
bay =
3
cac yy
3yba = 8yc + 8yca
yc = 8
2yba - yca
15 t.m
452 2
75
C d
x
A B
A B
8 t
B
yba
CA
ca
c
y
y
Ao
a) B.M.D.
b) Elastic Curve
Figure (14)
8
3yba =
3000
1
2
75
3
10+
2
45 6)
8
2
= 3000
5.97100 = 3.25 cm
Chapter (1) - Deflections 27
yca = 3000
100 1
2
45 = 0.75 cm
yc = 3.25 – 0.75
= 2.5 cm
To get ymax
d = 0; at x from B
ydB
dy
A Bd
oBy
x
yab
c. Elastic Curve (yab)
d. Elastic Curve (ydb)
Figure (15)
yd = yAB . 8
x- ydB
ydB = 2
3 2
EI
xx (Fig.15.d)
B -d = 2
..3
EI
xx =
5.1 2
EI
x
B = 5.1 2
EI
x =
8
ABy
x = 19.37 = 4.04 from B,
yd = 2.8 cm. =ymax
Example (9)
Calculate yB and B for the
given cantilever beam
shown in Fig.16
(EI = 2500 t.m2)
Solution
a - b = EI
1
48
3
1
b = EI3
32
= 25003
32
ob
by
8 tm 3EI75
b
1 t /m
a
Figure (16)
28 Chapter (1) - Deflections
= 0.0043 radian
yb = 100
EI
3
3
32 = 1.28 cm
Example (10)
Find yB &B for the given cantilaver
in Fig .17
EI = 3000 t. m2
Solution
A-B = EI2
00.9= 0.0015 radian = B
yb = 200 EI2
9
= 0.3cm
b
yb
1t
a
92EI3
bo
Figure (17)
It will become apparent from these examples that these computations can
be facilitated by introducing some new ideas. The analogy based on these
ideas, discussed in the next method.
6. ELASTIC – LOAD METHOD
The ideas involved in the elastic – Load method can be developed by
considering the beam AB is loaded by elastic load which is equal to M/EI
diagram, the elastic load produce elastic reactions, elastic shear and
elastic bending moment at any section. Let beam AB which was
originally straight line and has been bent as shown in Fig.18.
Applying the second moment – area theorem givens;
yba = dxEI
MB
A
x)- (L
Chapter (1) - Deflections 29
x = x)- (L EI
Am
then
A = L
yba = RA
A = L
x- L
EI
Am = RB
a) B.M.D.
b) Elastic Curve
c) Elastic Load
AmAR BR
BA
oc
c
oByba
BA
oA cay
cy
MEI
MA B
M
BA
Figure (18)
If we imagine that the M/EI diagram represents a distributed vertical load
applied to a simple beam AB as shown in Fig.18. The computation for the
RA RB
30 Chapter (1) - Deflections
vertical reaction at A of the imaginary beam would yield a value exactly
equal to the value of A computed above, then:
A = RA
Where RA is the elastic reaction at support A. in the same time equal to
elastic shear at A with the same sign. Similarly, B = RB = elastic shear at
B. This analogy can be carried still further if we consider the form of
computation for c and yca . Note that c given the slope of the tangent
with reference to the direction of the chord AB of the elastic curve and
that yca gives the deflection of point c from the same chord AB. Consider
first c , then
c = A - (A - c)
= RA – (Area of EI
M digram between A and C
= Eastic shear at C from left
Further, "The slope of the tangent to the elastic curve at any point is
equal to the corresponding ordinate of the elastic shear diagram for
the imaginary beam AB loaded with the M/EI diagram."
Similarly; from Fig.18.d
yc = A . a - yca
= RA . a - yca
Where yca is the first
moment of M/EI diagram
between points A and C
about point C. hence
Figure (18.d)
yc is the elastic bending moment at point C form left side or;
"The deflection at any point along an end supported beam AB is
equal to the value of the elastic bending moment at that point'.
Sign Convention
In order to take full advantage of the elastic, load method, it is desirable
to follow the same sign convention and principles as those used in
drawing regular load, shear, and bending moment diagrams. Since
Chapter (1) - Deflections 31
downward elastic loads are considered as positive in such computations,
positive M/EI ordinate downward loads. Plotting shear and bending
moment diagrams for the imaginary beam according to the usual beam
convention, positive bending moment indicate deflection below the chord
AB. Likewise, positive shear indicate that the slopes with clockwise or;
"Positive elastic shear mean positive angle of slope and positive
elastic bending moment mean positive deflections".
Example (11)
Calculate the deflection and
angle of rotation at point c, for
the given beam shown in Fig.
19. Sketch the elastic curve
(EI = 6000 t.m2)
Solution:
by using principle of supper
position i.e B.M.D. as shown
in fig. due to uniform load +
due to concentrated load.
EI9
+6
2EI6x3
36EI
+
x23 EI
3x18
18
4t
B
4 t /m
CA
B.M.Ds.
Figure (19)
c = Elastic shear at c from left side
= 0 9
- 36
- 9
36
EIEIEIEI
yc = Moment of elastic load at c
=
3
3
1 - 3
9 3
8
3 - 3
36
EIEI
= EI
2 9
9
15
36
EI
32 Chapter (1) - Deflections
= cm 100 5.85
EI
= 1.425 cm
Example (12):
Find yc & c for the
given beam shown
in fig.20 sketch the
elastic curve
(EI = 6000 t.m2)
Solution:
W1 =
EI
16
EI 2
8 4
ra1 = EI 2
16
W2 =
EI 2
3
2
3
= EI 4
9
W3 =
EI
8 16
3
2
Figure (20)
ra2 = EI 3
8 16
W4 = EI 2
3 15
W5 = EI 8
9 2 3
3
2
= EI 2
9
c =
EI 4
9
EI 3
16 -
EI 3
8 16
-
EI 2
9 -
EI 2
45
= EI 12
151 = 0.0020 radians
1y
w 45w
x 233
w =16x8
2w =162w
2ar
=ra1163 16x2
3
316x8
w =2 t /m
4t
Bw =2 t /m
C
A
16 t.m
Chapter (1) - Deflections 33
yc = EI
1
2
3
2
9 - 1
2
45 - 3
3
8 16 1
4
9 3
3
16
= (- 16 + 2.25 + 128 – 22.5 – 6.75) EI
100 cm.
= 1.416 cm
FRAME DEFLECTION:
The moment–area, and elastic load methods can be used advantageously
in the computation of frame deflections. The frame deflections computed
in this manner, however, do not include the effect of axial changes in
length of the members. It is usually permissible to neglect the effect of
axial deformation in most frame–deflection problems.
Example (13)
Compute the deflections of the shown frame in Fig.21. Hence sketch the
elastic curve
Solution
The deflection at points A and C are equal to zero then;
Angles of slopes
W1 = 2
7.2
EI 2
6.21 = 38.88/EI
W2 = 2
7.2 .
EI 2
4.14 = 25.92/EI
RA = (7.2) EI
2.4 25.92 - 3.6 38.88
= 10.8 / EI
Rc = 2.16 / EI
A = RA
= 10000
80.10 = 1.08 10
-3 rad
= 0.0619
34 Chapter (1) - Deflections
c = 10000
16.2 = 2.16 10
-4 rad
= 0.012
EIM
deformed frame
Diagram
B.M.D.
RC
A
AR
C
CA
0.24
y =2.3cmb
4= 21.6X10
cocoA
+
2EI21.6
2EI21.6
2EI7.2
-
+
2EI14.4
+
14.4
14.4
EI = 10000 t.m2
B
I
2I
12t12t
AD
C
E
c
E
Figure (21)
Chapter (1) - Deflections 35
Deflections:
yB = (10.8 (3.6) – (19.44 – 6.48) 1.2) EI
1
= 10000
328.23
= 0.0023 m = 0.23 cm
To get ymax at = 0, assume the position at distance x from A then
= EI) 2( 2
x
7.2
4.14
8.10
EI
2
x
EI 2 3.6
21.6 -
2
= 10.80 + .5 x2 – 1.5 x
2
i.e;
x = 3.28 m ,
ymax = 3.28 8.10
EI
3
3.28
EI
3.28 -
2
= 0.24 cm
2
1w
10.8
y =2x
19.44
6.48
BA
10.8
BA C
RCAR
w
Since the joint at c is rigid, the tangents to the elastic curves of all
members meeting at that joint rotate through the same angle. Since there
is no bending moment in the column, the elastic curve is a straight line
inclined at the same angle as the tangent of the elastic curve of the beam.
E = c. 3.6 = .078 cm
36 Chapter (1) - Deflections
Example (14):
Compute the slopes and
deflection of the given
compound beam shown in
Fig.22; compute the
maximum deflection.
EI = 3000 t.m2
Solution
After studying the sketch of
the elastic curve, it is
apparent that yb can be
computed by applying the
second moment – area
theorem to the part AB. This
deflection establishes the
position of chord BC. The
deflections and slopes of
beam BC can be calculated
by the elastic load method
applied to an imaginary
beam of span Bc.
C
Figure (22)
EIyb = 1.2 2
1.8 36
1.5
2
.9 18
= 1.7 cm
B = EI
5.40
Rotation of chord BC
BC = 540
7.1 = 13.510
-3 rad.
The point of maximum y occurs where the tangent to elastic curve is
horizontal i.e., where the tangent slopes down to the right w.r.t. the chord
BC or
Chapter (1) - Deflections 37
EI m = 4.5
77.24 = 7.92
7.92 = 110.4 - 2
x
6.3
72
x2 = 10.248
x = 3.20 m
EI my = 110.4 (3.20)
- 3
(3.2) 10 3
= 244.05
EI ym = 244 + 7.92 3.2
ym = 3000
39.269
= 8.98 cm
64.8
mEI0
my
EIt.m72
EI
40.5EI
EI
A
18
B
54
Figure (22)
Example (15)
Compute the deflections at point B for the given frame shown in Fig.23
Solution
Joint c is rigid hence;
c = 3
2
EI 2
7.2 108
= EI
259 = 25.92 10
-3 rad.
EIB = c (3.6) (3.6) 3
2
2
3.6 108
= (259.2 3.6 + 466.56)
38 Chapter (1) - Deflections
B = 13.99 cm
Note: Compare the elastic curve with that given in example 13.
B
C
2EI = 10000 t.m
108tm.
108tm.
30t
co
co
co
A
A
a) B.M.D.
b) Elastic Curve
Figure (23)
Chapter (1) - Deflections 39
7. THE CONJUGATE BEAM METHOD
Form the previous examples; it is apparent that deflection computations
for any beam can be handled effectively by a proper combination of the
use of the moment area theorems and of the elastic load method. The
procedure involved in this combination, however, may be identified as
nothing more than a slight extension and variation of the elastic load
method. This extension is called the conjugate – beam method. In order to
develop these new ideas, consider the beam shown in figure 24.
Figure( 24)
40 Chapter (1) - Deflections
Fig.24.a shows the real beam and its loading. Also shown by the dashed
line is the deflection curve, which has certain notable characteristics
determined by the type of supports and by the hinge at B:
1. At support A both deflection and slope of the elastic curve are zero.
2. At support C the deflection is Zero but the elastic curve is free to
assume any slope required; and
3. At hinge B, there can be a deflection, and in addition, a sudden
change in slope can occur between the left and right sides of the
hinge.
The objective is to select a conjugate beam i.e., a corresponding beam,
which has the same length as the real beam but is supported and detailed
in such a manner that when the conjugate beam is loaded by the
EI
Mdiagram of the real beam as an (elastic) load, "the elastic shear in the
conjugate beam at any location is equal to the slope of the real beam at
the corresponding location and the elastic bending moment in the
conjugate beam is equal to the corresponding deflection of the real
beam". Note that these slopes and deflections of the real beam are
measured with respect to its original position; i.e. they are the true slopes
and deflections. It is always possible to select the proper supports for the
conjugate beam to achieve the desired objective by simply noting the
known characteristics of the elastic curve of the real beam at its supports
or at any special construction features, such as the hinge at B. To
illustrate the selection of the supports of the conjugate beam, consider the
beam in the following Fig.25
Chapter (1) - Deflections 41
Figure (25) Real Loaded Beam
At A, there is neither slope nor deflection of the real beam; therefore,
must be neither shear nor moment at this point of the conjugate beam.
That is, point A of the conjugate beam be free and unsupported. At C,
there is slope but no deflection of the real beam; therefore, there must be
shear but no moment in the conjugate beam. That is, point C of the
conjugate beam must be provided with the vertical reaction of a roller
support. At B, there is deflection and a discontinuous slope in the real
beam; there for, a vertical reaction must be provided to create the sudden
change in shear in the conjugate beam, and it must be capable of resisting
bending moment. That is, point B of the conjugate beam is loaded and
purported as shown in fig.26.
Figure (26) Conjugate Loaded Beam
These and similar considerations lead to the rules shown in Fig.27, 28,
and 29.
Illustration of selection of the supports and details of typical conjugate
beams are shown in Fig.28, and 29.
Not that statically determinate real beams always have corresponding
conjugate beams which are also determinate. Statically indeterminate real
42 Chapter (1) - Deflections
beams appear to have unstable conjugate beams. However, such
conjugate beams turn out to be in equilibrium since they are stabilized be
the elastic loading corresponding to the M/EI diagram for the
corresponding real beam.
Figure (27) Selection of Supports and Details of Conjugate Beam
Chapter (1) - Deflections 43
a b
dcba
b c
b c d
a
ab
fd eca cfe
d
d
d
c
c
c
c
b
b
b
b
a
a
a
a
a
a
bcb
a
b ca
cb
ba
a
b c
cba
ba
ba
stabilized by elastic loadUnstable equilibrium but
Ind
eter
min
ate
Str
uct
ure
sD
eter
min
ate
Str
uct
ure
s
Figure (28)
a b
dcba
b c
b c d
a
ab
fd eca cfe
d
d
d
c
c
c
c
b
b
b
b
a
a
a
a
a
a
bcb
a
b ca
cb
ba
a
b c
cba
ba
ba
stabilized by elastic loadUnstable equilibrium but
Inde
term
inat
e S
truc
ture
sD
eter
min
ate
Str
uctu
res
Figure (29)
44 Chapter (1) - Deflections
Example 17
Calculate the deflection and the slope angle at points A, C, B, D, for the
given beam shown in Fig.30, draw elastic curve.
El = 4000 t.m2
Solution
1. Draw B. M . D. For actual beam
2. Construct the conjugate beam
3. Calculate Q & M at points A, B, C, & D as
BeamCONJ
M . D
EI
2EI
14EI
CA BD
D
EI6
4EI
EI10
10EI
aQ
36EI
12EI
EI1212
EI
EI36
9 t.m
4 t.m
c
2t
a 2 t /mb
EI3
18
Figure (30)
point A, To get A at conj. Beam
MB = O
Chapter (1) - Deflections 45
El
12 2 -
El
36 3 + QA. 6 = O
A = El
14
MA = 0.0
Hence
QA = A
= El
14 = 0.0035 radians
MA = zero
Point B
B = QB
MA = 0
QB = (El
12 4 +
El
36 3 )
6
1
QBleft = El
10 = -0.0025 radians
MB = YA = zero
Point C, From left side
QC = EI
14+
EI2
32-
3
2
EI
93
= EI
1
c = - 0.0025 radians (anticlockwise)
yc = Mc
46 Chapter (1) - Deflections
= EI
1( 14 3 + 3 1 – 18 3
8
3
= EI
75.24 m
= 0.618 cm (downward)
Point D, from part B D
D = Q
= El
6 = 0.0015 radians (antilock wise)
yD = MD = (EI
10 2 +
EI
4
3
2 2)
= EI
67.14
= - 0.36 cm ( upward)
bLeft
cY
=0.0035a Ac
b
D
DY
Figure (30) Elastic Curve
Chapter (1) - Deflections 47
Example 18
Find A , C , B ,yd , draw
elastic curve and locate the
deformations on the elastic
curve. For the given beam
fig.31 El = 8000 t.m2
Solution
By using conjugate beam
Method
A = 8000
23 rad.
= 2.875 10-3
rad.
clockwise
B =8000
19
= -2.37510-3
rad.
anticlockwise
D = EI
15
= -1.875 10 -3
rad.
anticlockwise
c = EI
391823
4
12
18
9
84
9
9 t.m
4t 2t
D
4 t.m
bc
6 t.m
a 2 t /m
O aa
0.53
c
23
a
18 9
c
D
O
bd
O b Y
a
23
3
18 36
b
19 4 d
18
Figure (31)
48 Chapter (1) - Deflections
= EI
1 =-0.125 10
-3
yc = EI
10016125.118323 = 0.53 cm Downward
yd = -( EI
3
44219
) =-0.408 cm Upward
Example (19)
Find yc , c , A , B for the shown beam in Fig.32
EI = 3000 t. m2
L = 4m P = 4t
Solution
A = EI
5.2
= 0.83 10 -3
B = .83 10 -3
c = zero
( from symmetry )
pL/8pL/8pL/4
B.M.D
EIB.M.D
modefied
2.5/EI 2.5/EI
1/EI1/EI 1/EI 5/EI 1/EI
ba
2/EI 2/EI2/EI
I
2I
I
P
ba
Figure (32)
yc = 3000
1( 2.5 2 -1 1.33 – 1 0.5 - 0.5 - 0.5 0.33)
= 3000
3 = 0.001 m
= 0.10 cm
Chapter (1) - Deflections 49
Example (20)
Calculate the deflections and the angles of rotations at the given points
for the shown beam in fig. 33 . ( EI = 8000 t.m2 )
AO
Oe
Oe eO edcA b
10t.m
4t.m
4t.m
2t
2t
4t
4t.m
4t.m
10t.m
2II
5t4t
c d ebA
__EI8 20
10-2.67
7.3310-5.334.67
8.33
8
2.33
EI __
EI __
EI __
EI __
EI __
EI __
EI __2
Figure (33)
Solution
Elastic reactions:
rc = 10 – 5.33 = 4.67 / EI
50 Chapter (1) - Deflections
re = 10 – 2.67 = 7.33 / EI
rA = EI
33.2
rB = EI
33.8
Point A , B
QA = rA = A = 0.25 10-3
radians( clockwise)
QBleft = EI
833.2
= -5.67 / EI = - 0.75 10-3
rad.
QBright = + EI
67.2
yA = MA = zero
yB = MB = (- 4.67 2 + 2 3
4)
EI2
1
= -0.10 cm (Upward)
Point C
c left = cright
= EI
67.4 = 0.58 10
-3 radians
yc = Mc = zero
Point d
Qd = EI
33.78
d = 0.085 10 -3
rad.
Chapter (1) - Deflections 51
yd = ( 7.33 4 – 8 3
4)
EI
1
= 0.235 cm (downward)
Point e :
e =Qe = - EI
33.7 = 0.915 10
-3
ye = Me = zero
8. THEORY OF REAL WORK
If a variable force F moves along its direction dL, the real work done is F
dL. The total work done by F during a period of movement may be
expressed by
W = 2
1
L
L
dLF
Where L1 and L2 are the initial and final values of position. Consider a
load gradually applied to a structure. Its point of application deflects and
reaches a value as the load increase from 0 to N. As long as the
principle of superposition holds, a linear relationship exist, between the
load and the deflection a represented by the line Oa in the following
figure (Fig.34)
52 Chapter (1) - Deflections
C
da
b
FLoad
deflectionO
Fig. 34
Figure(34)
The total work performed by the applied load during this period is given
by:
W =
0
FdL
= 2
1N.
Which is equal to the area of the triangle Oab in Fig.34. If further
deflection d, caused by an agent other than N, occurs to the structure in
the action line of N, then the additional amount of work done by the
already existing load P will be;
dW = N.d
Which equals the rectangular area abcd shown in Fig.34. Similarly the
work done by a couple M to turn an angular displacement d is M.d .
The total work done by M is:-
Chapter (1) - Deflections 53
W = 2
1
Md
Also, the work performed by a gradually applied couple M accompanied
by a rotation increasing from O to is given by :=
W = 2
1 M.
Now consider a beam subjected to gradually applied force. As long as the
linear relationship between the load and the deflection maintains, all the
external work will be converted into internal work or elastic strain
energy. Let dW be the strain energy restored in an infinitesimal element
of the beam as shown in the following figure (Fig.35)
Figure(35)
We have dW = Md2
1
If only the bending moment M produced by the forces on the element is
considered significant. Using;
dx
d =
EI
M ,
EI
M
dx
yd2
54 Chapter (1) - Deflections
Or d = dx EI
M
We have
dW = EI
M
2
xd . 2
For the loaded beam, its longitudinal axis taken as the x-axis, we let dL =
dx. The total strain energy restored in the beam of span L is, therefore,
given by:
W = L
EI
M
0
2
2
xd .
For a truss subjected to gradually applied loads, the internal work
performed by a member with constant cross sectional area A, length L,
and internal axial force N is:
dW = EA 2
L d . N2
, ( E = LL
AN
/
,
)
The total internal work or elastic strain energy for the entire truss is:
W = EA 2
L . N
2
In some special cases deformations of structures can be found by equation
of conservation of energy:
External work (WE) = Internal work (WI)
Or WE = WI
Example (19)
Find the deflection at free end of the loaded cantilever beam shown in fig.
36.
Chapter (1) - Deflections 55
Solution
WE = 2
1 P. b
WI = L
EI
M
0
2
2
xd .
Figure(36)
= L
EI0
2
dx 2
Px -
= EI 6
P
32 L
Setting
WE = WI
b = EI 3
3pL
Note that the method illustrated is quite limited application since it is only
applicable to deflection at a point of concentrated load. Furthermore, if
more than one load is applied simultaneously to a structure, then more
than one unknown deformation will apear in one equation, and a solution
becomes impossible. Thus, we do not consider this as a general method.
8.1. Deformation and Work due to Normal Force N
From hook's law
E =
=
/
dx
d
AN
d = EA
dxN .
i.e. dW = 2
. dN
dW = EA 2
.2 dxN
56 Chapter (1) - Deflections
8.2. Deformation and work due to M
d = change in the slope
of elastic curve
d = EI
M xd .
dW = 2
d . M
dW = EI
M
2
xd . 2
8.3. Deformation and work due to shearing force Q
= G
,
G = ) (1 2
E
where:
G = shear modulus, or shear
rigidity
dy
dy
Q
= poisson's ratio (3
1for steel and
6
1for concrete)
Using
= rA
Q , =
dx
dy
dy = .dx = rGA
Q. dx
Where Ar reduced area of cross section. It depends on the shape of cross
section:-
Ar = 0.9 A for rectangular section (steel)
Ar = 0.83 A for rectangular section (conc.)
i.e. dW = 2
dy . Q or dW =
G . A 2
dx .
r
2Q
Chapter (1) - Deflections 57
8.4. Deformation and work due to torsion
dW = Mt. d/2
= G
where
= PI
R .Mt
= . G
= G p, I
R .Mt
but = dx
dR
R.d = .dx
i.e. d = p
t
GI
M dx . ,
i.e. dW = 2
d . tM, d =
6 .
dx . t
pI
M
dW = p
t
I
M
G . 2
dx . 2
Where
Ip = polar moment of inertia
Ip = Ix + Iy
For rectangular cross sections;
d = t
t
IG
M
.
dx .
Where
It = torsional moment of inertia of the cross section.
For rectangular cross sections:
58 Chapter (1) - Deflections
It = 3
1a b
3(1–0.63
a
b
+ 0.052 5
5
a
b )
Where, a > b
For I – beams (steel) or channels;
It = 3
ab
3
For Hollow cross sections
It =
t
U
4F
2m
Where
Fm = closed area (dashed) between
the center line of the perimeter
of the area
U = length tangential to the
perimeter of the cross section
t = thickness of cross walls
For Hollow rectangular sections
It =
21
22
t
b
t
a 2
ba 4
For hollow sections with more than one
cell, neglect the interior webs.
Chapter (1) - Deflections 59
Hence for an element subjected to N, M, Q; and Mt
WI = EA 2
2dxN +
EI
M
2
dx2
+ r
2
GA 2
dxQ +
p
t
I
M
G . 2
dx 2
This is the general equation of real work where
EI = Flexural (bending) rigidity
EA = Normal rigidity
GAr = Shear rigidity
8.5 Deformation due to temperature
a- uniform temperature change:
The strain due to temperature change t is
t = . t
Where:
= Coefficient of temperature deformation
= 1.2 10-5
for steel
= 1.0 10-5
for concrete
L = . t. L
t = temperature change
L = length of member
L = free elongation
If a member is not free to deform, then the stresses would arise in the
member with value. From Hook's low
= E. t = E. . t
For example if two hinged concrete beam with span L and
t = 40,
= 510
40 210000
= 84 kg/ cm2 (big)
60 Chapter (1) - Deflections
b- Non- uniform temperature change
The uniform temperature change 2
t t 21 causes a uniform strain
t = . 2
t t 21
And the non-uniform change of t causes a rotation angle:
dt = h
dL t. .
Note
In case of the length is dL
Work due to Uniform rise of Temperature
W = L N. L
0
= L
0
dL . N. t
= dL .N t L
O
= t (area of normal force diagram)
Work due to Nonuniform rise of Temperature
W = L N. L
O
= d M. L
O
= t (Area of N. diag.)
+ h
t (Area of M. diag.)
Chapter (1) - Deflections 61
9. METHOD OF VIRTUAL WORK
Bernoulli's principle of virtual work for rigid bodies is the most general
and direct method for computing the deflections of all types of structures.
This method is based on an application of an alternate form of the
principle of virtual displacements, which was originally formulated by
John Bernoulli in 1717. This alternate form of these ideas can be
developed from the following considerations.
Figure(37) Translation of Rigid Body
Consider a rigid body shown in fig 37 which is in static equilibrium under
a system of forces Q. In this sense, a rigid body is intended to mean an
undeformable body in which there can be no relative movement of any of
its particles. Suppose first that, as shown in the above fig., this rigid body
is translated without rotation a small amount by some other cause which
is separate from, and independent of, the Q-force system. Upon selecting
an origin O and two coordinate reference axes x and y, this translation
may be defined by o, the actual translation of the origin O, or by the two
components ox and oy in the x and y directions, since the body is rigid,
every point on the body will translate through exactly the same distance
at point O. All the Q–forces can be resolved into x and y components,
62 Chapter (1) - Deflections
designated as Qnx and Qny for any particular force Qn. Since these Q
forces are in static equilibrium, the following equations are satisfied by
the components of these forces:
Qnx = 0
Qny = 0
(Qnx. yn – Qny. xn) = 0
Consider now work WQ done by only these Q forces. All Q forces may be
assumed to maintain the same position and direction relative to the body
and to each other and hence to remain in equilibrium during the
translation. Then we can write,
WQ = (Qnx. ox – Qny. oy) = 0
= o Qnx + oy Qny = 0
The total work done by the Q forces in such a case is equal to zero.
Similarly, the total work done by the p forces during a small of the rigid
body above point 0 also equal zero. Hence the following Bernoulli's
principle, it may be stated as:
"If a rigid body is in equilibrium under a system of loads, and remain so
when it is subjected to any small displacement, the virtual work done by
the P- force system is equal to zero".
Bernoulli's principle of virtual work for rigid bodies can now be used to
develop the basis for the method of virtual work for computing the real
deflections of structures. This method is applicable to any type of
structures-beam, truss or frame, planar or space frameworks. For
simplicity, however, consider any planar structure such as shown in the
figure 38.
Chapter (1) - Deflections 63
Figure(38) Planar Structure in Equilibrium under Q-force System
For the shown structure, it may by stated that;
"If a deformable structure is in equilibrium under a virtual P-load system
and remains so while it is subjected to a small virtual deformation, then,
the external virtual work (We) done by the P–load system as it moves
through the virtual displacement is equal to the internal virtual work (Wi)
done by the internal straining actions produced by Q–load system as they
move through the virtual deformation"
We = Wi
The term virtual deformation means that the action producing the
deformation is independent of the Q–load system or that it is caused by
some additional action. Such action may be another load system, hence,
referred to a P- load system, temperature, error in lengths of members, or
other causes or whether the material follows Hook's law or not. Also, the
virtual work refers to the work by the P-load system during the virtual
deformation.
It should be noted that the external virtual work (We) is the work
produced by the P-load system only as it moves through the virtual
displacement, and that the internal virtual work (Wi) is the work done by
the internal forces produced by the Q- load system as they move through
the virtual deformations. The equation We = Wi is the basis of the method
of virtual work for deflection computation. With some assumptions, it
may be used to calculate any deflection component at any point of a given
structure. This is done by choosing a P-load system consisting of a single
unit load and placed on the structure at the point where the deflection is
required and in its direction before the structure is subjected to the actual
64 Chapter (1) - Deflections
Q–load system. The Q-load system will then be considered as the source
of the virtual displacement, which in effect is the actual displacement
required.
9. APPLICATION
9.1. In cases of Beams and Frames
Figure (39)
The frame shown in Fig.39.a loaded by a Q-load system, the deflection at
point C is required. The procedure of solutions as follows;
a) The Q – load system is removed and a P–load system, consist of unit
load at point C, is placed.
b) The internal force diagram produced from 1t at C are drawn and
denoted by N1 , Q1 , and M1 diagrams
c) The Q–load system is added to the frame already loaded by the unit
load. The Q–load system produces another internal forces are denoted
by No, Qo, and Mo. The deformation in element of frame, dx Length
are as follow;
d = EA
.0 dLN
dy = L d . GA r
0Q
d = EI
.0 dLM
dtor = G .I
.
p
dLM t
Chapter (1) - Deflections 65
The actual load (Q–load system) causes a deformed shape with different
deflection at any point along the beam span. The deflection at C denoted
by c.
d) Consider that the unit load at C is the original load and that the Q–
load system to be the source producing the virtual displacement, then
We = 1 c
And the internal virtual work in the length dx of beam is
dWi = M1 d + Q1 . dy + N1 . d.
And the total internal work is
Wi = L
O
M1 d + L
O
Q1 . dy + L
O
N1 . d.
Hence form We = Wi and substitute for the value of d , dy , and d;
1c = L
O
EI
01MM d x +
L
O
EA
01NN d x +
L
O
r
0 1
GA
QQ d x
For the most member subjected to bending
moment, however, the deflection due to shear
force is small, then:-
1c = EI
01 MM d x
If the angle of rotation is required we can
applied by unit moment at desired point
(Fig.40).
1c = EI
01 MM d x
Figure (40)
66 Chapter (1) - Deflections
Where M1 is the bending moment diagram due to 1 t.m at point C.
If the horizontal
displacement is required at
point C, we can apply unit
load at C as shown in
Fig.40.c.
1.C = dxMM 01
Figure (40.c) hl. Displacement
If the relative vertical displacement is required, the unit loads are as
shown in Fig.41.a and b.
a. Relative angle of slope at C b. Relative displ. Of c and D CD
Figure (41)
10.EVALUATION OF INTEGRAL dxMM 10
This integral which appears in the computing of deflection, is actually an
integral of two bending moment diagrams M1 and Mo. At least either the
M1 or Mo – diagrams are a straight line while the other may be a single
straight line, broken line or curve. It can be readily evaluated by use of
the following simple formulae;
10.1. Mo–diagram is a curve and M1–diagram is linear
Chapter (1) - Deflections 67
L
O
M1 Mo dx = A.C
where:
A = Area of Mo.D
C = ordinate of linear M1 .D opposite to centroid of Mo.D
10.2. Mo. D and M1. D are Both linear
a) L
O
M1 . Mo dx = (Area of M1 or Mo) ordinate of Mo or M1
respectively opposite to centroid. L
O
M1 Mo dx = 3
L (ac + bd +
2
1 ad +
2
1 cb)
68 Chapter (1) - Deflections
b) L
O
21M d x =
3
L (a
2 + b
2 + ab)
c) L
O
21M d x =
3
L a
2
d) L
O
21M d x = L a
2
M . D1
1M . D
1M . D
L
a a
L
a
C a
b
1- Mo and M1 Diagrams are both second degree Parabolas
L
O
M1 Mo dx = 5
4 A1 .b
= 5
4 A2 .a
= 15
8 Lab
where
A1 = area of Mo. D
A2 = area of M1 . D
2- Composite M1-Diagram
L
O
21M d x =
L
O
(M2+M3)2dx
= L
O
22M d x +
L
O
23M d x +
L
O
2 23 M M d x
Every integral evaluated by the same above methods.
Chapter (1) - Deflections 69
Example (21)
Calculate the vertical deflection at
point d and the angle of rotation at
point A for the given beam. Shown
in Fig.42 (EI = 8000 t.m2)
Solution: Draw MO . D
deflection at d, draw M1 .D hence;
1 yd = EI
dx . . 1MM o
yd = 2
2 8 2 (-
8000
1
2) 3
2
2
2 4 8
= 0.33 cm
angle of rotation at A
put 1 t.m at A; draw M1-diagram
Figure(42)
1 A = dx . EI
. 1MM o
=
5.0
2
8 8
3
1
2
8 4 -
8000
1
= 1.33 103 radians (clockwise)
Example (22)
Determine the vertical deflection at point n, the horizontal displacement
at B and the angle of rotation at C. for the given frame shown in Fig. 43
(consider effects of M,N and Q)
EI = 25200 tm2 , EA = 63000 t, GAr = 49200 t.
70 Chapter (1) - Deflections
Figure(43)
Solution:
1- Draw Mo, No and Qo
Figure (43.a)
a) Vertical deflection at n
Figure (43.b)
Chapter (1) - Deflections 71
1n = 30 2
2 1
3
2
2
2 30
25200
2
2 49200
.5 2 15
63000
0.5 5 15
= .0099 m = 0.99 cm
b) Horizontal displacement at B: (put 1t at B)
Figure (43.c)
1B = EI
01
MM .d x +
EA 0
1
NN . d x +
r
10
GA
QQ d x
= 0 0.625 63000
5 15 -
2
5
2
4 8 30
25200
1
= 0.017 m =1.7 cm
c) The angle of rotation at C (put 1 t.m at c)
Figure (43.c)
t
72 Chapter (1) - Deflections
1 c = EI
. 10 MM .d x +
A.E
. 10 NN .d x +
G A
.
r
10 QQ .dx
1 c = 0 8
1
63000
5 15 - 0.5
2
4 8 30
25200
1
= 0.0035 radian clockwise
Note.
a) due to load
1. = M1 d + N1 . d. + Q1 . dy
= M1. EI
.0 dLM +
EA
dL 01NN
+ p
0 1
GI
b) due to temperature
1. = N1 . d. + M1 d
= . t. N1.d L +h
t . M1. d L
Example (23)
Find the horizontal displacement of support B (in example 22) due to
uniform rise in temperature 20 C (Fig.44) = 1 10-5
WE = wi
Solution
Mo = zero
No = zero
Qo = zero
d = . tL
d = zero
dy = zero
1 . B = N1.d. + M1d
= N1 . d.
= N1 . d.
= . t. N1 .L.
Figure (44.a)
Chapter (1) - Deflections 73
= 1 10-5
20 (1 8 + 0.625 5)
= 0.22 cm
Example (24)
For the frame shown in Fig.44, calculate the horizontal displacement at B
due to vertical downward displacement at A equal to 1.0 cm as shown in
Fig.44.c.
Figure (44.b)
Solution
a) From the external work WE equal to internal work WI equal zero, then
WE = WI = 0
i.e. WE = 0
1.B + 0.625 1.0 = 0
B = -0.625 cm (to left)
b) Due to vertical and horizontal movements = 0.5 cm to outward. at A.
From WE = 0
1.B + 0.6250.5 +10.5 = 0
B = - 0.8125 cm (to left)
74 Chapter (1) - Deflections
Figure (44.c)
Example (25)
Find the change of the angle at
C due to a rise in temp. of 20 C
at interior fibers and 40 C at
the exterior fibers. For the
shown frame in Fig. 45
(Section 30 100)
= 1 10-5
/C
Solution:
d = 2
21
= . 2
)t (t 12 . dL
= 30 10-5 dL
Figure(45)
d = .h
)t (t 12 . dL
1t
1t
0.625 t
Chapter (1) - Deflections 75
d = 00.1
01 1 5- (40 -20) . dL
( -ve sign because it is in the same
sense of – ve B.M)
change of the angle at C = c
1xc = M1 d + N1 . d
= -20 10-5
M1 dL + 30 10-5 N1 . dL
= 2 – 20 10-5
5-10 30 10.44 .991 10.44 2
1 7.0
2
7 7.0
= - 4.8 10-3
rad.
i.e. increase in angle at C = .0048 rad.
Example (26)
Find B , c , d , B, yc, yd , xd for the shown frame in Fig.46
EI= 10000 t.m2
Figure(46)
Solution:
1- Draw Mo. D
76 Chapter (1) - Deflections
Figure (46.a)
2- Draw M1-diagram for each case.
d bc
Figure (46)
Chapter (1) - Deflections 77
a) angle of rotations
1 = EI
dx.M. M o1
1b = (12 8) EI
1 = 9.6 10
-3 radians
1 c =
2EI 2
1 3 12
EI
90 =
EI
89
= -310 8.9 rad.
d = c =8.9 10-3
rad.
b) displacement
1 = dx . EI
M. M o1
1 b = 100
8 0.5
EI
8 12 = 0.384 cm (xb = xc)
1 yc =
2EI
5 4 12 6
EI
4/2 8 - 8 12
= 5.4 cm. (yc = yd)
1 d = 6 2EI
4 5 4 - 5
3 EI
8 2 - 8 12
= 1.4 cm,
Example (27): Find the horizontal displacement at point b for the given frame shown in
Fig.47.
El1 = 4000 t.m2
El2 = 8000 t.m2
Figure (47)
Solution
B1 = dx . EI
M. M o1
78 Chapter (1) - Deflections
= 4000
1 4
3
2
2
5 18( 2
8000
4- ). 6 4
3
2 4 (18
= - (.06 + 0.044)
= - 0.104 m
= - 10.4 cm (to right)
Example (28)
For the given hinged arch
shown in Fig.48 calculate
the vertical deflection at C
due to horizontal`
displacement at B = 0.5
cm (to Left)
Figure (48)
Chapter (1) - Deflections 79
Solution:
Apply 1 ton at c
We = Wi = 0
1. yc – 1.5 0.5 = 0
yc = 1.5 (.5)
= 0.75 cm
Figure (48)
Example (29):
For the given frame shown in Fig.49
with variable moment of inertia,
compute the displacement of point B
relative to point A. EI = 10000 m2 . t
Solution:
1) Drow Mo.D due to given loads.
2) To find BA , apply a unit loads
at B and A in direction of AB, and
draw M1. D.
BA = EI
. 1 dxMM o
Figure (49)
A
12
80 Chapter (1) - Deflections
= 1.8) 3
6 9
3 3
6 3.33 6
3
6(
EI
1
= 0.599 cm
Positive sign, which mean that B moves away from A in direction of AB.
Example (30):
For the shown arched–frame shown
in Fig.50, has a parabolic arch,
Determine the horizontal
displacement at B.
EI = 100000 t.m2
Solution:
1) Draw Mo.D due to given load.
2) Drow M1. D due to unit load
at B
Figure (52)
B = dxMM o
EI
. 1
= - 1.4 cm (to right)
Chapter (1) - Deflections 81
Example (31):
For the shown cantilever, Fig.51, it is
required to calculate yb.
E = 200 t/cm2,
Solution:
EIo.B = M1 Mo dxIo I
= M1 Mo )( I
dLIo
Assume
Io = 12
1 3.0 3
Figure (51)
Io = .025 m4
(Io = I at point A)
EIo = 50000 t.m2
I
oI =
3
d
od
The following Table gives the results
Part D
(m) I
oI
Mo
(t.m.)
M1
t.m. Mo . M1
I
oI
1
2
3
4
1.0
0.85
0.70
0.55
0.40
1
1.628
2.915
6.011
15.62
-50.0
-37.5
-25.0
-12.50
0
-5.0
-3.75
-2.50
-1.25
0
250.00
194.59
127.53
51.65
0
623.785
B = 0EI
1.25 785.623 100 = 1.56 cm
82 Chapter (1) - Deflections
Example (32):
For the shown cantilever in Fig.52 with variable
moment of inertia, calculate the vertical defection
and rotation of point C.
Solution:
The structure is divided into number of divisions
as shown
depth
cm
Point
50
80
120
C1
B
A
Figure (52)
E = 200 t/ cm2
B = 30 cm
Choosing
Io = Ic
= 12
50 03 3
= 6250
EIo = 6250 t. m2
1.yc = EI) / (L EI
M . M
o
o1
= L I
I M M
EI
1 oo1
o
1.c = L I
I M M
EI
1 oo2
o
Figure (52)
Calculations are shown in the follow Table
Sec L
m
d
cm
3
1
oo
d
d
I
I
M0.
t.m. M1 yc M2 c
C
1
2
B
0.5
1.0
1.0
0.5
50
60
70
80
1
0.578
0.364
0.244
0
-3
-8
-15
0
-1
-2
-3
0
1.73
5.83
5.50
-1
-1
-1
-1
0
1.736
2.916
1.83
Chapter (1) - Deflections 83
B
3
4
5
A
0.75
1.5
1.5
1.5
0.75
80
90
100
110
120
0.244
0.172
0.125
0.094
0.072
-15
-18
-21
-24
-27
-3
-3
-3
-3
-3
8.20
13.9
11.81
10.14
4.39
-1
-1
-1
-1
-1
2.146
4.63
3.937
3.38
1.46
61.53 22.64
yc = 100 6250
53.61 =0.985 cm
c = 6250
64.22 = 0.003622 rad. = 0.003622
180
= 12\ 27
\\
Example (33):
For the given beam, Fig.53, fixed at
A and spring support at B. If the
vertical deflection at B = 2 cm
draw the S.F and B.M. Ds EI =
2000 t.m2
(Hint: this beam is satically
indeterminate)
Solution:
1) Draw Mo. D due to given
load. By assume the reaction at B =
RB
(If we know RB, one can Draw
B.M.D)
2) Draw M1. D due to unit load
at B
1B = EI
1 . 1 dMM o
100
2 1 = 4.5 6 36
3
1(
1
EI
) 4 6 2
y 6 - 4 6
2
12 B
100 = 468 – 72yB
yB = 4.94 t.
Figure (53)
A
M = - 48 + 6 4.94 = - 18.33 t.m
84 Chapter (1) - Deflections
DEFLECTION OF TRUSSES
Figure (54.a)
For the given truss shown in Fig.54:
1- Given Q load system then calculate No for each member
2- Apply P–load system unit load and calculate N1 for each member
The truss members have generally normal forces only (N), from the
virtual work equation we have generally:
1. = N1 . d + N1 . .t dx
= case of load + temp. effect
= all
members EA
L NN o1 +
affected
members
N1 . . t .L
3- To calculate displacement of any point in a truss, one apply the
virtual unit load in the direction of the required displacement at this point.
4- Calculation of Relative Displacement
Chapter (1) - Deflections 85
Figure (54.b)
The calculation relative displacement between two points c and d in a
truss, shown in Fig.54.b; apply the virtual unit loads in the two points c, d
in the direction c-d, calculate for this case of loading normal forces in
each member N1, and from the virtual work equation, calculate the
relative displacement.
1.cd = EA
L 01NN
5- Calculation of Member Rotation
Figure (54.c)
For a member rotation, apply unit moment at the member as shown in
Fig.54.c, to produce unit moment, the two virtual loads should be equal to
h
1 in case of member BE or (
cdL
1) in case of member c d.
Example (34)
For the given truss shown in Fig.55, compute the vertical deflection due
to given loads and due to rise in temperature t = 30 of the upper chord
members at point 7. (A
L = 20), E = 2000 t / cm
2.
86 Chapter (1) - Deflections
Figure (55)
Deflection at point 7
a) due to given load
1- It is easy for the given load 20t at point 7 to determine the forces in
all members (No)
2- For 1t at point 7 the forces in members (N1) is 20
1 from (No) then.
3- 1. 7 = L . EA
1NNo (
EA
L = 0.01 cm/t)
= 0.01 No. N1
The calculation is tabulated in the following table;
Chord Member No
tons
N1
tons EA
L
cm/t EA
L . 1NNo
Cm
Lower
chord
A-2
2-4
4-6
0
10
20
0
0.5
1
.01
.01
.01
0
.05
.20
upper
chord
1-3
3-5
5-7
-10
-20
-30
-.5
-1.0
-1.5
.01
.01
.01
.02
.20
.45
diagonals 1-2
3-4
5-6
14
14
14
.7
.7
.7
.01
.01
.01
.098
.098
.098
Verticals 1-A
3-2
5-4
-10
-10
-10
-10
-.5
-.5
-.5
-.5
.01
.01
.01
.01
.05
.05
.05
.05
Chapter (1) - Deflections 87
2
1 (7-6)
2
1 = 1.40 cm
7 = 2 1.4 = 2.8 cm down ward
b) due to temperature change
17 = N1 . .t.L
= N1 . L (10-5
) (30)
The calculation of 7 due to temperature change of upper chord is given
in the following table.
Member L
(cm) . t .L
(cm)
N1
(t) N1. . t .L
1-3
3-5
5-7
200
200
200
0.06
0.06
0.06
-0.5
-1.0
-1.5
-0.03
-0.06
-0.09
2
1 = -0.18
1 7 = 2 (-0.18) = - 0.36 cm (upwards)
88 Chapter (1) - Deflections
Example (35)
For the given truss shown in
Fig.56, calculate the vertical
deflection at joint 2 and the
horizontal displacement, at
the roller support.
A
L = 10 cm,
E = 2000 t/cm2.
Figure (56)
Solution
a) Vertical 2
The calculation may be tabulated in the following table. In this case (N1 =
5
No )
b) Horizontal displacement at A
Calculate 1N due to horizontal unit load at A
Member No N1 1N No. N1 No.
1N
A-B
B-1
A-1
A-2
1-2
-5
5
-5
-5
5
-1
1
-1
-1
1
-1.16
0
0
0
0
5
5
5
5
5
5.8
0
0
0
0
25 5.8
1. 2 = EA
L )N . N( 1o
= 2000
10 25
= 0.125 cm
1. A = EA
L )N . N( 1o
= 2000
10 .85
= 0.29 cm
Chapter (1) - Deflections 89
9. CASTIGLIANO' S SECOND THEOREM
In 1897, castigliano published the results of an elaborate research on
statically indeterminate structures in which he used two theorems which
bear his name.
Castigliano's second theorem
"In any structure the material of which is elastic and follows Hook's law
and in which the temperature is constant and the supports unyielding, the
first partial derivative of the strain energy with respect to any particular
force is equal to the displacement of the point of application of that force
in the direction of its line of action".
In this statement, the words force and
displacement should be interpreted also to
mean couple and angle of rotation,
respectively. Consider the beam shown in
fig.57, loaded gradually by forces P1, P2, ...
, Pn.
Figure (57)
Then the external work done by these forces is some function of these
forces. According to the principle of the conservation of energy, we know
that in any elastic structure at rest and in equilibrium under a system of
loads, the internal work or strain energy stored in the structure is equal to
the external work done by these loads during their gradual application.
Wi = We = F (P1 , P2 , ... , Pn) (1)
Suppose now that the force Pn is increased by a small amount (dPn), the
internal work will be increased by, and the new amount will be.
iW = Wi +
nP
Wi
. d Pn (2)
The magnitude of the total internal work, however, does not depend upon
the order in which the forces are applied; it depends on the final value of
these forces. Further, if the material follows Hook's law, the deformation
and deflection caused by P1 , P2 , ... , Pn. and hence the work done by
them are the same whether these forces are applied to a structure already
acted upon by other forces or not, as long as, the total stresses within the
elastic limit. If therefore, the infinitesimal force dPn is applied first and
the forces P1, P2, ..., Pn. are applied produces an infinitesimal
90 Chapter (1) - Deflections
displacement (dn), so that the corresponding external work done during
the application of (dPn) is a small quantity of the second order and can be
neglected. If the forces P1, P2, ... , Pn. are now applied, the external work
done just by them will not be modified owing to the presence of dPn and
hence will be equal to the value given in eqn.(1). However, during the
application of these forces, the point of application of dPn is displaced an
amount n. let the total amount of external work done by the entire system
during this loading sequence by We . Then,
eW = We + dPn. n (3)
But, according to the principle of conservation of energy, We must be
equal toiW ,
We + dPn. n = Wi + n
i
P
W
. dPn (4)
However,
We = Wi
n = n
i
P
W
(5)
This equation is the mathematical statement of castigliano's second
theorem.
Castigliano's first theorem
" In any structure the material of which is linearly or nonlinearly elastic
and in which the temperature is constant and the supports are unyeilding,
the first partial derivative of the strain energy with respect to any
particular deflection component is equal to the force applied at the point
and in the direction corresponding to that deflection component"
n
Wi = pn (6)
Castigliano's theorems are used principally in the analysis of statically
indeterminate structures, although it is sometimes used to solve deflection
problems.
Chapter (1) - Deflections 91
Example (36)
Compute the deflection of point b at
cantilever beam shown in Fig.58
Solution
Wi = L
O
2
EI2
dx M
Figure (58)
p
w i
= b =
L
OEI
M.
p
M
dx
M = -Px
p
M
= -x
Therefore
b = L
O
P x (-X ) EI
dx =
L
O
3
EI3
Px
hence
b = EI3
PL3
Example (37)
Compute the slope at A for the given structure (Fig .59).
Figure (59)
Solution
Suppose M1 was applied at a, considering this as part of load system
92 Chapter (1) - Deflections
Wi = EI2
M2
dx
a
i
M
w
= a = EI
M
aM
M
. dx
From a to b
M = Ma + ( 7 - 20
Ma ) x
aM
M
= 1-
20
x
From d to c
M = ( 13 + 20
aM)x – 10 (x-4)
aM
M
=
20
x
From c to b
M = ( 13 + 20
aM)x- 10(x - 4)
aM
M
=
20
X
Then, (and put Ma = 0 since is imaginary load)
Ela
i
M
w
= EI a =
10
O
7 x( 1- 20
x) d x +
4
O
1320
xdx
+ 10
4
( 3x+ 40 ) 20
xdx
= (21
7 3x
60
x7 3
)0
10 +(
60
x13 3
)0
4 + (
60
x3 3
+x2)
0
10
a =EI
378 radians
Chapter (1) - Deflections 93
11.MAXWELL'S LAW OF RECIPROCAL
DEFLECTIONS; BETTI' S LAW:
Maxwell's law is special case of the more general Betti's law. Both laws
are applicable to any type of structures, whether beam , truss, or frame, to
simplify this discussion, however, these ideas will be developed by
considering the simple truss shown in Fig.60. Suppose that the truss is
subjected to separate and independent systems of forces, the system of
forces Pm and Pn. The Pm system develops the normal forces Nm in the
various members of the truss, while the Pn system develops Nn. Let us
imagine two situations. First, suppose that the Pm system is at rest on the
truss and that we then further deform the truss by applying the Pn system.
As a second situation, suppose that
just the reverse is true, i.e. that the
Pn system is acting on the truss and
that then we further deform the truss
by applying the Pm system. In both
situations, we may apply the law of
virtual work and thereby come to a
very useful conclusion known as
Bettis law.
Pm mn = Nm . L
where
Pm1 m2P
m3P
n2P
n1P
n3P
Fig. 59
Figure (60)
mn is the deflection of point of application of one of the forces Pm (in
direction and sense of this force) caused by application of Pn force
system.
L = EA
L . Nn
then:
Pm mn = Nm Nn EA
L
In the second situation, however the Pn forces will now be in the role of
the virtual Q forces, the deformation caused by Pm
94 Chapter (1) - Deflections
Pn .nm = Nn . L
Where nm is the deflection of point of application of one of the force Pn
caused by application of Pm forces.
L = Nm . L/EA
then:
Pn .mn = Nn Nm EA
L
Hence
Pm mn = Pn .mn
Which when stated in words is called Bett's law.
BETTI'S LAW
"In any structure, the material of which is elastic and obey hook's law
and in which the supports are unyielding and the temperature constant,
the external virtual work done by a system of forces Pm during the
deformation caused by a system of forces Pn is equal to the external
virtual work done by the Pn system during the deformation caused by the
Pm system"
11. MAXWELL'S LAW
This suggests that Maxwell's
law of reciprocal deflection can
be derived directly from Betti's
law consider a beam as shown
in Fig.61, hence
P .12 = P .21
12 = 21
2a = a2
figure (61)
Chapter (1) - Deflections 95
Maxwell's law of reciprocal deflections:
"In any structure as shown in fig. 62 the material of which is elastic and
follows Hooke's law in which the supports are unyielding and the
temperature constant, the deflection of point 1 in the direction ab due to
P at ponint 2 acting in a direction cd is numerically equal to the
deflection of point 2 in the direction cd due to a load P at point 1 acting
in direction ab"
12 = 21
Figure (62)
12. INFLUENCE LINE FOR DEFLECTION:
Suppose that we wish to draw the influence line for the vertical deflection
at point a on the given beam Fig.63. The ordinates of such an influence
line can be computed and plotted by placing a unit vertical load
successively at various points along the beam and in each case computing
the resulting vertical deflection of point A. In this manner, when the unit
load is placed at any point m, it produce a deflection am at point a, or
when placed at some other point n, it produces a deflection an at point a.
Note however, the advantage of applying Maxwell's law to this problem.
96 Chapter (1) - Deflections
Figure (62)
If we simply placed unit load at a the deflection ma and na at points m
and n will be equal to am and an, respectively. In other words,
"The elastic curve of the beam when unit load is placed at point (a) is the
influence line for the vertical deflection at point a".
To obtain the influence line for the deflection of a certain point, simply,
place a unit load at that point and compute the resulting elastic curve.
Chapter (1) - Deflections 97
PROBLEMS
(1) By using the double integration method, Moment – area Method, and
elastic load Method Determine:
a- deflection at points C, d
b- Slope at pint a, b, d
c- Maximum deflection for cases 3 and 5
d- Draw elastic line
E = 2100 t/cm2
I = 70000 cm4
(2) Determine by using conjugate beam method for the following
beams;
a- Slopes at points a, b
b- Deflections at points c, d, e, f
c- Relative slopes at intermediate hinges
d- Sketch the elastic line for the given beams.
98 Chapter (1) - Deflections
(1)
(2)
(3)
(3) a- A horizontal paneled floor beam composed of three simply
supported main girders and across girder as shown. Draw
B.M.Ds for all beams due to concentrated load P at the center of
the floor,
EI = constant for all beams.
(3) b- Determine the slope at A and deflection at A , B for the shown
cantilever
Chapter (1) - Deflections 99
(3) c- For the given beam, if the deflection at the spring support = 0.5
cm, EI = 2000 m2t, Draw S.F.D. & B.M.D. and find the stiffness
of spring k
(4) By using virtual work method, Determine;
a- Horizontal displaement at support A.
b- Vertical deflection at c, D.
EA = 45000 t
EI = 30000 m2.t
100 Chapter (1) - Deflections
EI = 18000 t.m
2 EI = 15000 t.m
2
(5) For the given frame, determine
a- Relative rotation,
horizontal displacement,
vertical displacement at
the intermediate hinge (at
c)
b- Relative displacement db.
c- Rotation at a
El = 10000 m2t.
(6) For the shown frame, calculate
a- Relative vertical deflection between b, b-
b- Relative rotation
between b, b-
c- Relative horizontal
displacement bet. c,
Chapter (1) - Deflections 101
c-
El = 20000 m2t.
(7) For the following trusses it is required to determine
a- Vertical deflection at c, d, e
b- Horizontal displacement at h
c- Relative displacement gf in truss (a)
(EA = 30000 t, EI = 25000 m2t.)
(8) a- For the given frame, it is required:-
1- Horizontal displacement at B
2- Rotation at A
3- Relative displacement between c, A due to
a- Uniform rise of temperature 20
b- Non-uniform rise of temperature from – 20 to + 20 for the
inner and outer sides respectively
= 1 10-5
, h = 1.0 m , EI = 12000 t.m2
102 Chapter (1) - Deflections
B
C
A
(9) Draw B.M.D., S.F. D. for beam C D if the deflection at k = 0.8 cm
EI = 3000 m2t.
Chapter (1) - Deflections 103
(10) For the shown structure, determine the vertical deflection at G and
the horizontal movement at roller B
El = 2 104 m
2t.
5t 5t
5t 5t 5t
10t
B
A
(11) Using the method of virtual work, compute the vertical component
of the deflection of joint d due to the given load, for the shown
trusses also horizontal component at roller support
E = 2100 t/ cm2 , A = 50 cm
2
a)
b
10t
d
e
c
a
104 Chapter (1) - Deflections
b)
c) e
cb
d
12t
d)
fa
5t
c
b e
d
e)
A
20t
5t
e
c d
b
Chapter (1) - Deflections 105
f)
a b2 t /m
2EI = 3000 t.m
g)
ba
b
b
3t
3t
3t
3th
(12) Draw the influence lines for the displacement at the roller support
and the relative rotation at the intermediate hinge
EI = 20000 t.m2
A B
D
B
A
C P
(13) Draw the influence lines for the relative displacement between c and d cd. For
the given trussed beams braced by a system of link members as shown in the
following figures.
EI = 30000 t.m2
106 Chapter (1) - Deflections
a) ba
b)
2 BUCKLING
1. INTRODUCTION
A vertical member whose cross section dimensions are small as compared
to its height and subjected to compressive force is known as a column.
Horizontal or inclined members subjected to compressive force are
known as struts
Along column when subjected to direct load, deflects in lateral direction
which is known as buckling. The effect of lateral deflection is quite
considerable in long columns. In contrast to long columns the effect of
lateral deflections is negligible in short columns. In very long columns
the effect of direct stresses is small as compared with bending stresses.
The main causes of bending in the columns are lack of straightness in
member, i.e. initial curvature in the member, eccentricity of the load and
non –homogeneity in the material of construction of the column. Every
column will have at least small degree of eccentricity.
From mechanics, it is known that a body may be in three types of
equilibrium; stable, neutral, and unstable. A stable equilibrium is one in
which body returns to its original position on being displaced from its
position of equilibrium e.g. a ball resting on a concave surface as shown
in Fig.1.a. A neutral equilibrium is one in which a body does not return
to original position on being displaced but its motion stops e. g a ball on a
horizontal plane as shown in Fig.1.b. In unstable equilibrium the body
continues to move further away from its position of equilibrium on being
displaced e.g. a ball on convex surface as shown Fig.1.c.
A long column subjected to small loads is in a state of stable equilibrium.
If it is displaced slightly by lateral forces, it returns to its original position
on the removal of the force. When the axial load (P) on column reaches
certain critical value ( crP ), the column will be in a state of neutral
equilibrium. When it is displaced slightly from its straight position, it
108 Chapter (2) - Buckling
remains in deflected position, Fig.1.b. If the force (P) exceeds the critical
load ( crP ), the column becomes in unstable equilibrium (Fig.1.c). The
column either collapses or undergoes large deflection (Fig.1.c). The
critical load of column is defined as the load at which column is in neutral
equilibrium.
a) Stable b) Neutral c) Unstable
Figure (1)
2. SLENDERNESS RATIO
In the long column as shown in Fig.2, the effect of bending is to be
considered while designing. The resistance of any member to bending is
governed by its flexural rigidity (EI), where;
2.iAI
Where i is the radius of gyration and A is the
cross sectional area. Every structural member
will have two principal moments of inertia
one is maximum and the other is minimum.
Resistance to bending is determined by least
moment of inertia minI ( Iy ).
2minmin .iAI
Where minI is the least radius of gyration
A
Ii min2min
Figure (2)
Chapter (2) - Buckling 109
The ratio
mini
L=
gyrationofradiusleast
memberoflength=
is known as the slenderness ration of the member. Whether a column is
short or long is according to the numerical value of the of the slenderness
ratio.
3. END CONDITIONS
The various end conditions encountered in columns are; fixed, hinged,
roller or free as shown in Fig.3. Thus considering end conditions, we
have the following categories of columns:-
1. One end free and other fixed
2. Both ends are hinged
3. Both ends are fixed
4. One end is fixed and the other end is hinged
5. One end roller and the other end fixed
6. Both ends are elastically
Figure (3)
110 Chapter (2) - Buckling
4. EULER'S FORMULA
Euler found out the failure load for various end conditions,
considering stability of columns on assumptions that column is initially
straight, homogeneous of uniform cross section throughout, axially
loaded, the material is linearly elastic and lateral deflections of the
column remain small in relation to its length.
Figure (4)
Consider a strut (or beam) as shown in Fig.4 carrying an axial
compressive load P. Hence the buckling will occur in the plane of the
least rigidity, the critical load (Pcr) can be calculated by using the
differential equation of elastic curve as follows:-
min2
2
EI
M
dx
yd
The bending moment (M) at any distance x from the left hand end is ;
M = yp.
Hence;
yEI min = yp.
yEI
py .
min
=0
The solution of this differential equation is:-
CxCCxCy cossin 21
Where:
Chapter (2) - Buckling 111
minEI
PC
C1 and C2 are integration constants and can be determined from the
boundary conditions as follows:-
(1) At x = 0 → y= 0
(2) At x = L → y=0
From first condition C2 = 0 and CxCy sin1 , from second condition:
CLC sin0 1
If C1=0, this case of no buckling , then the strut remains straight . If
sin(CL)=0, hence
CL = n (n=0, 1, 2, …… etc.)
If n=0 → then; no buckling
If n=1 → then ; c=L
i.e. P = 2 .2
min
L
EI …..(1)
And y = 1C .sinL
x …..(2)
The deflection form is a half sine curve of undefined magnitude.
The value of P given by Equation (1) is the smallest value for which this
non–straight equilibrium form can exist. If P is smaller than this value,
then the strut can be in equilibrium in the straight form only (C1=0). The
value P given by Equation (1) is therefore a very special value in that it
marks the boundary between the straight equilibrium state and the non–
straight given in Equation (2) and it is termed the critical load (Pcr) or
buckling load. this case was first solved by the Swiss mathematician
Euler, and is therefore frequently termed the Euler load.
2
2 .
L
EIPcr
…..(3)
Pcr is the lowest critical load for hinged ended strut (Euler strut) by taking
n=1. If n is taken equal to 2 , 3, 4 etc . , series of critical load is obtained
112 Chapter (2) - Buckling
EIL2
24, EI
L2
29, EI
L2
216, . . . .etc.), each corresponding to a more
complex equilibrium form as shown in Fig.5.
(a) 2
2
L
EIPcr
(b)
2
24
L
EIPcr
(c)
2
29
L
EIPcr
Figure (5)
The behavior of the strut can be compared to that of the sphere shown in
Fig.1. In Fig.5.a, a sphere is shown resting on a concave surface; it is in a
state of stable equilibrium. If displaced from its initial "at rest" position in
the center of the surface, it will return to that position. This is similar to
the column carrying an axial load less than the Euler load (Pcr). Fig.1.c is
in state of unstable equilibrium, and is similar to that of the column
loaded beyond the Euler load. Fig.1.b shows a state intermediate between
the stable and unstable. Fig.6 shows a graph of axial load P against
central lateral deflection.
crP 2min
2
L
EIPcr
Figure (6)
Chapter (2) - Buckling 113
5. COLUMN WITH ONE END FIXED AND THE OTHER
FREE
As shown in Fig.7, bending Moment at
distance x
M = )y - ( P -
yEI = M
yEI = )( yP
yEI = )( yP
yPyEI . = P
Putting
2c
EI
P
Figure (7)
22 cycy
The solution of this differential equation is
)sin()cos( 21 cxCcxCy
Taking x from the fixed end,
At x = 0 → y = 0
i.e. 0 = C1 + 0 +
C1 = -
y = )cos(..)sin(.. 21 cxcCcxcC
At x = 0 → y = 0
0.2 cC → 02 C
Hence )cos(cxy
))cos(1( cxy
At x = L → y =
))cos(1( cL
0)cos( cL
114 Chapter (2) - Buckling
cL = .,.........2
3,
2
Taking least value of cL
cL = 2
crP = min2
2
4EI
L
crP = min2
2
)(EI
Lb
i .e. LLb 2
Similarly as shown in Fig.8, in general Euler critical load crP equal to
crP = 2
min2
)( bL
EI ….(4)
Where bL is the buckling length according to end conditions Fig.3 and
Fig.7 and minI is the minimum moment of inertia
2
min2
04.2L
EIPcr
2
min2
4L
EIPcr
2
min2
L
EIPcr
Figure (8)
6. CRITICAL STRESSES
The proceeding analysis have given values of critical load ( crP ) for
various types of column, but the designer usually works with stresses. In
the fundamental case of the hinged column, the critical stress is given by,
A
Pcrcr ….(5)
Chapter (2) - Buckling 115
Where A is the cross section area of column in case of short column, the
failure occur when the stress reaches the ultimate value of column
material )( u and.
A
Puu (6)
In case of slender column if P < crP , the column in state of equilibrium ,
and if P = crP ,the column in state of neutral equilibrium and the buckling
has occured if P > crP , the column become unstable hence;
IL
iEI
b
cr2
22 .
2
min
2
)(i
L
E
b
cr
2
2
Ecr ….(7)
The critical stress in a column is therefore dependent only on the young's
modulus of column material, and the slenderness ratio i
L of the column .
7. LIMITATION OF EULER'S FORMMULA
In the Euler formula it was assumed that the member absolutely straight
and the load is axial. The critical load was derived from the differential
equation of the elastic curve which is based on Hook's law. Hook's law is
valid as long as stresses do not exceed proportional limit. The critical
stress cr was found by;
2
min
2
)(i
L
E
bcr
p (8)
Where p is the proportional limit of the material of the column. For
Euler's formula to be valid; i.e;
p
b E
i
L
min
116 Chapter (2) - Buckling
According to Egyptian Code of Practice for steel, 1989, and to avoid
inelastic buckling, then assume; P=0.8y, where y is the yield stress.
For steel, the modulus of elasticity E=2100 t/cm 2 , hence;
104i
Lb for steel 37 (y=2400 kg/cm2, P=1920 kg/cm
2)
96i
Lb for steel 44 (y=2800 kg/cm2, P=2240 kg/cm
2)
85i
Lb for steel 52 (y=3600 kg/cm2, P=2880 kg/cm
2)
Euler's formula is valid for steel 37 if pcr and 104/ iLb . Fig.9
shows the relation between cr and min/ iLb and the curve is asymptotic
to both axes. As the ratio iLb / increase the column will buckle at a lower
value of cr . In the other hand the value of cr tend to infinity as the ratio
iLb / become very small, and the column actually become a short one
and the failure is governed by the ultimate strength of column material
u which is represented in Fig.9 by horizontal line c-e. Euler's formula is
valid only for part a-b ( 104/ iLb ). If 104/ iLb , (for steel 37),
empirical formulae, which represent the experimental results used to
calculate the buckling stress, according to part b-c, this part may be
parabolic or straight line. Hence from the above discussion, the buckling
stress is therefore represented by the curve a-b-c as shown in Fig.9.
i
Lb
cr
p
pb
pc
u
Figure (9)
Chapter (2) - Buckling 117
8. FACTOR OF SAFETY
In the design of columns a factor of safety (n) is used, and the permissible
or working buckling stress ( )pb is represented by curve e-f-g as shown
in Fig.9; where:
n
crpb
(9)
where n is the factor of safety.
9. EMPIRICAL FORMULAE
a) For steel 37
The ultimate strength u =3.7 t/cm 2 ; and the yield stress
is y =2.4 t/cm 2 ; and the modulus of elasticity E = 2100 t/cm 2 . The
permissible or working stresses in tension and compression are;
2/2.1 cmtpt
2/1.1 cmtpc (no buckling )
The permissible buckling stress pb value for steel 37 as follows;
For 104i
Lb 2
2
/
)(
6000cmt
i
Lbpb
For 104i
Lb
Empirical formula is: 22 /)(00005.0 cmti
Lbpcpb
i.e. 22 /)(00005.01.1 cmti
Lbpb
a) For steel 44 (PC=1.30 t/cm2)
For 96i
Lb
Use Euler's formula 2
2
/
)(
6000cmt
i
Lbpb
118 Chapter (2) - Buckling
For 96i
Lb
The parabolic formula is: 22 /)(00007.030.1 cmti
Lbpb
a) For steel 52 (PC=1.40 t/cm2)
For 85i
Lb
use Euler's formula 2
2
/
)(
7500cmt
i
Lbpb
For 85i
Lb
The parabolic formula is: 22 /)(000065.04.1 cmti
Lbpb
Example (1)
For the shown steel column (steel 37) in Fig.10 determine the
permissible buckling load pbP for two end conditions;
a) Cantilever
b ) Hinged-fixed
E=2100 t/cm 2 , A=77.8 cm 2 , 412510 cmI x
4782 cmI y , cmix 7.12 , cmiy 67.2
c) Calculate the factor of safety for two cases Solution
a) case of cantilever
bL = 2502 = 500 cm
mini
Lb = 67.2
500 = 26.187 >104
use Euler formula
pb = 2)26.187(
6000 = 0.171 2/ cmt
The permissible buckling load is:
pbpbp
= 0.171 8.77
= 13.31 ton
Figure (10.a)
Chapter (2) - Buckling 119
b) in case of hinged-fixed column
Lb = 0.70 250 = 175 cm
mini
lb =
67.2
175 =65.54 <104
Use parabolic formula:
2
min
)(00005.010.1i
lbpb
Figure (10.b)
= 1.10 2)54.65(00005.0
= 1.10 2/8852.02148.0 cmt
The permissible buckling load is:
pbpbP
=0.8852 8.77
=68.86 ton
c)Factor of safety (n) for (case a)
n = pb
cr
or n=pb
cr
P
P
= 171.0
)//( 2min
2 iLE b
= 171.0
)26.187/()2100( 22
= 3.45
Factor of safety for (case b)
n = 8852.0
)54.65/()2100( 22
= 5.445
pb
pc
i
Lb
120 Chapter (2) - Buckling
10. MAXIMUM FIBER STRESS
The value of permissible buckling stress represents the average stress in
column cross section area where:
pb = av = A
Ppb
On the other hand, the value of maximum compressive stress not exceed
the value of permissible compressive stress of material ( )pc as shown
in Fig.11. Hence ;
max = kav . pc
i.e.
pc = kpb .
Where k is buckling coefficient and
depend on slenderness ratio. Hence
pb
pc
i
Lb
pb
Figure (11)
K =pb
pc
(10)
In case of column subjected to compression force P which is less
than pbP , hence the maximum stress in case of buckling is equal to :
kA
p.max (11)
In case of eccentrically loaded columns subjected to axial load and
bending moment, the maximum stress is equal to;
max = maxmax xI
My
I
Mk
A
P
y
y
x
x pb (12)
Chapter (2) - Buckling 121
Example (2)
Fig.12 shows steel column (steel44) subject to eccentric load b and
horizontal load 1.0t. the cross section is B.F.I no 40 with;
A=209 cm 2
60640xI cm4 , 0.17xi cm
11710yI cm4, 49.7yi cm
Determine the maximum value of P if 2/3.1 cmtpc
Figure (12)
Solution :
Buckling length = cm8004002
2
22min
min
52908106
60006000
10480106497
800
497
t/cm.).()(lb/i
σ
..
/iL
.iI
pb
yb
y
Also M )4(1004001100 PPx t.cm
The maximum value of P depend on maximum stress then :
maxmax .. yI
M
A
P
xpb
pc
3.1
122 Chapter (2) - Buckling
=60640
20100)4(
5259.0
3.1
209
pp 3.1
i.e. P(0.0118+0.033)-0.13 3.1
0448.0
43.1P 92.31 t
P 92.31 t
hence the maximum allowable value of P 92.31max t
Example (3)
For the given steel column (steel 52)
Fig.13 find the allowable buckling load if:
a) Both ends are hinged with height 10m
b) One end is hinged and the other end
fixed.
c) Both ends are hinged but the column is
laterally supported in plane x-x at middle
height as shown in Fig.13, calculate the
factor of safety for each case.
2)//(7500 ilbpb for 85i
lb
2)2
(000065.04.1 bwb
l for 85
i
lb
Column section B.F.I No 300
A=154cm2, 425760cmI x , 49010cmI y
E=2100 t/cm 2
Figure (13)
Solution
a) Both ends are hinged: (lb=10m)
cr =2
min2
bL
EI
=2
2
)1000(
)9010)(2100( =186.74 t
cr =A
Pcr = 154
74.186 =1.21 t/cm
2
Chapter (2) - Buckling 123
2
2
min
/437.0)89.130(
7500
10489.13064.7
1000
64.7154
9010
93.12154
25760
cmt
i
l
cmA
Ii
cmA
Ii
pb
b
y
y
xx
Safe or permissible Load ( AP pbpb )
154437.0 =67.268 t
factor of safety = b
cr
=
b
cr
= 437.0
21.1 = 76.2
b) hinged- fixed column
lb = 0.7L
= 700 cm
cr = 2
2
)700(
90102100)14.3( =381.10 t
cr =A
Pcr =154
1.381
= 2.47 t/cm2
mini
lb = 64.7
700 =
= 8562.91
pb =2)62.91(
7500
= 0.893 t/cm2
safe load = b
b = 154893.0 =117.50 t
124 Chapter (2) - Buckling
factor of safety =pb
cr
pb
cr
= 89.2516.131
1.381
b) hinged – hinged column with laterally
support at middle height
lb about x-x =1000cm
lb about y-y = 10005.0
= 500cm
t.)(
)(πp
t.)(
))((πP
..i
l
..i
l
cm.A
Ii
.A
Ii
cr
cr
y
yyb
x
xxb
y
y
xx
97746500
90102100
95331000
254602100
1044465647
500
10433779312
1000
647
9312
2
2
2
2
Hence
2/46.3,9.533 cmtA
t crcrcr
22 /011.1)33.77(000065.040.1 cmtpb
Permissible safe load tpb 694.155154011.1
factor of safety =pb
cr
=
694.155
97.746 =3.42
Chapter (2) - Buckling 125
Example (4) For the shown steel column (steel 37),
calculate;
1. Max compressive stress in the column
due to given load
2. The max value of P which can be
safety carried by the column
section properties ; (B.F.I 28)
A =144 cm2
Ix = 20720 cm4
Iy =7320 cm4 ix = 12cm
Iy = 7.14 cm
Solution
buckling length (lb) =600 cm
least radius of gyration iy = 7.14 cm
greatest slenderness ratio is:
= 14.7
600 = 84.03 < 104
tmL
M
K
cmt
b
c
pb
.5.74
65
4
473.1747.0
10.1
/747.0)03.84(00005.010.1 22
Max compressive stress
maxmax yI
Mk
A
P
x
x 1.10
Figure (14)
1420720
)100(5.7473.1
144
0.30max =0.3068 + 0.5067
= 0.8135 t /cm2 < 1.10 (ok)
To get Pmax , 5067.0)473.1(144
1.1 max P
Hence ; Pmax = 58.655 t
126 Chapter (2) - Buckling
Example (5)
For the shown column (Fig.15) and
link members, determine the
maximum stress in the column and
marked truss member due to
buckling
2
2
/20.1
/10.1
cmt
cmt
t
c
B.F.I No 32 42 32250,171 cmIcm x
49910 cmI y
Figure (15)
Ch .No 10 25.13 cm 4206 cmI x 43.29 cmI y
cme 55.1
cmb 5
Solution
Column ABC
bl =2L =1600 cm
xI = )1723612
236(232250 2
3
=73914 cm4
12
3629910
2yI = 17686 cm
4
Chapter (2) - Buckling 127
)236(2171 = 315 cm
2
315
17686min I =7.49 cm
mini
lb = 49.7
1600 =213.5 >104
pb =25.213
6000 =0.1316 t/cm
2
N = - 20 t Mx=40 m.t for part AB
max = yI
M
A
P
x
x
pb
pc..
(comp)
= 1873914
2000
1316.0
10.1.
315
10 = - (0.2653 + 0.4870 )
= - 0.7523 t/cm2 <1.10 o.k
Member B-d, ch. No. 10
A =213.5 =27 cm2
bl =L = 10022 =282.84 cm
xI =2(206) =412 cm4
yI =2(13.51.552 +29.3) =123.47 cm4
mini =27
47.123 =2.138 cm
mini
lb =138.2
84.282 =132.26 >104
pb =226.132
6000 =0.343 t/cm
2
max =pb
pc
A
N
=
343.
1.1
27
210 =-1.679 t/cm
2 >1.10 Unsafe
The cross section dimensions must be increased
The other member c-d is tension and the buckling does not occur, hence
t =27
10 =+0.37 t/cm
2 <1.2 Safe
The other members d-e and e-b are zero force and stresses
128 Chapter (2) - Buckling
Example (6)
Figure (16) shows a
frame has the given cross
section for link member AC;
find:-
1) the max value of P
2) the max value of stress for
the
given section
3) the value of safe load P
4) factor of safety.
Figure (16)
pc =1.1 t/cm2, E =2000 t/cm
2
xI =4670 cm4, yI =139000 cm
4
A =254 cm2 ,
xi =4.287 cm
yi =23.39 cm
Solution
lb = 600 cm
1- Value of P/2 = 0.306 254 =77.80 t
i.e. P =155.60 t
2- Max. stress max = pb
pc
A
P
.
2/
i.e. max =306.
1.1.
254
8.77 =1.10 t/cm
2 Just Safe
3- factor of safety =pb
cr
=
306.0
)/( 22 ilE b =
306.0
06.1 =3.45
b pb
b
p
cm t
cm i
lb
2
/ 306 . 0 ) 95 . 139 (
6000
104 95 . 139 287 . 4
600
2 2
min
Chapter (2) - Buckling 129
Example (7)
For the shown column in Fig.17 determine Pcr. The cross section is an
angle 130x130x12cm
xI = yI =472 cm4
A =30.0 cm2, e =3.64 cm
E =2100 t/cm2, pc =1.1 t/cm
2
Calculate the factor of safety and max stress
Figure (17)
Solution
Get Ixy = 312 cm4
Lb = L = 600 cm
minI = vI =22)
2(
2xy
yxyxI
IIII
minI =472–312 =160 cm4
30
160min i =2.3 cm , 104
3.2
600
min
i
lB
crP =2
min2
)( bl
EI
= 2
2
)600(
)160)(2100( =9.20 t
130 Chapter (2) - Buckling
mini
lb = 30.2
600 =259.8 >104
pb =2
min
)(
6000
i
lb
=0.0889 t/cm2
Safe load (Ppb)
tpbpb 67.2)30(0889.0
Factor of safety (n)
N = pb
cr
P
P =3.45
Maximum Stress
45.330
67.2max =0.30 t/cm
2 < 1.10 (o.k)
Example (8)
For the shown column (steel 44) in Fig.8, a rise
in temp. accrued by a value t find the
maximum value of t which make a column still
stable. Cross section is SIBNo.30:-
A =64.1 cm2
yI =451 cm4
E =2000 t/cm2
=1.2 10-5
Solution
mini =A
I y = 2.55 cm
Lb = 0.51000 = 500 cm ,
104
3.2
600
mini
lB
Compressive stress occur due to rise of temp t
is:
Figure (18)
Chapter (2) - Buckling 131
E =
E
tt
L
LtE
L
LE
0252.0102.12100
...
.
5
Axial force = .
= 69.1 (0.0252t)
= 1.741 t
The column is stable if the axial force crP = 2
min2
)( bl
EI
Pcr = 2
2
500
4512000 =35.57 t
Hence 35.57 1.741 t, i.e. t ≤ 20.40C
11. COLUMN WITH INITIAL CURVATURE
Let ABC be the shape of the column before
loading with central deflection e as shown in
Fig.19 and let AC B be the shape after loading
with total central deflection y0. At a point
distance x from top hinge, let y1 be the
deflection before loading and y be the total
deflection after loading. As the curvature is very
small, the curve may be assumed to be sin curve
such that
1y =L
xe
sin
It will be assumed that bending is uniplanar,
M = P . y
Figure.19
132 Chapter (2) - Buckling
2
12 )(
dx
yydEI
=-M = -P.y
2
2
dx
ydEI =-P.y +
2
12
dx
ydEI
L
xey
sin1
dx
dy1 =L
x
L
e cos
2
12
dx
yd =
L
x
Le
sin
2
2
2
2
dx
ydEI =-P.y =
L
x
LeEI
sin
2
2
yEI
P
dx
yd
2
2
=L
x
Le
sin
2
2
Solution of this differential equation is
2
2
2
2
2
21
sin
sincos
cL
L
x
Lecxccxcy
= 1/
/sinsincos
22221
Lc
Lxecxccxc
From boundary conditions :-
(1) at x = o y = o
i.e c1 = o
then y = c2 sin cx- 1/
/sin222
Lc
Lxe
1
cos
cos
2
222
Lc
L
x
Le
cxccdx
dy
Chapter (2) - Buckling 133
(2) At x = 2
L, 0
dx
dy
i.e. 0 = 2
cos.12
CLCC
Then C2 = 0, Put EI
PC 2
y =
2
22
1
sin
Lc
L
xe
=
2
2
1
sin
EI
PL
L
xe
but Pcr = 2
2
L
EI
i.e. y =
crP
PL
xe
1
sin
(3) At x = L/2, y = y0
i.e. y0 = PP
ePP
cr
cr
..
Maximum B.M. = P .y0
=PP
ePP
cr
cr
.. =
PP
ePP
cr
cr
..
Maximum compressive stress = Z
M
A
P
= ))(
..1(
2iPP
yeP
A
P
cr
ccr
Where Z =cy
I =
cy
Ai2
134 Chapter (2) - Buckling
Example (9) The shown column (steel 37) in
Fig.20;has initial curvature e =10 cm.
find the safe value of P if the cross
section Is B.F.I No 38
E=2100 t/cm2
A=194 cm2
xI =50950 cm4
yI =10810 cm4
xi =16.2 cm
yi =7.46 cm
Find also the factor of safety
Solution
mini
lb =46.7
800
=107.23 >104
Figure (20)
cr =2
min2
bL
EI =
2
2
)800(
)10810)(2100( =349.72 t
y0 = ePP
P
cr
cr .
y0 = )10(72.349
72.349
P
i.e. M =P.y0
max = ))(
..1(
miniPP
yeP
A
P
cr
ccr
< 1.10 t/cm
2
i.e. 1.1 = )46.7)72.349(
)15)(10(72.3491(
194 P
P
1.1 ≥ P
PP
72.349
25.36
194
If we assume P =10 t ( trial and error )
Chapter (2) - Buckling 135
i.e. 1.1 = 0.0500+ 1.06 (o.k) i.e. P ≤ 10 t
The safe value offload: P ton10
12. LATERALLY LOADED COLUMN (beam – column ) Column with a concentrated load at mid height is considered. Let F
be the concentrated load applied
Figure.21
M = yPxF
.2
.
2
12
dx
ydEI =-M
= yPxF
.2
.
yEI
P
dx
yd
2
2
=2
.x
EI
F
Where:
C2 =
EI
P
ycdx
yd 2
2
2
= xEI
F.
2
)( 22 cD = xEI
F.
2
136 Chapter (2) - Buckling
The solution of this equation from mathematics is:-
y = ..sincos 21 IPcxCcxC
Where P.I . is the particular integral .
P.I. = )2
(1
22x
EI
F
cD
= ).2
(2
xcEI
F
Then:-
y = xcEI
FcxCcxC
221.2
sincos
At x = 0 ; y = 0 i.e. C1=0
dx
dy =
22.2
cos.cEI
FcxCc
At x =2
L ;
dx
dy = 0
i.e. C2 =
2cos.2 3 cL
cEI
F
then; y =P
Fxcx
cLcEI
F
2sin
2cos.2
1
3
Where
EI
P = c
2
At x =2
L ; y = y0
i.e. y0 =P
FLcL
cP
F
42tan
2
Max. B.M is:-
= 04
PyFL
Chapter (2) - Buckling 137
=2
tan2
cL
c
F
Max. stress max
=Z
M
A
P
=2..2
)2
tan(..
1(icP
cLyF
A
P c
Example (10)
Determine the maximum uniformly distributed lateral load which can be
carried by a given cross section as shown in Fig.22
y =140 kg / cm2 , E = 100000 kg / cm
2 (Wood)
Figure(22)
Solution
M =2
.
2
...
2xwxLwyP
yEI =2
.
2
...
2xwxLwyP
From mathematics;
y = )2
.(2
sincos2
221
cxLx
P
wcxCcxC
where C2 = P/EI
138 Chapter (2) - Buckling
Form boundary conditions
1C =2.cP
w
2C =2
tan. 2
cL
cP
w
0y =P
wLcL
cP
w
8)1
2(sec
.
2
2
Max. B.M.:-
= P . 0y +8
2wL
= )12
(sec2
cL
c
w
2
cL =
2.3
3 rad. =31
o
2
seccL
=1.165
Max. B. M = 22.5 w m.t
Max. stress =I
My
A
P max
= w31608.0
80.05.22
08.016.0
200
w < 0.525 t/m
Chapter (2) - Buckling 139
PROBLEMS
1. A steel column (steel 37) 6 m height, has an B.F.I –section with
properties:
A = 110 cm 42 11700, cmIx
I y = 4200 cm 24 /2100, cmtE
Determined the permissible value of the axial Load P for this column,
in the following cases
a- both ends hinged
b- one end hinged and the other fixed
c- both ends hinged but the column is laterally supported in
the X – plane at middle height. Find the factor of safety
for each case.
2. The steel column (steel 44) AB is hinged at A&B and carries an axial
load P and a lateral load H = 2 t as shown the cross–section
B.F.I.No.16 with properties
A = 58.6 cm2, 42634cmI x ,
4958cmI y
Determine the permissible value of load P
2/2100,30.1 cmtEpc
Find the factor of safety
140 Chapter (2) - Buckling
3. In the shown structure; if the column AC is restricted in direction x –
x at c, Calculate:
a) the max value of uniform load w if the column properties :
B.F.I.No.36, A = 190 cm 2
Ix = 45000 cm4, 10800yI cm
4
E = 2000 t/cm 22 /4.1, cmtc (steel 52)
4. Find the max. stresses in the column given
A = 77.8 cm2, 12510Ix cm
4 , 555Iy cm
4
E =2100 t/cm2
5. For the shown column truss element, find the max. fiber stresses for
column and link members
)44(/2100./30.1 22 steelcmtEcmtb
Column section is B.F.I No 30 and 2PL 2 cm34 as shown and link
member section is 2 channels No. 10. Find the factors of safety.
Chapter (2) - Buckling 141
6. For the given indeterminate frame. ABCD determine the factor of
safety against buckling if;
96)(00007.030.1
96)/(
6000
2
2
i
lfor
i
l
i
lfor
ilb
bbb
bb
7. For the given column section which consist of 4 angles
100 )37(10100 steelmm latticed as shown. If the height of
column is 5.0 ms, and is fixed at base and hinged at top find the safe
load; critical load and the factor of safety.
142 Chapter (2) - Buckling
8. A Latticed column shown in Fig. has 8.0 high, with hinged ends,
find:
a) The safe load if the eccentricity in direction x, e = 5cm
b) The factor of safety
c) Maximum stress. ( 22 /1.1,/2100 cmtcmtE b )
d) Show how to increase the safe load to its double value?
9. A Shown column (steel 44) hinged at A and B and the load as given
in fig, calculate;
a) Max stress in the column.
b) Safe load.
2
44
111
,4150,11690
cmA
cmIcm y
10. For the shown fixed frame a rise of temperature occur t. find the
max. value of t which make the frame still stable.
A =53.4 , I 45740 cmx ,I4288 cmy
Chapter (2) - Buckling 143
Coefficient of thermal expansion of steel is 5102.1 2/2100 cmtE
11. For the given fixed column (steel 44) with initial curvature e= 12cm
and the cross section is S.I.B No 40
A =118 cm 42 29210, cmI x
E =2100 t/cm 42 1160 cmI y
a) Find the safe value of P.
b) Maximum fiber stress.
c) Factor of safety.
12. Determine the value of P which causes instability of the structure
shown in fig.
E = 2100 t/cm 42 270300, cmI x
24 324,15350 cmAcmI y
22 /2.1/1.1 cmtcmt tc (Steel 37)
144 Chapter (2) - Buckling
13. Determine the buckling load for member AB for the given frame
shown in fig for one channel No. 30
A=58.8 cm 42 8030, cmI x
cmI y 495 cme 70.2,4
E=2000 t/cm ,2 2/1.1 cmtc
14. For the shown truss find the value of safe load P considering
buckling effect. Section; of member is 2 angle mm14100100
with the following Properties, for one angle:
)34(/2.1
,/1.1,/2000
98.2
2.26
235
2
22
2
4
steelcmtF
cmtRPccmtE
cme
cmA
cm
pt
y
Find the factor of safety and maximum stress for all members.
Chapter (2) - Buckling 145
15. For the following statically indeterminate structures; and for the
marked member; find the critical buckling load, safe buckling load;
and value of factor of safety;
E=2100t/cm 224 /2.1/1.1,37, cmtcmtsteel ptc
(a)
(b)
(c)
(d)
146 Chapter (2) - Buckling
(e)
(f) All members are2 angles 120x120x11 mm
(g) All members are2 angles 90x90x9 mm
(h) All truss members are 2 angles 80x80x8 mm
STATICALLY
INDETERMINATE
STUCTURES 3
1. INTRODUCTION
Statically indeterminate structure means that the system cannot be
determined by means of the given equations of equilibrium and the
conditional equations. In other words, when the equilibrium conditions
are not sufficient to determine the reactions and the internal forces of a
structure, one say that this structure is statically indeterminate. A
structure can be externally, internally or externally and internally
statically indeterminate. As shown in figs.1, 2 and 3, if the equilibrium
conditions are not sufficient to determine the reactions, but when the
reactions are obtained we can determine the internal forces, then the
structure is externally statically indeterminate, if the equilibrium
conditions are sufficient to determine the reactions, but we can not
determine the internal forces, then the structure is internally statically
indeterminate. The methods of solving statically indeterminate structures
are categorized into two groups, the first includes force methods and the
second includes the displacement methods.
For plane structures, we have three equilibrium conditions as follows;
M =0, yF =0, M =0
For space structures, the conditions of equilibrium are:
xF =0, yF =0, zF =0
And
xM =0, yM =0, tM =0
The following figures (Figs.1, 2 and 3.) show statically indeterminate
structures:
148 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Frames
Beams
Trusses
Figure (1) externally statically indeterminate
Beams
Frames
Trusses
149 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Figure (2) Internally statically indeterminate
Frames
Trusses
Arched Frame
Figure (3) Externally and internally statically in terminate
2. FORCE METHODS ( flexibility Approach)
Which assume that the reactions and internal forces are the
unknowns. They are determined from deflection equations. From these
methods; consistent deformations, three moments equation, and column
analogy method. For example (Fig.4) the shown once statically
indeterminate beam, the deflection at point 1 is equal to zero, if the
support at 1 is removed, the deflection at 1 due to given load equal to 10.
If 1t is applied at point 1; the deflection is 11. Then, the compatibility
equation is
0. 11110 X
150 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Hence calculate the reaction X1 and the other reaction can be
calculated. Term 11 is called flexibility of the maim system at point 1.
10
11
Figure (4)
3. DISPLACEMENT METHODS (stiffness Approach )
In these methods, the unknowns are the deformations that are
determined from equilibrium conditions. From these methods; moment
distribution, slope deflection methods, and stiffness matrix methods. For
example, fig.5 shows statically indeterminate beam. In the stiffness
approach, deformation (rotation & translation) at joints A and B are
obtained and used to obtain the internal forces. .To determinate A at
support A, assume fixed support at A, hence;
aM = 0AM + 1AAM =0
From the above equation, calculate the value of A and then
calculate the internal forced at any section.
151 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
A
Figure (5)
4. DEGREE OF STATIC INDETERMINACY
The first step to solve any statically indeterminacy structures is
determination of the degree of indeterminacy. From the degree of
indeterminacy one knows how many redundant forces and moments
could be considered in solution by using the force methods.
4.1. Degree of Indeterminacy For Beams (Line Structures) (Degree Of
Redundancy)
If we assume
n = degree of redundancy
r = number of reactions
c = number of equations of condition
( c = 1 for a hinge, c = 1 for roller )
h = degree of indeterminacy
if r < c + 3 → the beam is unstable
if r = c + 3 → the beam is statically determinacy
if r > c + 3 → the beam is statically indeterminate
i.e. n = r - c - 3
152 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Figure (6)
For the above beam shown in fig. 6
r = 6
c = 1
i.e. n = 6 – 1 -3
= 2 → Twice statically indeterminate
Another example, for beam shown in fig. 7
Figure (7)
R = 6
C = 2
n = 6 – 2 - 3
= 1 → Once statically indeterminate
For beam shown in fig. 8
n = n1 + n2 = 3
Figure (8)
n1 = 4 - 2
= 2
153 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
n2 = 2 - 1
= 1
4.2. Degree of Indeterminacy for Plane Frames
If we assume the frame shown in fig. 9
r = number of reactions
b = number of members
(3 unknowns / member )
j = number of rigid joints
(3 eqn. / joint )
c = number of equations of conditions
n = degree of indeterminacy
if 3b + r < 3j + c → the frame is unstable
if 3b + r = 3j + c → the frame is statically determinate
if 3b + r > 3j + c → the frame is statically
indeterminate
hence;
n = 3b + r – 3j – c
For example the above frame shown in fig. 9
b = 6
r = 6
j = 6
c = 0
i.e.
3 6 + 6 > 3 6 + 0
Hence
n = 6
→ degree of indeterminacy
or number of redundants.
Figure (9)
154 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Example (1) For the given frames shown in figs. 10, 11, 12 and 13, determine the
degree of indeterminacy
B = 10
r = 9
j = 9
C = 0
n = 310+9
–39–0
= 12
(12t h degree)
Figure (10)
B = 10
r = 9
j = 9
C = 4
n = 8
(Eighth degree)
Figure (11)
b = 10
r = 9
j = 9
c = 1
the overhanging portion a b
should not be counted in the
number of members
n = 310+9
-39–1
= 11
(11th degree)
Figure (12)
155 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
b = 10
r = 9
j = 9
c = 3
c is the number of member
meeting at the internal hinge
minus one
c = 4 – 1
= 3
n = 30 +9
- 39–3
= 9
(ninth degree)
Figure (13)
Note:
For stable structure at least
three components of external
reactions which must not be
parallel or intersecting at a point.
The shown frame in fig.14 is
unstable because
M , at A ≠ 0.
Figure (14)
4.3 Degree of Indeterminacy of Plane Trussed
If we assume the truss shown in fig.15
b = number of members (1 unknown / member )
r = number of reactions
j = number of joints ( 2eqn. / joint )
n = number of redundant
n = b + r – 2 j
156 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
Figure (15)
Hence:
1) b + r < 2j → the truss Is unstable
2) b + r = 2j → the truss is stable and determinate
3) b + r > 2j → the truss is statically indeterminate
i.e. n = b + r – 2j
Example (2)
For the above truss (Fig.15)
B = 19
R = 3
J = 10
n = 19 + 3 – 2 10
= 2 (Twice degree of indent.)
Example (3)
For the given truss in fig.16
B = 7
R = 3
J = 5
n = 7 +3–52
= 0
(determinate and stable)
Figure (16)
157 Chapter (3) STATICALLY
INDETERMINATE
STUCTURE
See the following examples shown in table1
truss
b
r
J
n
Type
7
3
5
0
unstable *
( we must avoid three hinges on one line)
7
3
5
0
unstable **
6
4
5
0
unstable ***
8
4
5
2
Indeterminate to
2nd
degree
* Internal geometric instability due to three hinges a, b, c, on a link,
possible displacement as shown by dotted link.
4 METHOD OF CONSISTENT DEFORMATIONS
1. INTRODUCTION
Statically indeterminate structure may be analyzed by direct use
of the theory of elastic deformations. Any statically indeterminate
structure can be made statically determinate and stable by removing the
extra restraints called "Redundant Forces" or simply redundant, that is,
the force elements which are more than the minimum necessary for the
static equilibrium of the structure. The statically determinate and stable
structure that remains after removal of the extra restraints is called the
"Primary Structure". The original structure is then equivalent to the
primary structure subjected to the combined action of the original loads
plus unknown redundancy. The conditional equations for geometric
consistence of the original structure at redundant points are called the
"Compatibility equations" are then obtained from the primary structure by
superposition of the deformations caused by the original loads and
redundancies. We can have as many compatibility equations as the
number of unknown redundant so that the redundant can be determined
by solving these simultaneous equations. This method known as
"Consistent Deformations" is generally applicable to the analysis of any
types of structures, whether it is being analyzed for the effect of loads,
support settlement, temperature change, or any other case. However, there
is only one restriction on the use of this method: the principle of super
positions must hold.
Chapter (3) - Consistent Deformations 159
2. ONCE STATICALLY INDETERMINATE
STRUCTURES
Figure (1) shows once statically
indeterminate structures. The unknown
reaction components at supports are
four, while the conditions of static
equilibrium are only three. Hence one
more equation, depending on the elastic,
behavior of the structure should be
added in order to determine the
reaction components. The application of
consistent deformation method to solve
such beam or frame, may be carried out
as follows:-
a. Beam with fixed and Roller
Supports
b. Two Hinged Frame
Figure (1)
1.
Choose a main system Which is
determinate, by removal of the
redundant reaction component. For
the given beam in fig. 2 the main
system is simple beam by assuming a
hinged support at A, thus eliminating
the reaction component X1. Draw for
the main system Mo. D as shown in
fig.2.b.
Original Beam
PA B10
X1 = 0
a.main system
2.
Apply a virtual load
X1 =1 t.m at A and draw M1 .D
PA B
+
b. Mo Diagram
3.
The rotation 10 (or 10)at support A
of main system, can be calculated
from the equation:
X1 = 1 t.m
11
c. Elastic Curve
160 Chapter (3) - Consistent Deformations
10 = 10 = B
AEI
dlMM 10 .
Similarly, the rotation 11 (or 11)
due to unit load 1 t.m at A is equal
to:
11 = 11 = B
AEI
dlM .2
1
-1 t.m
d. M1 Diagram
-
+
e. B.M.D
.
Figure (2)
4. Since the rotation at fixed support A must be equal zero in the original
indeterminate beam hence (A =0) then; the compatibility equation as
follow:
10 + X1 . 11 = 0
5. The total bending moment or shearing force at any support or section of
the indeterminate beam is equal to:
M = M0 +X1 .M1
Q = Q0 +X1 .Q1
The bending moment diagram may also be obtained by the
superposition of Mo and X1.M1 diagrams.
Example (1)
For the given indeterminate beam
shown in Fig.3, Draw B.M, and
S.F.Ds.
Solution
6 t
3 3
A B
BA6 t
3 3X1 = 0
A B
9 t.m
a. Mo D.
1.
choose the main system as
shown and draw M0.D.
(Fig.3.a)
Chapter (3) - Consistent Deformations 161
2.
3.
4.
Draw M1.D as shown (Fig 3.b )
Write the compatibility
equation at A :-
10 + X1 . 11 = 0
Calculate 10 and 11
10 = EI
dlMM 10.
= EI2
5.069
= EI4
54
11 = EI2
5.061
= EI4
6
i.e.
X1 = 11
10
S
S
= 6
54 = 9 t.m
Hence
M = M0 + X1 M1
MA = 0+ -91 = -9 t.m
Mc = 9-9 0.5 = + 4.5
Hence B.M, S.F.Ds, reactions,
free body, and main steel RFT.
As shown
BA6 t
3 3X1 = 0
1 t.m
-
X1 = 1 t.m
b. M1 D.
+
-
9 t.m
4 t.m
9 t.m
c. B.M.D.
6 t9 t.m
3 t3 t
1.5 t 1.5 t
4.5 t 1.5 t
d. Reactions
6 t9 t.m
4.5 t 1.5 t
e. Free Body Diagram
g. Main steel Reinforcement.
4.5 t
1.5 t
4.5 t
1.5 t
+
-
f. S.F.D.
Figure (3).
162 Chapter (3) - Consistent Deformations
Example (2)
For the shown two hinged
frame in fig.4 Draw B. M. D
Solution:
a) Main System
b) M0 Diagram
1.
2.
3.
4.
Choose the main system
as shown in Fig 4.a
Draw Mo.D (Fig4-b)
Draw M1. D (Fig4.c)
The compatibly equation
at B is
10 + X1. 11 = 0
EI.10 =EI
dlMM .. 10
= 43283
2
+ 42
816
+ 43
2
2
416
= -341.33
EI.11 =
EI
dlM1
= 484
+2
4
3
2
2
44
= 170.67
c) M1 Diagram
X1 = t
S
S2
11
10
M = M0 t X1M1
Mc = -16-42 = -24
m.t
Md = 0 -42 = -8
m.t
d) B.M.D.
Chapter (3) - Consistent Deformations 163
Example (3)
Draw B.M.D and free body
diagram for the given frame in
Fig. (5)
EI =10000 2.mt
Solution
4
A
I
16
B
I
C I D
10 t
1.
2.
3.
4.
Choose main system as
shown in Fig.5.a
Draw M0. D
Draw M1. D
The compatibility eqn. is
10 + X1 11 = 0
10 t
X1 = 0
10
a) Main System
40 t.m
+
b) M0 Diagram
-4 t.m
X1 = 1 t
-
4 t.m
4 t.m
-
111 t
4 t.m
c) M1 Diagram
17.16 t.m17.16 t.m
-
17.16 t.m
-
17.16 t.m- -+
22.84 t.m
8.57 t
5 t
8.57 t
5 t
d) B.M.D.
10 t
5 t5 t
9 t.m 9 t.m
5 t 5 t
9 t.m 9 t.m8.57 t
8.57 t
8.57 t
8.57 t
5 t5 t
8.57 t8.57 t
e) Free Body Diagram
Figure (5)
10 =EI
MdlM 0 =
4
2
8402
EI
164 Chapter (3) - Consistent Deformations
= EI
1280 = 128 m
11 =
484)4(
3
2
2
442
EI =
EI3
)38464(2
= EI3
896 =0.0299 m
X1 = 896
31280 = 4.29 t
5. Draw M.D
M = M0 +X1 M1
Mc = Mc = 29.44 = -17.16 t.m
Example (4)
Draw B.M,S.F.D s for the given
continues beam in fig.6
EI = 8000 t.m 2
Solution
The structure is once statically
indeterminate
a) Main System
1.
2.
3.
4.
Choose main system or primary
structure as shown the figure
(remove support B)
Draw M0. D
Draw M1. D
Compatibility equation
10 +X1. 11 = 0
10 = EI
dlMM 10
b) M0.D
c) M1.D
Figure (6)
Chapter (3) - Consistent Deformations 165
=
8752.1636
3
22
EI
= EI3
1404 =
EI
540
= 0.0675 m d) B.M.D.
11 =
32
32632
EI
= EI
36 = m0045.0
X1 = 36
468 = -15 t
M = M0 + X1. M1
MB = +39 - 45
= -9 m . t
Sketch the steel reinforcement as
shown in fig. 6.g
e) Reactions
f) S.F.D
g) Steel reinforcement
Figure (6)
Example (5)
Determine the reactions and
draw S.F and B.M.Ds for the
following structure shown in
Fig.7
(EI constant )
Solution ( using the deflection at 1)
Figure (7)
166 Chapter (3) - Consistent Deformations
One of the reactions may be considered as being extra. In this case let us
first choose the vertical reaction at 1 as the redundant assumed to be
acting downward. By the principle of superposition we may consider the
beam as being subjected to the sum of the effects of the original uniform
loading and the unknown redundant X1, as shown in Fig.7.b and 7.c we
should multiply 11 by X1 because 11 due to unit load only. The vertical
deflection at point 1 due to uniform load w t/m for primary structure is
given by
10 = EI
Lw
384
)2(5 4
And that the vertical deflection 11 due to 1 t at point 1 is given by
11 = EI
L
48
)2.(1 3
Note that 10and 11 can be determined by the method described in
deflection chapter.
Applying compatibility equation:-
10 +X1. 11 = 0
We obtain
EI
Lw
384
)2(5 4
+ X1 EI
L
48
)2( 3
= 0
From which
X1 = -8
10 w L
The minus sign indicates an upward reaction. With reaction at 1
determinate, we find that the beam reduces to a statically determinate one.
We can obtain reaction component at 0 and 2 from the equilibrium
equations:
Y = 0
Chapter (3) - Consistent Deformations 167
and from symmetry
y0 = y2
= (w(2L) - 2
1)
8
10WL
= wL8
3
The shearing force and bending
moment diagrams are as shown in
Fig.7.d and Fig.7.e
Figure (7)
Example(6)
Solve the given beam in Fig.8 using
different main systems.
Solution (1) (using conjugate beam)
10 + X1. 11 = 0
10 = 333.21
E
= 1
64
E
11 = EI
8)4
3
2(
= EI3
64
1.3
6464X
EIEI = 0
168 Chapter (3) - Consistent Deformations
X1 = YB = 3 t
i.e.
YA = 342 = 5 t
MA = 24243
= - 4 m. t
Figure (8)
solution (2) (using elastic load)
11110 .X = 0
10 = EI2
44
3
2
= EI3
16
11 = EI2
41
3
2
= EI3
4
13
4
3
16X
EIEI
= 0
i.e
X1 = MA = 4 m.t.
Figure (8) cont.
Solution(3) (adding intermediate hinge )
From the previous solutions we come to recognize that we are free to
select redundant in analyzing a statically indeterminate structure, the only
restriction being that the redundant should be so selected that the structure
remains stable. Let us cut the beam at mid-span section C and introduce a
pair of redundant couples called Mc, together with the original loading are
then applied to the main system as shown in the following Fig.8.c.
Chapter (3) - Consistent Deformations 169
The redundant Mc is solved by the condition of compatibility that the
rotation of the left side relative to the right side at section C must be zero.
Using the method of virtual load.
10 = co
= LL d
EI
MM 100
.
11 = cl
= LL d
EI
M2
10
The compatibility equation is
10 +Mc . 11 = 0,
knowing
Mc = + 16
2WL
Then Mfinal can be drawn by
knowing Mc +ve at mid span,
and:
M = M0 +X1 .M1
Figure (8) cont.
MA = - 4
2WL +
16
2WL(2)
= 8
2WL (ok)
170 Chapter (3) - Consistent Deformations
3. TWICE STATICALLY INDETERMINATE
STRUCTURES Consider the continuous beam shown in fig. 12 the first step is to remove
supports 1and 2 and put the two redundants X1 and X2. The original
structure is now considered as a simple beam (the primary structure )
subjected to the combined action of number of external loads and two
redundants X1 and X2 as shown in Fig.9.b. The resulting structure in
Fig.9.b can be regarded as the superposition of those shown in Fig.9.c and
Fig.9.d. multiplied by X1 and fig.9.e multiplied by X2 consequently. Any
deformation of of the structure can be obtained by the superposition of
these effects. Referring to Fig. 9.a, for unyielding supports, we find that
compatibility requires
1 = 0
2 = 0
Where
1 = deflection at redundant point (1) in the direction of reaction X1
due to external loads of the original structure
2 = deflection at point (2) in the direction of X2 due to external
loads of the original structure
By the principle of superposition the compatibility equations at supports 1
and 2 are as follow and referring to Figs. 9.c, 9.d and 9.e
10 + 11. X1 + 12 . X2 = 0
20 + 21. X1 + 22 . X2 = 0
Where
10 = deflection at redundant point (1) in the direction of reaction X1
due to external loads of the main system.
20 = deflection at point (2) in the direction of x2 due to external loads
of the main system.
11 = deflection at point (1) due to a unit load at point 1. (see Fig.9.d.)
12 = deflection at point (1) due to a unit load at point 2.( see Fig. 9.e.)
And so on.
Chapter (3) - Consistent Deformations 171
(a)
(b)Main System
(c)Deflections 10
and 20
(d) )Deflections
11 and 21
(e) Deflections 12
and 22
f) B.M.D.
Figure (9)
Example (7) For the shown continues beam in fig.10, Draw S.F, B.M.Ds. due to given
loads.
Solution Choose the main system as shown in fig.10.a., then the compatibility
equations are:
10 + X1. 11+ X2. 22 = 0
20 + X1. 21 +X2. 22 = 0
a) Main system
Figure (10)
The Flexibility coefficients are :-
10 = EI
dlMM 10
= 23
2
2
448(
2
EI
172 Chapter (3) - Consistent Deformations
)4842
42
= EI
1280
20 = EI
dlMM 02
20 =
4882
7525
)83253
2(
2
448
1
EI
= EI
288
11 = EI
dlM 2
1
11 =
4
3
2
2
842
EI
48 t.m 48 t.m
+
b. M0 Diagram
+
X1 = 1t
4 t.m
11
c. M1 Diagram
X2 = 1t.m
1 t.m
22
-
d. M2 Diagram
e. Reactions
Figure (10)
11 = EI3
256
21 = 12 = EI
dlMM 21 =
5
2
1641
EI =
EI
16
22 = EI
dlM
2
2 = 13
2
2
161
EI =
EI3
16
then
1280+ 2163
2561 X = 0 --------(1)
and
864 + 48X1 +16X2 = 0 ---------(2)
Solve equations (1) and (2)
X1 = -11.14 t
X2 = 20.57 m .t
To get reaction Yc 0 aM
0 = 814.1157.20
+ )121294)16( cY
Yc = 5.14 t
f. S.F.D.
Figure (10)
Chapter (3) - Consistent Deformations 173
From; y = 0
Y C +Y B +YA = 122
5.14 +11.14+ YA = 24
YA = 7.72 t
Mb = 412814.5
= -6.88 m .t
g. B.M.D.
Figure (10)
Hence S. F and B. M. Ds as shown in fig.10.f and g
Example(8) For the shown frame fig.11 draw N.F, S.F, and B.M.Ds due to given
loads.
a) Main System
Figure (11)
Solution (Twice statically Indeterminate)
Choose the main system as shown in Fig 11.a, hence the compatibility
equations are:
10 + X1 11 + X2 12 = 0
20 + X1 21 + X2 22 = 0
The value of flexibility coefficients are as Follows:
11 = EI
dlMM 11
=
5455
3
2
2
552
EI =
EI3
850
174 Chapter (3) - Consistent Deformations
21 = 12 = EI
dlMM 21
=
1
2
55585
2
EI
= EI
5.32 =
EI3
5.97
22 = EI
dlM 2
2
=
3
2
2
81151
1
EI =
EI3
23
10 = EI
dlMM 10
=
5
3
2840
1
EI=
EI
3200
20 = EI
dlMM 20
=EI3
320
hence
-3200+ 850 X1 + 23 X2 = 0 ----(1)
-320 + 97.5 X1 + 23 X2 = 0 ----(2)
solving equation (1) and (2)
-1843.48+ 436.68 X1 =0
i.e. X1 = 4.22 t Figure (11)
And X2 = -3.98 m. t
MF = Mo + X1. M1 - X2. M2
MF = Mo + 4.22 M1 - 3.98 M2
MB = + 3.98 m.t
Mc = 22.45 = 21.10 m.t
Md = 98.3522.4 = -17.12m.t 4
Reactions
YF = Yo + X1. Y1 - X2. Y2
Chapter (3) - Consistent Deformations 175
i.e.
YA = YA0 + X1. YA1 + X2 YA2
= 8
198.3020 = 19.5 t
e) Reactions f) B.M.D.
g) N.F.D. h) S.F.D.
Figure (11)
4. 3-TIME STATICALLY INDETERMINATE The following structures shown in Fig.12 are 3-time statically
indeterminate structures:
X3 = 0
X1 = 0
X2 = 0
Main System Original Structure
(Fixed Bexm)
Case (1)
X3 = 0
X1 = 0
X2 = 0
Main System Original Structure
Case (2)
Figure (12)
176 Chapter (3) - Consistent Deformations
X2
X3
X1
X3
X1
X2
Main System (2) Main System (1) Original Structure
Case (3)
Figure (12)
In this case the redundant are; X1, X2, and X3 and the compatibility
equations are:
10 + X1 11 + X2 12 + X3 13 = 0
20 + X1 21 + X2 22 + X3 23 = 0
30 + X1 31 + X2 32 + X3 33 = 0
Example (9) For the given frame shown in fig.13 find the reactions and draw B.M.D.
Solution To solve this frame we start by removing support A and introducing in its
place three redundant reaction components X1, X2, and X3 as shown in
Fig.13.a, hence:-
10 m
10 m
A
C D
B
1.2 t / m
1.2 t / m
X2
X3
X1
a) Main System
Figure (13)
10 +X1 11 + X2 12 + X3 13 = 0
20 +X1 21 + X2 22 + X3 23 = 0
30 +X1 31 + X2 32 + X3 33 = 0
Chapter (3) - Consistent Deformations 177
60 t.m
60 t.m
60 t.m
-
-
Mo.D
X1 = 1t
10 t.m
10 t.m
10 t.m
10 t.m-
- -
M1.D
X2 = 1t
10 t.m
10 t.m
10 t.m
+
+
M2 .D
X3 = 1t.m
+
+ +
1t.m
1t.m 1t.m
1t.m
1t.m
M3 .D
Figure (13) cont.
Values of flexibility coefficients:-
11 = EI
dLM .21 =
EI
1667
12 = dLEI
MM 21 = EI
1000
13 = dLEI
MM 31 = EI
200
21 = 12
22 = dLEi
M 22 =
EI
1333
23 = 32
= dLEI
MM 23 = EI
150
31 = 13 = EI
200
33 = dLEI
M 23 .
= EI
30
178 Chapter (3) - Consistent Deformations
10 = dLEI
MM 01 = 5000
20 = dLEI
MM 02 = -7500
30 = dLEI
MM 03 = -800
hence
0
0
0
30150200
15013331000
20010001667
800
7500
5000
3
2
1
X
X
X
by Solving the above equations; we obtain
3
2
1
X
X
X
=
m33.3
6
1
tons
Final B.M.D
M = M0 + X1 M1 + X2 M2 +X 3. M3
6 t
3.33 t.m
1 t
1.2 t / m
6.67 6.67
6.67 6.67
3.33 3.33
8.33
+- -
b) Reactions c) B.M.D.
A
C D
B
d) Elastic Curve
Figure (13)
Chapter (3) - Consistent Deformations 179
The final results are shown in Fig. 13.b, c and d at which the moment
diagram for the whole frame is given. A sketch of elastic curve of the
frame due to bending distortion is also shown by the dashed line in
Fig.13.d. Note that in this case there is one point of inflection in each
column and two point of inflection in the beam CD.
By referring to the previous example, we see that by using the method of
consistent deformations in analyzing a rigid frame, we encounter hard
calculations of the flexibility coefficient. The work, if done by hand, will
become complex if the problem involves as many redundants as a rigid
frame usually does. As a matter of fact, the method of consistent
deformations is often used by hand calculation, since a solution can be
much move easily obtained by any other method. However, with the
development of high-speed electronic computers, this method has
regained considerable strength in the scope of structural analysis.
Another solution
By using the symmetry; the frame becomes twice statically indeterminate
(fig.14); because X2= X3; hence:
X1X3 = X2
X2
1.2 t / m
10 10
Main System
Figure (14)
10 + X1 11 + X2 12 = 0
20 +X1 21 + X2 22 = 0
Calculate the displacement coefficients as follows:
15 t.m
1t
-
-10 t.m
10 t.m
-
10 t.m
10 t.m
X1 = 1t
X2 = 1t.m
1t.m
1t.m
1t.m
1t.m
X2 = 1t.m
Mo .D. M1 .D. M2 .D.
Figure (14) cont.
180 Chapter (3) - Consistent Deformations
10 = EI
dlMM 10
= 103
21015 =
EI
1000
20 = EI
100
11 = EI
dlM
2
1
=
)10
3
2
2
1010(2101010
1
EI
= EI3
5000
12 = EI
dlMM 21 = 21
=
)1
2
1010(211010
1
EI
= EI
200
22 = EI
dlM 2
2
= 1101101101
EI
= EI
30
Hence;
-1000 + 22003
50001 X = 0 ------ (1)
and
- 230200100 1 X = 0 -------(2)
Solve(1) ,(2)
- 213
255 XX = 0
- 213
20
3
10XX = 0
13
5X =
3
5
Chapter (3) - Consistent Deformations 181
X1 = 1 m.t, X2 = - 3
10
Mf =M0 + X1M1 + X2 M2
MA = 0 + 0- 13
10 = +3.33 m.t OK
Mc = 3
1010 = -6.67 m.t OK
3.333.33
-+
8.33
6.67
6.67
-
6.67
6.67
B.M.D.
Figure (14) cont.
The same result in Fig.13.c.
5.CASE OF n- STATICALLY IN DETERMINATE
STRUCTURES
Both the deflections resulting from the original external loads and the
flexibility coefficients for the primary structure can be obtained by the
method of virtual work. The remaining redundant unknowns are then
solved by simultaneous equations. This process can be generalized. Thus,
for a structure with n redundants, we have:
182 Chapter (3) - Consistent Deformations
10 + 11X1 + 12 X2 +………….. +1n X n = 0
20 + 21X1 + 22 X2 +………….. +2n X n = 0
. .
. .
. .
. .
. .
n0 + n1 X1 + n2 X2 +………... + nn X n = 0
..(5)
Equation (5) in matrix from is:
0
.
.
.
.
0
0
.
.
.
.
.
.......
...........
..........
...........
..........
.......
.......
.
.
.
.
2
1
21
22221
11211
0
20
10
nnnnn
n
n
n X
X
X
……(6)
or simply
110 nnxnn
X = 0
Example (10)
For the shown fixed beam in
fig.15 draw B.M & S.F.Ds due
to the shown applied loads
(w=2 t/m)
Solution
From symmetry
X1 = X3
X2 = 0
hnce the beam is once st. Ind.
10 + 11.X1 = 0
Figure (15)
Chapter (3) - Consistent Deformations 183
10 = EI
dlMM 10
= 183
2 2
Lwl
= EI
wl
12
3
11 = EI
dlM .21
= EI
L 11 =
EI
L
X1 = 11
10
S
S =
12
2WL
= 12
)6(2 2
= 6 t.m
YA =2
wl =
2
62 = 6t
Figure (15)
Example (11)
For the given fixed beam
shown in fig. 16; find the fixed
end moments MA and MB. Hence
draw B.M and S. F. Ds (use the
method of conjugate beam)
Figure (16)
Solution (using conjugate beam)
The fixed beam shown is
statically indeterminate to the
second degree since the
horizontal force does not exist.
End Moments MA and MB are
selected as redundants. By
applying the conjugate beam
method to determine MA and MB
based on the slope and
deflection at A and B must be
zero.
184 Chapter (3) - Consistent Deformations
Y = 0
EI
LM
EI
LM
EI
abp BA
222
. = 0
MA +MB = L
bap ..
BM = 0
2MA+MB = 2
2....
L
bap
L
bap
hence
MA = 2
2..
L
bap, MB =
2
2 ..
L
bap
YA = L
bPMM BA . ,
YB = P-YA
Example (12)
For the given fixed beam
shown in fig.17 draw S.F
and B.M.Ds.
A
b
B
a
L
M
A B
BA
+
-M.a/L
M.b/L
2EILM.a
2
2M.b
2EIL
a)M0.D
2EI
M
M
b
a
M .La
2EIbM .L
-
+
b) Ma and Mb
Figure (17)
Solution The deflected curve will
be somewhat like that
shown by the dotted line,
which gives the sense of
the end moments as
indicated. Now we choose
MA and MB as redundants.
The elastic load based on
the moment diagrams
divided by EI plotted for
external moment M and
redundants MA and MB as
shown Must be in
equilibrium from Y = 0;
then:-
Chapter (3) - Consistent Deformations 185
EIL
aM
EI
M
EIL
bM
EI
LM LBA
2
.
22
.
2
. 2.
2
= 0
MA – MB = 2
22 )(
L
baM …….(1)
From BM = 0; then:-
)3
.(2
.
3.
2
.
3
2.
2
.
3
2.
2
. 22 ab
EIL
aML
EI
LMb
EIL
bML
EI
LM BA =0 ….(2)
2MA – MB = 2
22 22(
L
bbaaM
Solving (1) and (2)
MA = )2(.2
baL
bM
MB = )2(.2
abL
aM
Ma
bM- -
+ +
c) B.M.D.
-Ya bY
d) S.F.D.
Figure (17)
Note that MA and MB are the same sense as externally applied M, if a>3
L
and b>3
L.
6. SETTLEMENT OF SUPPORTS
In a more general from, we may include the prescribed displacements
(other than zero ) occurring at the releases of the original structures. Then
these values ,......., 21 (Fig.18) must be substituted for the zeros on the
right-hand side of equation (6)
21P0Q
3w
1 2
Figure (18)
t/m-
186 Chapter (3) - Consistent Deformations
Thus
nnnnnn
n
n
n X
X
X
.
.
.
.
.
.
......
.........
.........
.........
......
......
.
.
.
2
1
2
1
20
22221
11211
0
20
10
In which the column matrix n0 on the left hand side represents the
displacements at redundant points of the released structure due to the
original loads; the square matrix nn represents the structure flexibility,
each column of which gives various displacements at redundant points
due to a certain unit redundant forces; and the column matrix on the
right hand side contains the actual displacements redundant points
(settlements) of the original structure.
Settlements of supports (or temperature changes) in case of indeterminate
structures will develop additional internal force, and reactions. But in
case of determinate structures the settlement of supports (or temperature
changes), no additional internal force and no reactions will develop.
7. CHANGES OF TEMPERATURE:
The change of temperature has no effect on internal forces and internal
deformations at centerline of statically determinate structures. On the
other hand, in statically indeterminate structures, the changes of
temperature will result in the development of internal force and reactions.
a. Case of Uniform Rise of Temperature:
For the given once statically indeterminate beams and frame in Fig.19,
the compatibility equation is
10 +X1 11 = 0
Chapter (3) - Consistent Deformations 187
t co
ot c
a. Frame
t co
ot c
b. Beam
Figure (19)
And the main system as shown in Fig.19.c and d.
t co
ot c
10
c. Main system
11
t co
ot c
X1 = 1t
d. get N1.D
Figure (19)Cont.
We = Wi
i.e.
10 = dlN .1 = )..(1 dltN
= dlNt .. 1
10 = t. ( Area of normal force diagram )
Mf = X1 M1 (M0 = 0 )
Nf = X1 N1 (N0 = 0 )
b. Non–Uniform Rise of Temperature
In case of non-uniform rise of temperature shown in Fig.20, also the
compatibility equation is
10 +X1.11 = 0
188 Chapter (3) - Consistent Deformations
t co
ot c1
2
=
2
1t c
ot c
10
a. Main system
X1 = 1t11
b. get M1.D
C. L.h/2
h/2
.t .dL1
2.t .dL
d
d
d - ve M
c. Elongation & Rotations
Figure (20)
And from
We = Wi
hence
1. S10 = dMsdN .11
= )).(
()2
.( 211
211
h
ttMdl
ttN
= dlMh
ttdlN
tt.
21
211
21
Negative sign for d because the elongation is opposite to the M. Get X1
and hence
Mf = X1. M1
Nf = X1. N1
Knowing that:-
S11 = EA
dLN
EI
dLM 2
121
Chapter (3) - Consistent Deformations 189
Example (13)
For the given continuous beam
shown in Fig.21; draw S.F and
B.M.Ds due to
1) given load
2) Settlement at support B of
2cm
3) t temp. = 20
b =25 cm
I = 7.146 310 m4
E = 2.1 26 /10 mt
= 1 510
h1 = 70 cm
h2 = 80 cm
Solution
1. Due to Uniform Load
The compatibility equation is:
10 +X1.11 = 0
10 = dlEI
MM 10 .
10 = -46.59 / EI
11 = dlEI
M.
12
Figure (21)
= 3.80 / EI
10 +X1 11 = 0
i.e.
X1 = 11
10
= 12.26 t. m
B.M.D. as shown in Fig.21.c.
190 Chapter (3) - Consistent Deformations
2. Due to 2 cm Settlement at B
10 +X1 11 = 600
2
800
2
10 = 0
11 = EI
dLM 2
1 = 3.8/ EI
X1 = 8.31200
7 EI
= 23.0 t.m
as shown in Fig.21.f
3. Anther Solution for B. M, S. F. Ds due to 2cm Settlement at B:
10 +11 .X1 = 100
2
10 = 0
11 = EI
dlM 2
=
2.12
8
2
643.3
3
2
1
43.3
EI
= 44.45/ EI
X1 = 45.44
10146.7)2100000(02 3
= 6.75 t
Mf = X1 M1
Qf = X1 .Q1
Figure (21)
4. Due to t = +20o
= 1 510
10 +X1 11 = 0
10 = dMdN 11
Chapter (3) - Consistent Deformations 191
= dlMh
tdlN
tt.
211
21
= 0 + h
t (area of M1.D)
10 = 1 510 20 ( )8.0
8
7.0
6(
2
43.3 )
= - 6.37 310 m
i.e.
X1 = 11
10
11 = EI
dlM 2
1
= EI
45.44
Figure (21)
X1 = 45.44
10146.7)210000(1037.6 33
= 2.15 t
Mf = X1 M1
Qf = X1 .Q1
hence
Mb = 2.153.43 = 7.37 m. t
Reaction at A
= 6
37.7 = 1.23 t
Reaction at B
=8
36.7
6
36.7 = 2.15 t
Reaction at C
= 8
36.7 = 0.92 t
Figure (21)
192 Chapter (3) - Consistent Deformations
Example (14)
Compute the reactions and draw the Bending Moment diagram for the
beam shown in fig.22 due to the following support settlement:-
- point A . 5 cm downward
- point B 1.0 cm downward
- point C 1.5 cm downward
- point D 0
EI = 5000 t .m
Solution
A B C D
I 3 I 2 I
866
a) Main
System
b) M1.D.
X1 X1 X2X2
1 t.m
+
c) Settlement
Condition
d M2D.
0.5 1.0 1.5
1 t.m
+
e. B.M.D.
f. S.F.D.
0.86 t.m
6.89 t.m
+
-
+
--0.14
1.29
0.86 0.86
Figure (22)
Chapter (3) - Consistent Deformations 193
The compatibility equations are:
12211110 . XX = 1 …….(1)
22221120 .. XX = 2 …….(2)
From either the method of virtual work and the geometry of settlement
condition the values of 1 and
2 are:
1) 1 = 0
2) 2800
5.1
600
5. = 0.0027 rad.
And;
11 = dlEI
M 12
= )3
1
3
21
3
2(
2
61
EIEI
=
EI3
8
12 = 21 = dlEI
MM 21
= 13
1
)3(2
61
EI =
EI3
1
22 = dlEI
M 22 =
3
2
22
81
3
2
)3(2
61
EIEI =
EI
2
Hence;
cB XX3
1
3
40 = 0
cB XX 23
10 = EI (0.0027)
XB = -0.86 t. m
Xc = 6.89 t. m
The find B.M.D are shown in Fig.22.e.
8- BEAM ON ELASTIC SUPPORTS:
For the given structure shown in fig.23, support at b is an elastic support.
The spring stiffness is K (force / unit displacement). To determine
reaction and deflection at b (b), assume the spring load is X1. The
downward deflection 10 at b plus that caused by upward reaction X1
should be equal to the spring contraction (b). Hence;
194 Chapter (3) - Consistent Deformations
10 +11. X1 +K
1 .X1 = 0
The last term in the equation is the
spring contraction
X1 =
kS
111
10
10 = EI
WL
8
4 =
EI
dLMM 10
11 = EI
L
3
3
= EI
dLM 2
1
X1 =
3
31
1
8
3
KL
EIWL
1 = .1
K
X
1
Figure (23)
For non-yielding support (k = ) , the above equation gives;
X1 = WL8
3 o.k. (Case of roller support)
Example (15)
For the shown beam in Fig.24,
draw S.F and B.M.Ds in case
the support with stiffness K=
10t/m. compare the results of
the two examples
2 t / m
B
6
A
6
C
Figure (24)
Solution K = 1000 t/m
The compatibility equation is;
10 +X1 (11+ )1
K = 0
10 = EI3
1404 = 0.0675 m
36 t.m
+
a) M0.D
Figure (24)
Chapter (3) - Consistent Deformations 195
11 = EI
36 = 0.0045 m
3 t.m
1t
+
b) M1.D
Hence
X1 =
1000
10045.0
0675.
= -12.27 t
Mf = M0 + X1 M1
Mb = 327.1236
= -0.82 t.m
Qf = Q0 +X1.Q1
QA = 6
82.
2
62
= 5.86
QB = 6
282.
2
622
= 12.28 t
0.82 t.m
8.59 t.m
++
8.59 t.m
c) B.M.D.
+ +- -
5.86 6.14
6.14 5.86
d) S.F.D.
e) Main Steel reinforcement
Figure (24)
The value of –ve moment at spring support B is very small if we compare
with –ve moment at B for example 5 (Fig.6). If a beam is provided with n
redundant elastic supports with stiffness K1, K2, …. K n; then the general
compatibility equations in matrix form are:-
0
.
.
.
.
0
0
.
.
.
.
.
)1
(
...
...
...
...
..)1
(
..)1
(
.
.
.
.
2
1
21
2
2
2221
112
1
11
0
20
10
n
n
nnnn
n
n
n X
X
X
K
K
K
196 Chapter (3) - Consistent Deformations
Example (16) For the given frame shown in fig.25 Draw B.M.D. due to
1) Given loads
2) Horizontal displacement at C = 1 cm to right
EI = 12000 t.m2
Kspring = 100 t/m
Solution
1. Due to given loads
4 4
5 t 5 t
4 4
6
A
B CD
Spring
X2= 0
X1= 0
a) Main System
+
20 t.m 20 t.m
b) M0.D.
X1= 1
1t
6 t.m
6 t.m -
-
b) M1.D
X2= 1
4 t.m
-
b) M2D
Figure (25)
10 + X1 11 + X2 12 = 0
20 +X1 21 + X2 (22 + )1
KB = 0
10EIS = dlMM 01 = 3)2
168(20
= -720
20EIS = dlMM 02 = )2042
422
3
2
20
420(2
= -586.7
Chapter (3) - Consistent Deformations 197
12EIS = dlMM 21 = )66
5
2
84(2
= 96
11EIS = dlM 21 = 6
3
2
2
666
3
2
2
166
= 264
K
EIEIS 22 =
100
11200024
3
2
2
84 2
= 205.33
264 X1 + 96 X2 = 720 …..(1)
96 X1 + 205.33 X2 = 586.70 …..(2)
96 + 34.91 X2 = 261.8 …..(3)
170.42 X2 = 324.9
X2 = 1.9 t
X1 = 2.03 t
M = M0 + X1 M1 +X2 M2
- ++
12.18
12.18
6.14
e) B.M.D.
Figure (25)
Moment at spring support is +ve moment because the stiffness of spring
support is small value. If the value of stiffness is bigger then 100 t/m the
positive moment decrease and in case of K = , the –ve moment at
support B will be the maximum values of –ve moment
2. Horizontal Displacement 1 cm at C
0 + X1 11 + X2 12 = -1 (-ve sign because displacement
in the opposite side of X1)
0 + X1 21 + X2 (22 + )1
K = 0
Get X1 and X2 and then draw B.M,, S.F, N.F..Ds as shown in Fig.26
198 Chapter (3) - Consistent Deformations
Hence (EI = 12000 t.m2)
264 X1 + 96 X2 = 100
1 (12000)
96 X1 + 205.33 X2 = 0
Hence
X1 + 0.36 X2 = -0.45 …..(1)
X1 + 2.14 X2 = 0 …..(2)
Subtraction (1) and (2)
X2 = 78.1
45.0 = 0.25 t
X1 = 96
9.51 = -0.54 t
Hence:-
M = X1 M1 +X2 M2
Q = X1 Q1 +Q2 M2
N = X1 N1 +N2 M2
MD = +3.24 m.t
MB = +0.62 m.t
X2= 0
X1= 1t
3.24
3.24
0.62+
+
f) B..M.D
0.54
0.32
0.08
0.54
0.40
g) Reactions
+
+
0.32
0.32
0.54 0.54
h) N.F.D
+
+
-
0.54
0.32 0.32
0.08
i) S.F.D.
Figure (25) Cont
Chapter (3) - Consistent Deformations 199
Example (17)
Draw B.M.D. for the given structure shown in Fig.26
EI = 10000 t.m2, kB = 5 t/cm
Figure (26)
Solution:
The given structure is once statically indeterminate
a. Primary Structure
b. Mo Diagram
c. M1 Diagram
d. Figure (26)
200 Chapter (3) - Consistent Deformations
d. B.M.D.
Figure (26)
)1
( 11110
BKX = 0
10EI = 5.125.235.275.383
6.35.1
3
2
2
325.23
+
5.275.386243
3)5.225.235.175.38(5.0
28163
24
3
2
2
8504623)475.385.262(5.0
= -1826.985
11EI = )5.13
25.2(
2
35.1)
2
45.2(35.24344
3
2
2
48
5.13
2
2
35.1)67.5.1(
2
6.31)
2
5.25.1(6.35.1
= 139.87
Hence
)500
1000087.139(98.1826 1 X = 0
X1 = 11.43 t
Mfinal =M0+X1M1
Qf =Q0 +X1 Q1
Nf =N0 +X1N1
Rf =R0 + X1R1
B.M.D. is shown in Fig.26.d.
Chapter (3) - Consistent Deformations 201
Example (18):
Draw B.M.D. for the following structures shown in Fig.27
EI = 15000 t.m2, kA = 300 t/cm, kB = 350 t/cm
Figure (27)
Solution:
The structure is twice statically indeterminate; hence:-
10 +X1 (11 + 122)1
XK A
= 0
20 +X1 21+X2 (22 + BK
1) = 0
a. Primary Structure
125
304
26
26
50
24
+
-
-
- -
b. Mo.D.
Figure (27)
202 Chapter (3) - Consistent Deformations
c. M1.D.
X2= 1t
+
+
+
10
10
10
10
15
d. M2.D.
Figure (27)
EI.10 = dlMM 01.
= 26610)203
24(
2
1010
)30510125(5.10305125(3
5
42.32455.7525.63
2
= 3344.63
EI 20 = dlMM 02
= 3010125153
51062681050
3
1
+ 5.12525.63
25.0)153010125(
= -21713.28
EI 11 = )53
25(
2
555.7551061010
3
2
2
1010
Chapter (3) - Consistent Deformations 203
= 1225.21
EI 22 = )53
210(
2
555.125101061010
3
2
2
1010
= 1725.21
EI 21 = -1225
Hence
3344.63+X1(1225 + 21225)300
15000X = 0 ……..(1)
)350
1500021.1725()21.1225(28.21713 21 XX = 0 ……..(2)
From (1) and (2)
X1 = 5.51 t
X2 = 8.46 t
Hence
M final = M0 +X1.M1 +X2.M2
B.M.D. as shown in Fig.27.e
e. B.M.D.
Figure (27)
Example (19)
Draw B.M.D. due to loads and 10t inter fiber for the given frame
shown in Fig.28
I = 0.048 m4, E = 200 t/cm
2, kC = 400 t/m,
kD = 300 t/m, h=100 cm
204 Chapter (3) - Consistent Deformations
4 t / m
o10 c
o0 c
A
B
C D
D
8 8 10
Figure (28)
Solution:
This structure is twice statically indeterminate
1. B. M. D. due to given loads
EI10 = dlMM 01
=
53.585.137(
3
853.5
3
2
2
885.137
+ )53.57.14707.385.137(2
1)07.37.147
2
07.315.6(832
3
207.3
3
2
2
107.147
= -9226.370
17.23
14.77
137..85147.70
32
+
a) M0.D.
X1= 1t
5.53
3.07
-
b M1.D.
Figure (28)
Chapter (3) - Consistent Deformations 205
X2= 1t
6.15
3.07
c) M2.D.
d) B.M.D.
Figure (28)
EI20 = dlMM 02
= -
70.1473
2
2
1015.607.3
3
2
2
885.137
15.67.14707.385.137(3
8
))07.37.14715.685.137(2
1
2
15.607.3832
3
2
= -10229.045
EI11 = dlM 21 = 2653.5
3
1 2
= 265.03
EI22 = dlM 22 = 2615.6
3
1 2
= 327.79
206 Chapter (3) - Consistent Deformations
12 = 15.63
2
2
1007.307.3
3
2
2
853.5
)07.315.653.5(
2
115.607.307.353.5
3
8 2
= 261.73
But
10 +X1(11+ 122) XK
EI
C
= 0
20 +X1 21 + X2 (22 + )dK
EI = 0
Hence
21 73.261)400
048.200000003.265(37.9226 XX
= 0 ……(1)
)300
046.10279.327()73.261(04.10229
6
21
XX = 0 ….…(2)
Solving equations (1) and (2), hence:-
X1 = 12.75 t
X2 = 10.63 t
then
M final = M0 +X1 .M1 +X2 .M2 , and B.M.D. as shown in Fig.28.d
2) Springs deflections due to loads
c = 100400
75.12 =3.1875 cm
d = 100300
63.10 = 3.546 cm
2. B. M.D. due to t = +100 (inside the frame)
Figure (28)
Chapter (3) - Consistent Deformations 207
(10)t = dlMh
ttdlNt .
)(... 1
1210
+ dlM .1
= 10-5
2
2653.5
00.1
)100( (neglect effect of N1)
= -0.72 10-2
(20)t = )2615.62
1(
1
1010 5
(neglect effect of N2)
= -0.8 10-2
-ve sign because the rotation of the cross section is in the opposite sense
of M1or M2.
Hence:-
EI (10)t+X1( 12211 ) XK
EI
c
= 0
EI (20)t+ )()( 222211
dK
EIXX = 0
-691.2+X1 (265.03+240) +X2207.97 = 0 ….. (3)
-768.0+X1 207.97+X2 (327.79+320) = 0 ….. (4)
From (3) and (4)
X1 = 0.99 = 1.0
X2 = 0.90
Then
Mfinal = X1M1+ X2 M2 , hence B.M.D. as shown in Fig.28.f.
-
8.298.60
f. B.M.D.
Figure (28)
208 Chapter (3) - Consistent Deformations
In case of t = +10 outside the frame hence the B.M.D. is as follows:
+
8.29
8.60
g) B.M.D.
Figure (28)
9. FORCED DEFORMATIONS: Forced deformation are those not caused by external loads; but caused for
example by sliding or dettelemets of supports, and temperature
changes,….. etc. hence; We = Wi = 0
The procedures are:
1. Choose the main system.
2. Apply the forced deformation to the main system
3. Apply unit redundant, one at a time to main system and find M1, N1,
Q1 for each redundant
4. Calculate the values of displacements or rotation at removed
redundant in the main system Due to applied case of forced
deformation and also all unit redundant. Hence;
We = Wi
5. Calculate 10 from We = 0 or from geometry of deformed shape as
follows:-
10 = d1
M 1dN (for temps change)
Where:
d = . t dl (uniform rise of temp).
Chapter (3) - Consistent Deformations 209
and d =
2
2
1
ttdl (non-uniform rise of temps).
d = 0 (uniform rise of temps).
And d =
h
2 t
1t
dl (non-uniform rise of temp).
(t1 inside the frame, and t2 out side the frame)
6. Apply the compatibility equations and get the values of redundants
for once statically indeterminate structures.
10+ X1 11 = 0
Where:
11 = EA
LM
.N
EI
dL ̀
2
12
1
For frames, Arches, and beams with link
11 = EA
LM
.N 2
12
1 for trusses
7. Calculate the internal forces in the statically indeterminate structures
due to force deformation then;
Mf = X1. M1 (M0 = 0)
Qf = X1. Q1 (Q0 = 0)
And Nf = N1.N1 (No = 0)
Internal forces in determinate main system due to forced deformation
are equal to zero. Also, the displacement or rotation at any point (due
to forced deformation is:
n = n0 + X1 n1
8. In case of twice statically indeterminate structures;
10 + X1 11 + X2 12 = 0
20 + X1 21 + X2 22 = 0
And also;
20 = dM .2N d .2
22 = EA
LNM
.22
EI
dL 2
2
210 Chapter (3) - Consistent Deformations
12 = 21 = EI
dL
2
1MM
Mf = M1. X1 + M2 . X2
Qf = Q1. X1 + Q2. X2
Nf = N1. X1 + N2. X2
Example (20)
For the shown frame fig.29, draw B.M.D due
1) 3 cm down ward settlements at A
2) Uniform rise of temperature of 40o c.
3) Non uniform rise as given.
EI = 12000 t.m2, = 1 x 10
-5 , EA = 8000 t.
AB
C D
t1= 10°C
t1= 30°C
Figure (29)
Solution
1) 3 cm down ward settlement for main system
S10
X1=0a) main system
Figure (29)
Chapter (3) - Consistent Deformations 211
1m.t
X1=1m.t
1m.t
1/121/12
b) M . D1
1m.t
c) N . D11m.t
Figure (29)
We = Wi = 0
or
We = 0
i.e.
1.10 + 12
1 (0.03) = 0.
10 = 12
0.03-= -0.0025 m
11 = EI
dL 2
1M +
EA
dL 2
1N
= (1 x 4 + 2
1x12 x
3
2)
EI
1
= EI
8= 0.00067 m
then
X1 =
11
10-
=
0.00067
0.0025 = 3.73 t
Mf = X1. M1
212 Chapter (3) - Consistent Deformations
3.73m.t
3.73m.t
d) B.M.D
Figure (29)
2) Uniform rise of temperature
At main system
1 10 = .d 1
N
= . t. .dl 1
N
= 1 x 10-5
x 40
12
4 -
12
4= 0
hence X1 = 0 no internal forces in this case because the roller support at A
will move due to uniform rise of temp hence B.M.D. is zero if the two
supports at A and B not in the same level the internal forces for this case
has values.
3) Non uniform nise in temps:
1. 10 = .ds 1
.do 1
MM
=
1
30 - 10
EA
dL.
12
30 10
EI
dL.
1
NM
= 10-5
0 x 20
EI
8 20
= EI
31060.1 x
X1 =
11
10
=
8
31060.1 x = 0.0002 t
Mf = X1. M1
Chapter (3) - Consistent Deformations 213
0.0002m.t
0.0002m.te) B.M.D
Figure (29)
Example (21)
For the shown frame find B.M.D. due to 4 cm downward settlement at, B,
2 cm slide displacement to right at B, 1cm at B, downward settlement,
and 0.01 rad clockwise at A
EI = 16000 t.m2
C
A
B
0.01 rad
1cm2cm
4 cm
Figure (30)
Solution
We = 0
10 (1)- 4
3
100
1 + 0.01 x 10 +
4
3 x
100
4 = 0
10 = 400
3- 0.10 - 0.03
= - 0.13 + 0.007s
= - 0.1225 m
11 = EI
dL 2
1M
214 Chapter (3) - Consistent Deformations
= EI
1 4 x
3
2 x
2
4 x 4 6 x 4 x 6
2
6 x 3
2 x
2
8 x 6 (6)
3
2 x
2
6 x 6
= 0.268 m
X1 =
11
10
=
0.268
1225.0 = 0.46 t
Mf = X1. M1
0.01
X1=0
1cm
S10
1t
3/4t
3/4t
X1=1t
6
1
Figure (30)
The problem can be solved for each deformation and by the principal of
superposition we can get the final result. As shown.
4.6m.t
2.76m.t
2.76m.t
2.76m.t
Figure (30)
Chapter (3) - Consistent Deformations 215
Example (22)
For the shown frame Fig.31, draw B.M.D. due to given forced
deformation EI= 50000 t.m2
1cm
C
B
D
2cm
2cm
Figure (31)
Solution
The frame is 3 times statically indeterminate; hence;
10 + X1. 12 + X2. 12 + X3 13 = 0
20 + X1 21 + X2. 22 + X3 23 = 0
30 + X1 31 + X2 32 + X3 33 = 0
We = Wi = 0
i.e.
1. 10 – 1 x 0.01 – 18 x 0.001 = 0
X3=0
S30S10
X1=0
X2=0
S20
a) Main system
b) M1.D.
Figure (31)
216 Chapter (3) - Consistent Deformations
10m.t
10m.t
X2=1
M . D2
c) M2.D.
8m.t
8m.t
X3=1
M . D3
d) M3.D.
Figure (31)
Then:-
10 = 0.028
and;
1 x 20 – 1 x .02 – 10 x 0.001 = 0
20 = 0.03
And,
1. 30 – 1 x .02 + 8 x 0.001 = 0
30 = 0.012
Also
11 = EI
dL 2
1M
=
18 x 5 x 18 18 x
3
2 x
2
18 x 8
EI
I = 0.05 m
13 = (-8)5 18EI
I = -0.07128 m
21 = 12 =
10 x
3
2 8
2
10 x 8 18x5x10
EI
I = 0.0326 m
22 =
10 x 5 x 10 10
3
2 x
2
10 x 10
EI
I x = 0.0166 m
32 = 23 = (-8) 5 x 10EI
I = -.8 x 10
-3 m
33 =
8 x
2
8 x 8 8 x 5 x 8
EI
I
3
2 = 9.8 x 10
-3 m
Chapter (3) - Consistent Deformations 217
Then the compatibility equations are
0.028 + 0.05 X1 + .0326 X1 – 0.0144 X3 = 0
0.03 + 0.0326 X1 + .0166 X2 – 0.008 X3 = 0
0.012 – 0.0144X1 - .008 X2 + 0.0098 X3 = 0
Solve the 3 equations hence:
X1 = 5.27 t
X2 = -14.186 t
X3 = -5.6 t
Hence
Mf = M0 + X1M1 + X2M2 + X3M3
= 0 + 5.27 M1 – 1486M2 – 5.6M3
e) B.M.D.
Figure (31)
Example (23)
For the shown frame in Fig.32, draw B.M.D. due to given case of forced
displacements at supports
EI = 20000 t.m2
Figure (32)
218 Chapter (3) - Consistent Deformations
Solution
Part cgf is determinate then no internal forces due to forced displacement.
Hence the part A de B is twice statically indeterminate, then;
10 + X1 11 + X2 12 = 0
20 + X1 21 + X222 = 0
Choose main system as shown, hence:-
X1
S20
X2
S10
2I
main system
M . D1X1=1
6m.t
1t
6m.t 6m.t
6m.t2I
M . D2
1/101/10
X1=1
1m.t
1m.t
Figure (32)
We = Wi = 0
Chapter (3) - Consistent Deformations 219
i.e.
1. 10 + 1 0.03 = 0
10 = - 0.03 m
1 x 20 +1 (0.001) - 0.02 1 = 0
20 = +0.001 m
And
11 =
EI
324 6 x
2
x56 6 x
3
2 x
2
6 x 6 2
EI
I
22 = EI
7.67
3
2
2
1 x 6 x 1
EI
I
2
10 x 1
x
21 =12 EI
33-
Substitute in compatibility eqns., hence:-
324X1 – 33X2 = .03 EI
-33X1 – 7.67X2 =-.001 EI
Hence
X1 = 2.82t
X2 = 9.55t
Mf = 2.82 M1 + 9.55 M2
B .M . D
7.37m.t
16.92m.t
9.55m.t
16.92m.t
Example (24)
For the shown frame in
Fig.33 draw B.M.D. due to
downward settlement at B
of 3cm
EI = 12000 t.m2
Solution
6
4
12
A
C D
B
3cm
Figure (33)
220 Chapter (3) - Consistent Deformations
Choose main system as
shown in fig.29.a. The
compatibility equation is:-
10+X1. 11 = 0
To get 10 at support A due
to downward settlement of
3 cm at B apply the force
system hence;
We = wi = 0
i.e
1.10 36
1 = 0
10 = -.05cm
Hence
-0.05+X111 = 0
11 =EI
dlM 2
1
3cmX1 = 0
10
a) Main system
11X1 = 1
3cm
1t
1/6
1/6
b) Force System
6 t.m
6 t.m4 t.m
4 t.m-
--
c) M1.D.
Figure (33)
11 =
2
3
2
2
12241246
3
2
2
664
3
2
2
441
EI
= EI
33.381
= 3.2 cm
i.e
-0.50+3.2X1 =0
X1 = 0.156 t
Mf = X1.M1
Hence B.M.D as shown in fig
33.d
-
-
0.936
-
0.625
0.9360.625
d) B.M.D.
Figure (33)
Chapter (3) - Consistent Deformations 221
Example (25)
For the shown frame in Fig.34, draw B.M.D. due to:
1) A anticlockwise rotation at B of 0.003rad.
2) A horizontal slip of support at A of 2cm to right.
EI = 18000t.m2
Figure (34)
Solution
The frame is once statically indeterminate
1) B.M.D. due rotation
a- Choose main system as shown in fig.34.a then calculate the
Reactions and draw M1.D as shown in fig.30.b & c.
b- Compatibility equation:-
10 +X1 11 = 0.003
0+X111 =0.003
X1 = 11
003.0
11 = EI
dlM 2
1
=
22.
2
333.1
EI+( 2)22.
2
633
33.633.
+32
67.026667.0
Hence:-
11 = rad410164.1
X1 = 25.76t.m
Mf = 25.76M1
222 Chapter (3) - Consistent Deformations
A
C
B
a. Main system
A
B
C
1/9
1/18
1/18
1/9X1 = 1
11
b. Force system
0.33
0.330.33
0.33
1.00
--
+
+
c. M1 Diagram
8.5
-
-
8.5
8.5+
+
25.76
8.5
d. B.M.D.
Figure (34)
2) B.M.D. due to horizontal slip
Apply the force system at main system, Fig.34.f, hence:-
We = WI = 0
We =1.10 + )100
2(
9
1 = 0
10 = rad900
2
The compatibility equation is:
10 +X1. 11 = 0
X1 = 11
10
11 = rad410164.1
Chapter (3) - Consistent Deformations 223
Then:-
X1 = 410)164.1(900
2
= 19m.t
Final B.M.D = 19.0 M1
A
C
B
2 cm
2 cm
10
e) Main System
11
2 cm
1/18
1/18
X1 = 1
1/9
1/9
f) Force System
-
-
6.30
6.30
6.30
+
+
19.0
6.30
g) B.M.D.
Figure (34)
Example (26)
Draw B.M, S.F.Ds for the shown beam in Fig.35 due to
1) applied loads
2) a rotation at A of 003.0 rad
3) rise in temperature in member BC as shown t = -30oc
EI =10000t.m2
c/101 5 ,h = 0.8 m
0 = 0.003 rad
A CB
4 t/m
Figure (35)
224 Chapter (3) - Consistent Deformations
Solution
The beam is twice statically indeterminate hence choose the main system
as shown in Fig.35.a. The compatibility equations are:
10+X1. 11+X212 = 0.0003 .…….(1)
20+X1. 21+X2. 22 = 0 ……..(2)
+ve 0.003 because it is in the direction of X1. The flexibility coefficients
are:-
Figure (35)
10 =
C
B
dlMh
t
EI
dlMM 110 .
= 05.3
2618
1
EI = -0.0072 rad.
20 =
C
B
dlMh
tt
EI
dlMM .)( 2
2120
= 2
66)
8
30(103
3
2618
1 5
EI
= 00675.0216.0
= 0.02835 m
22 = EI
dlM 2
1
=
4
2
662
EI = 0.0144 m
12 = 21
= EI
dlMM 21
= 33.2
661
EI = -0.0006 m
Chapter (3) - Consistent Deformations 225
11 = EI
167
2
61
= 0.0020 rad.
Then
-.0072 +.002X1 -.0006X2 = 0.0003 …….. (1)
0.02835-.0006X1+.0144X2 = 0 …….. (2)
i. e
-3.6 +X1 - 0.3X2 = 0.15
47.25 - X1 + 24 X2 = 0
23.7X2 = -43.5
X2 = -1.83 t
X1 = 4.30 t.m
The final B.M, S.F.Ds as shown in fig.31.e and g
Mf =M0 + X1 M1+ X2 M2
Figure (35)
224 Chapter (3) - Consistent Deformations
10. TRUSSED BEAM AND TRUSSED FRAME (Composite Structures)
Figure (36)
In case of trussed beam or trussed frame the redundant (redundants) is the
force in truss (link) member, as shown in Fig.32. In the shown figure, the
beam and frame are once statically indeterminate. In case of composite
structure (frame with link members) the redundant force is the force in
links
Example (27)
For the shown trussed beam in Fig.36, draw S.F, B.M.Ds
EI = 10000t.m2, EA link = 4000t
A B
31
2 4
4t 4t
Figure (37)
Solution
Chapter (3) - Consistent Deformations 225
The beam is once statically indeterminate hence, the compatibility
equation is:
X1=0
X1 X1
4t 4t
a) main system
16m.t 16m.t
b) M . D0
10 +X1. 11 = 0
EA
dlNN
EI
dlMM 10
0110
001 EI
dlMM
)4416
3
2
2
416(
2
EI
mEI
0426.067.426
9.2 9.2
d) B.M.D
EI
dlN
EI
dlM 2
1
2
111
EAEI
24)41.1(441
2444)4
3
2(
2
44 2
EAEI
3267.170
= 0.0171+.008 = 0.0251 m
X1 = tX 7.10251.
0426.1
= -1.7 t
Hence
M = -1.7M1+M0
Figure (36) Cont.
Example (28)
226 Chapter (3) - Consistent Deformations
For the shown trussed frame Fig.34 draw B.M.D.
EI =30000 t.m2, EAlink =10000 t
Figure (36)
Solution
The frame is twice statically indeterminate. Choose the main system as
shown in Fig.36.a; hence:-
10 = EA
dlNN
EI
dlMM 2002
= )72
123(
1
EI
= -0.0042 m
20 = EA
dlNN
EI
dlMM 1001
= 0)71260(1
)67.72
660(
2
EIEI
= -0.248 m
22 = EA
dlN
EI
dlM 2
222
= )23
2
2
24262466
3
2
2
668
3
2
2
88(
1
EI
= ))241.16(5.061(1
EA
= 0.038 + 0.0014
= 0.0394 m
Chapter (3) - Consistent Deformations 227
12 = EI
dlMM 21
= )72
123(
1
EI
= 0.00126 m
Figure (36)
228 Chapter (3) - Consistent Deformations
11 = EI
dlM 2
1
= )33
2
2
36(
2
EI
= 0.0012 m
The compatibility equations are:-
10+X1. 11+X2 12 = 0 ….(1)
20+X1. 21+X2. 22 = 0 ….(2)
Substituting the values of
-0.0042 + 0.0012 X1 +0.00126 X2 = 0 ….(1)
-0.248 + 0.00126 X1 +0.0394 X2 = 0 ….(2)
Subdivide equation (1) by 0.00125 and equation (2) by 0.0394
-3.33 + 0.95 X1 + X2 = 0 ….(1)
-6.29 + 0.032 X1 + X2 = 0 ….(2)
-2.96 + 0.923 X1 = 0
Hence
X1 = -3.22 t
X2 = +6.40 t
Hence
Mf =M0 + X1 M1+ X2 M2
Nf =N0 + X1 N1+ X2 N2
Qf =Q0 + X1 Q1+ X2 Q2
Mc =-8 6.4 = -51.2 t.m
MD = -38.40 t.m
Mf = 5.50 t.m
The B.M.D. is shown in Fig.36.f
Chapter (3) - Consistent Deformations 229
Figure (36)
Example (29)
For the frame with link shown in Fig.35, draw B.M.D. due to given loads.
Calculate the relative displacement between points A and d
EI =20000 t.m2, EAlink =8000 t
Figure (37)
Solution
230 Chapter (3) - Consistent Deformations
In case of frame with link member or trussed frame or trussed beam,
generally the redundants are the forces in link members as shown in
Fig.37.
Figure (37)
sin = 10
8 = 0.80
cos = 10
6 = 0.60
The compatibility equation is
10 +X1 11 = 0
Figure (37)
Chapter (3) - Consistent Deformations 231
Figure (37)
10 = EA
dlNN
EI
dlMM 1001
= )08.13
28192(
1
EI = -0.09216 m
11 = EA
dlN
EI
dlM 2
121
= )8.43
2
2
88.48.4
3
2
2
68.4(
1
EI
EA
110
= EAEI
1052.107 = -0.00663 m
Hence
X1 = 11
10
=
00663.0
09216.0 = 13.91 t
Mfinal =M0 + X1 M1
Mc = 0 +13.90 (-4.8) = -66.768 t.m
Md = 192 +0 = 192 t.m
The B.M.D. as shown in Fig.37.e
Figure (37)
232 Chapter (3) - Consistent Deformations
11. DEFLECTION OF STATICALLY INDETERMINATE
STRUCTURES (REDUCTION THEORY)
The deflection of statically indeterminate structures may be calculated
exactly as determinate structures using virtual work method, but in this
case the calculations are very difficult because the indeterminate structure
must be solved twice, one to obtain final moments due to given loads
(Mf.D) and the second to obtain (M1.D) due to unit load at the section,
hence
y = EI
dlMM f 1
The reduction theory method reduce the solution of statically
indeterminate structure to once due to given loads (Mf.D) but the unit
load is applied at the section on the suitable main system or primary
structure chos en to obtain (M1.D), Hence
y = EI
dlmM f 1
Example (30)
Calculate the vertical deflection at n due to given loads for the shown
fixed beam in Fig.38.
EI =10000 t.m2
10t
A Bn
Figure (38)
Solution
1- Solution by traditional virtual work method (Get Mf Diagram)
10 +X1 11 = 0
X1 =11
10
10 =EI
1
2
820
=
EI
80
Chapter (3) - Consistent Deformations 233
11 =EI
81
X1 = X2 = 10 m.t
X1
10t
X2=X1
20t.m
a) M . D0
1m.t1m.t
0
b) M . D1
10mt10mt
10mt
c) B. M.D Figure (38)
To get M1 due to 1 t
Figure (38)
234 Chapter (3) - Consistent Deformations
10 +X1 11 = 0
10 = EI
dlMM 01
= )2
82(
1
EI =
EI
8
11 = EI
8
X1 = 1 m.t
Hence M1.D as shown in the Fig.36.f
1mt1mt
1mt
f) M1.D
Figure (38. f) M1.D.
yn = EI
dlMM f1
= )3
2
2
210(2
2
EI =
EI3
80
= 100003
10080
= 0.267 cm
2- Solution using reduction theory (Fig.38.h)
Choose any suitable main system (1)
y = EI
dlmM f 1
= ))10203
2(
2
42(
2
EI
Chapter (3) - Consistent Deformations 235
= EI3
80 = 0.267 cm
Figure (38)
For main system (2):-
yn = EI
dlmM f 1
= )3
4
2
4202410(
1
EI
= )3
16080(
1
EI
= EI3
80 = 0.267 cm
(the same result of main system 1)
Figure (38)
236 Chapter (3) - Consistent Deformations
Example (31)
Compute the reactions and
draw the bending moment
diagram for the frame shown
in Fig.39. due to given loads.
Find the deflection at point n
and rotation at A.
EI = 12000 t.m2
Solution
Draw M1 and M0 diagrams.
This frame is statically
indeterminate to the first
degree. Select X1 as the
redundant, then
Figure (39)
10 +X1 11 = 0
10 = EI
dlMM 01 = ))4()3(
3
2
2
848(
1
EI
= EI2
6848
= EI
1152
11 = EI
dlM 2
1
12t
A Bn
c
A B
c X1=0
10
12t
a) Primary system
Figure (39)
= )63
2
2
666
3
2
2
166(
1
EI =
EI
72192 =
EI
264
Figure (39)
Hence
EI
1152 +X1
EI
264 = 0
X1 =264
1152 = 4.36 t
Mfinal =M0 + Xc M1
48 t.m
Xc = 1t
X1=1t
11
b) M . D 0
Chapter (3) - Consistent Deformations 237
Mb = 0 + 4.36 (-6) = -26.16 t.m
Figure (39)
Reactions
XA = XB = 6
16.26 = 4.36 t.m
YA =16
1636.4812 = 4.36 t.m
YB = 7.64 t.m
Deflection at point n:-
Apply 1 ton on the main system at point n as shown in the figure
238 Chapter (3) - Consistent Deformations
Figure (39)
yn = EI
dlmM f 1
= )2
16.26
2
164(
1)48
3
2
2
84(
2
EIEI
= 12000
28.2091024 = 0.0678 m
Rotation at A:-
Apply 1 t.m at A and draw B.M.
Figure (39)
Chapter (3) - Consistent Deformations 239
A = EI
dlmM f 1
= )3
1
2
1616.26
2
1
2
1648(
1
EI
= 12000
24.122 = 0.01018 rad. Clockwise
Example (32)
Compute the force in the tie rod of the shown composite structure shown
in Fig.40. Draw B.M.D., N.F.D. Find deflection at point G
Figure (40)
E1I1 =12000 t.m2
E1A1 =10000 t
E2A2 =5000 t
Solution
The effect of normal force in link member and beam are taken into
consideration to obtain 10 and 11. The compatibility equation is:-
10 +X1 11 = 0
10
Figure (40)
240 Chapter (3) - Consistent Deformations
Figure (40)
10 = EA
dlNN
EI
dlMM 1001
= 4.2365.04.2548.436(3
64.2
3
2
2
654[
01
]363
2
2
128.4)8.4545.0
EI
= 11
6.1900
IE
= -1.584 m
11 = EA
lN
EI
dlM 2
121
= ]1110
[]6.0126.0
[]8.43
2
2
128.4[
2
221111 AEAEIE
= 5000
0.10
10000
32.4
12000
32.184
= 0.156 m t
X1 = 10.15 t
The force in the tie rod equal to 10.15 t
Chapter (3) - Consistent Deformations 241
Figure (40)
Deflection at B:-
Apply 1 t at B on the main system. Draw m1.D and n1.D is zero as shown
in Fug.38.g
Figure (40)
1 B = EA
dlnN
EI
dlmM ff 11
= 01 EI
dlmM f
= 72.12)62
36(
2
4672.12[
2
1
EI
242 Chapter (3) - Consistent Deformations
]33
2
2
664.294
2
636.42
= EI
84.17732.50872.17164.152
= 12000
8.361 = 0.030 m
= 3 cm
The elastic curve is shown
Figure (40.k) Elastic Curve
Example (33) For the shown trussed structure shown in Fig.41, draw N.F, S.F, and
B.M.Ds. Find deflection at d
Figure (41.a)
Solution The structure is once statically indeterminate. The primary structure is as
shown in the figures.
10+X1. 11 = 0
Chapter (3) - Consistent Deformations 243
10 = EA
dlNN
EI
dlMM 1001
= 2
70.477.10100(
2
7.410.98400[
01
)]7.44
3
3
77.10300
EI = -0.28407 m
Figure (41)
11 = EA
dlN
EI
dlM 2
121
= 2
7.410.987.47.4
3
2
2
77.107.4[
4.4
3
2(8
2
4.4
EI
1)]7.4
EA
1)81.177.106.087.181( 222
= 43 1026.4107.4
= 0.00513 m
X1 = 0051.0
4.2844.0
= 55.69 t (tension)
Figure (41)
Figure (41)
244 Chapter (3) - Consistent Deformations
Deflection at d:-
1d = EA
dlnN
EI
dlmM ff 11
Apply 1 t at d on main system then draw m1, n1 Ds
Figure (41)
tan = 20
8 = 0.40
sin = 54.21
8 = 0.371
cos = 54.21
20 = 0.9285
1d = 3
5.172/54.2127.38
3
5.72/54.211000[
1
x
EI
]202
8)78.10627.138(20827.138152/54.21100
+
]8134.872
2/54.21)1.3868.30(
2
2/54.2141.75928.0[
1
EA
= 80000
15.1106
100000
26.25117 = 0.2500 + 0.0138 = 0.2638 m
Compare the value of deflection from bending moment and normal force?
Chapter (3) - Consistent Deformations 245
12. ANALYSIS OF STATICALLY INDETERMINATE
TRUSSES
The indeterminancy of a truss may be due to redundant supports or
redundant members or both. If it results from redundant supports, the
procedure for attack is is the same as that described for a continuous
beam. If the redundant element is a member, the element is considered to
be cut at a section and replaced by two equal and opposite axial redundant
forces representing the internal force for that member. The condition
equation is such that the relative axial displacement between the two sides
at the cut section caused by the combined effect of the original loading
and the redundants should be zero.
Example (34)
Compute the reactions and member
forces for the given truss shown in
Fig.42.
E = 2100 t/cm2
L/A = 120 m-1
Solution The truss is indeterminate to the first
degree. Select yb as redundant. Then
Figure (42)
b0 +Xb bb = 0
or
10 +X1 11 = 0
a) Primary Structure (N0)
b) N1
Figure (42)
246 Chapter (3) - Consistent Deformations
10 = b0 =EA
dlNN 10 = )(10
EA
LNN
11 = bb =EA
dlN 2
1 = )(21
EA
LN
The following table gives the values of 10 and 11 and internal forces N
Member L/A N0 N1 N0 N1 N12 X1 N1 N
ab 120 -6 -0.375 2.25 0.14 +0.82 -5.18
bc 120 -6 -0.375 2.25 0.14 +0.82 -5.18
ad 120 +10 0.625 6.25 0.39 -1.36 8.64
dc 120 -10 0.625 -6.25 0.39 +1.36 11.36
Bd 120 0 -1.0 0 1.0 +2.18 2.18
4.50 2.06
The values of reactions
X1 = Xb =06.2
5.4 = -2.18 t
N = N0 + Xb N1
or
N = N0 + X1 N1
Example (35)
Compute the reactions of the given truss shown in Fig.43
L/EA=const.
Figure (43)
Chapter (3) - Consistent Deformations 247
Solution
The truss is indeterminate to the first degree. Select Xb as redundant.
10 +X1 11 = 0
Figure (43)
10 = )(10EA
LNN
11 = )(21
EA
LN
The following table shows the values of 10, 11. Owing to symmetry of
the load, structure and redundant, only one-half of the members need be
included in the following table:-
Member N0 N1 N0 N1 N12 X1 N1 N
a-1 -1.5 +0.75 -1.125 0.56 1.0 -0.5
a-2 0 -1.25 0 1.56 -1.67 -1.67
1-2 +2.5 -1.25 -3.125 1.56 -1.67 +0.83
1-3 -2.0 +1.0 -2.0 1.0 1.34 -0.66
2
1 (2-3)
-3.0 0 0 0 0 -3.0
2
1
-6.25 4.68
X1 =68.4
25.6 = 1.34 t
XA = XB = X1 (From 0XF )
YA = YB = 1.50 t (From symmetry)
248 Chapter (3) - Consistent Deformations
Example (36)
Compute the normal forces (N)
in the members of the given
truss shown in Fig.42.
Solution
The truss is once indeterminate.
The analysis and results are
tabulated as follow
Figure (44)
b) N1 a) N0
Figure (44)
Member L
(cm) Area
N0
tons
N1
Tons EA
LNNo 1
EA
LN 2
1
X1 N1 N
2-A 400 - -10 0 0 0 0 -10
A-B 400 2A -10 -0.71 EA
1420 EA
100 1.31 -8.69
B-4 400 - -10 0 0 0 0 -10
1-3 400 2A +10 -0.71 -EA
1420 EA
100 1.31 -11.31
2-1 566 - +14.14 0 0 0 0 14.14
A-1 400 2A -10 -0.71 EA
1420 EA
100 1.31 -8.69
B-3 400 2A -10 -0.71 EA
1420 EA
100 1.31 -8.69
4-3 566 - +14.14 0 0 0 0 14.14
1-B 566 A 0 1 0
EA
566 -1.85 -1.85
A-3 566 A 0 1 0
EA
566 -1.85 -1.85
EA
2840 EA
1532
10 +X1 11 = 0
X1 =1532
2840 = -1.85 t
N = N0 +X1 N1 as shown in the given tables.
Chapter (3) - Consistent Deformations 249
13. DEFLECTION OF INDETERMINATE TRUSSES
Figure(45)
The vertical displacement at point d for the truss shown in Fig.43 is
obtained from the following equation:-
yd = LEA
NN.
Where:
N are the normal forces in the members of the indeterminate truss due to
the given external loads and N are the normal forces in the members of
the indeterminate truss when subjected to1 ton at point d. This means that
250 Chapter (3) - Consistent Deformations
the indeterminate truss is to be solved two times; due to external loads
and the virtual load. Such procedure may be simplified as follows:-
N = 110 .NXN
and
N = 110 .NXN
Knowing that
dy = LEA
NN.
= EA
LNXNNXN ).)(.( 110110
= )( 1111
011
101
00 LEA
NNXXL
EA
NNXL
EA
NNXL
EA
NN
The term LEA
NN 10 is equal to the vertical deflection at support B due to
external loads which should equal zero.
The term LEA
NN 11 represents the vertical deflection at B due to vertical
load at B which also equal zero.
Then
dy = )( 1100 NXNL
EA
N
= LEA
NN0
Where 0N are the normal forces in the members of the choosen primary
structure due to 1 ton at d.
Example (37)
Compute the horizontal displacement at point 6 for the given truss shown
in Fig.46.
A =50 cm2, E = 2000 t/cm
2
Solution
The procedure and results are given in the following table
Chapter (3) - Consistent Deformations 251
Figure(46) Mem. L
(cm)
N0 N1
EA
LNNo 1
EA
LN 2
1
N* 0N
EA
LNN 0.
A-1 400 80 -1.33 -42560 707.6 5.71 2.67 6098.3
1-3 400 80 -1.33 -42560 707.6 5.71 2.67 6098.3
3-5 400 0 0 0 0 0 0 0
B-2 400 -180 2.67 -192240 2851.6 -30.87 -4 49392
2-4 400 -20 0 0 0 -20 -1.33 10640
4-6 400 -20 0 0 0 -20 -1.33 10640
A-B 300 0 0 0 0 0 0 0
1-2 300 -30 0 0 0 -30 0 0
3-4 300 0 -1 0 300 -55.85 0 0
5-6 300 -15 0 0 0 -15 0 0
A-2 500 125 -1.67 -104375 1394.45 31.73 1.67 52.99
2-3 500 -75 1.67 -62625 1394.45 18.28 -1.67 -30.53
3-6 500 25 0 0 0 25 1.67 41.75
4-C 600 0 1 0 600 0 0 0
EA
444360
EA
7.7955
EA
81.82932
252 Chapter (3) - Consistent Deformations
* N = No + X1 N1
X1 = 7.7955
444360 = 55.85 t
6 = LEA
NN 0. =
502000
80.82932
=0.83 cm
Example (38)
For the given truss shown in Fig.47, find the forces in members due to '
a) Given loads
b) Rise in temperature t = 20o in the upper members
EA
L =constant =0.01 cm/t
Figure (47)
Solution
This truss is once indeterminate internally. The chosen main system and
No and N1 are as shown in the given table
a) Due to given loads
10 + X1 11 = 0
X1 = 11
10
Figure (47)
From the table
Chapter (3) - Consistent Deformations 253
01NN = 14.14
21N = 4.0
11 = EA
LN
21 = 4 (0.01) = 0.04 cm
0.0002 LN1 = -0.057
Hence:-
a) Due to given loads
X1 = 4
14.14 = -3.54 t = -2.5 2
Normal force N =No + X1.N1
= No - 3.54.N1
b) Due to t = 20o for upper members
10 = dLtN ...1
= LtN ...1
= 110-520 LN .1
= 0.0002 LN .1
The following table shows the results
Due to loads Due to t
Member L N0 N1 N0 N1 N12 0.0002L 0.0002N1.L
A-2
400
0 0 0 0 - -
2-4 10 0.71 7.1 0.5 - -
4-B 0 0 0 0 - -
1-3 -10 0 0 0 0.08 0
3-5 -10 -0.71 -7.1 0.5 0.08 -0.057
5-6 -10 0 0 0 0.08 0
A-1 -10 0 0 0 - -
2-3 -10 -0.71 -7.1 0.5 - -
4-5 -10 0.71 -7.1 0.5 - -
B-6 -10 0 0 0 - -
1-2 14.14 0 0 0 - -
2-5 0 1 0 1 - -
3-4 0 1 0 1 - -
4-6 14.14 0 0 0 - -
-0.057
254 Chapter (3) - Consistent Deformations
i.e.10 = -0.057
X1 =11
10
=
04.0
057.0 = 1.41t
Hence:-
N = X1 N1
= 1.41 N1
Example (39)
For the shown truss in Fig.48, determine the forces in members due
settlement at B = 2 cm
L/EA =0.012 cm/t for all members.
Solution
Figure (48)
10 = 0.0
and
10 + X1.11 = -2.0 cm
The given truss is once statically indeterminate and since the truss is
symmetric, calculations are obtained for half the truss. The calculations
and results of 11 are shown in the following table:-
Chapter (3) - Consistent Deformations 255
Member N1 N12 N= X1.N1 (tons)
1-3 0.5 0.25 -5.95
3-5 1.0 1.0 -11.9
5-7 1.5 2.25 -17.85
a-2 0 0 0
2-4 -0.5 0.25 5.95
4-6 -1.0 1.0 11.90
a-1 0.5 0.25 -5.95
3-2 0.5 0.25 -5.95
5-4 0.5 0.25 -5.95
0.5(7-b) 0 0 0
1-2 -0.71 0.5 8.45
3-4 -0.71 0.5 8.45
5-6 -0.71 0.5 8.45
2
1
7.0
11 =7 2 0.012 =0.168 cm
= -2.0 cm
10 + X1.11 = -2
X1 = 168.0
2 = -11.9 t
N = X1.N (as shown in the table)
14. GENERAL REMARKS CONCERNING SELECTION
OF REDUNDANTS
From the previous examples, we recognize that there is considerable
latitude in selecting redundants. The only restriction being that they shall
be selected so that a stable primary structure remains. By proper selection
of the redundants, however we can minimize the numerical computations.
This objective can be achieved by adhering to the following polices.
1. Take advantage of any symmetry of the structure
2. Select the primary structure so that the effect of any of the various
loading conditions is localized as much as possible
Considerations of several alternative selections of the redundants for the
continuous truss shown in Fig.49 will illustrate the validity of these
256 Chapter (3) - Consistent Deformations
statements. This structure is indeterminate to the second degree. Any
selection of redundants will involve two equations of the following form:-
10+X1. 11+X2 12 = 0
20+X1. 21+X2. 22 = 0
Primary Structure (1)
Primary Structure (2)
Primary Structure (3)
Figure (49)
Knowing that:-
i21 = 12
10 = EA
LNN 01.
11 = EA
LN 2
1
20 = EA
LNN 02 .
21 = EA
LNN 12 .
Before these terms can be evaluated, N0, N1, N2 member forces must be
computed. If the structure is symmetrical, and if symmetric redundants
are selected, the X2 forces can be obtained from the X1 forces by
symmetry. Further 22 will be equal to 11 in such a cases, leaving only
Chapter (3) - Consistent Deformations 257
four deflection terms to be evaluated. The evaluation of these terms will
involve less computations if the redundants are selected to as to restrict
the effect of the various loading conditions to as few members as
possible. The latter will be true whether or not the structure is
symmetrical.
All the three alternative selections of the redundants show in the previous
figure take advantage of symmetry. The various loading conditions effect
the portions of the structure indicated in each case. Comparison of these
primary structures shows clearly that selection 3 is the best since it is
most effective in localizing the effects of various loading conditions. In
selection 3,if such a member is cut, only its axial force may be considered
as a redundant.
15. CHOICE OF MAIN SYSTEM IN CASE OF
SYMMETRY AND ANTISYMMETRY
1) Case of beam symmetry
The fixed beam shown in Fig.48 is three times statically indeterminate. If
one takes the symmetry into consideration, the beam becomes once
statically indeterminate; hence at center line shearing force and normal
force are zero; then:-
10+X1. 11 = 0
10 = EI
dlMM 01
11 = EI
dlM 2
1
Main System (1)
Main System (1)
Figure (50)
258 Chapter (3) - Consistent Deformations
2) Case of beam anti-symmetry
The shown fixed beam is anti-symmetry, hence bending moment at C.L.
and normal force are zero:-
10+X1. 11 = 0
10 = EI
dlMM 01
11 = EI
dlM 2
1
Main System
Figure (51)
3) Case of Frame Symmetry
Structure symmetry mean that the structure must has complete symmetry
in shape, loads, dimensions, supports and momet of ineria. The main
system in case of frame shown in Fig.49 may chosen as shown in main
system 1 or main system 2. The frame in this case is a twice statically
indeterminate not three times statically indeterminate,because the shear at
center line is equal to zero.
From symmetry, the frame has two
redundants only; X1 and X2
(Shearingforce at center line is
zero)
Figure (52)
Chapter (3) - Consistent Deformations 259
4) Case of Frame Anti-Symmetry
In case of anti-symmetry,at centerline
moment and normal force are equal to
zero. As shown in Fig.50, the frame is
once statically indeterminat (Bending
moment at center line is zero)
Figure (53)
5) Case of Closed Frame Symmetry
From symmetry, the frame is twice statically indeterminate because the
shear at centrline (cut section) is zero (Fig.51). Hence:-
10+X1. 11+X2 12 = 0
20+X1. 21+X2. 22 = 0
Figure (54)
260 Chapter (3) - Consistent Deformations
6) Case of Closed Frame Anti-Symmetry
The frame is anti-symmetry and
once staticallyindeterminate.Hence
10+X1. 11 = 0
and
Mf = M0 +X1. M1
Figure (55)
16. ANALYSIS OF STATICALLY INDETERMINATE
STRUCTURES USING CASTIGLIANO SECOND
THEOREM; THEOREM OF LEAST WORK
The previous approach to the analysis of indeterminate structures
involved writing superposition equations of the deflections of the points
of application of the redundants. Instead of doing this, however,
expressions for these deflections can be set up using Castigiliano's second
theorem.
The latter approach is actually very similar to the former. It is a somewhat
more automatic procedure, however, and is therefore preferred by some
engineers. Since Castigiliano's theorem should really limited to the
computation of the deflection produced simply by loads on the structure,
this method lacks the generality of the superposition- equation approach.
Consider the following indeterminate beam shown in Fig.53. The
deflection at point b can be evaluated by using Casigiliano's second
theorem. In this case only bending deformations are involved.
u = EI
dlM
2
2
……(1)
Chapter (3) - Consistent Deformations 261
But
bx
u
= b
But point b in the actual structure
does not deflect, b on the primary
structure must equal zero. As a
result,
bx
u
=
EI
dl
x
MM
b
= 0 ……(2)
Figure (56)
However, M, being equal to the total bending moment in the primary
structure due to all causes, may be expressed as being the superposition
of the contribution of the applied load only and the contribution of the
redundant Xb, thus
M = M0 + X1 M1 ……(3)
bx
M
= Mb
Equation (2) becomes
EI
dlMX
EI
dlMM bbb
20 = 0 ……(4)
But
b0 = EI
dlMM b0
……(5)
bb = EI
dlM b
2
From Eqn.5 it is immediately apparent that Eqn.4 is actually a statement
that:-
b0 + Xb bb = 0 ……(6)
Thus it is possible to use Castigiliano's theorem somewhat more
automatically and effectively in certain problems.
262 Chapter (3) - Consistent Deformations
If in the analysis of indeterminate structures the deflection of the point of
application of a redundant is zero, then applying Castigiliano's theorem as
in Eqn.1 reduces to the statement that the first partial derivative of the
strain energy with respect to that redundant is equal to zero. This is
equivalent to stating that the value of the redundant must be such as to
minimize the strain energy. This special case of Castigiliano's second
theorem is often called the theorem of least work and may be stated as
follows:-
"In a statically indeterminate structure, if there are no support movement
and no change of temperature, the redundants must be such as to make
the strain energy a minimum".
Castigiliano's theorem is applicable only when the deflection of the
structure is caused by loads. It is possible to solve the cases of settlement
and temperature but the procedure is often not as straight forward as that
of the superposition- equation approach.
Example (40)
Solve the following frame shown in Fig.57 using Castigiliano's theorem.
Figure (57)
Solution
This frame is indeterminate to the third degree. Cut the girder at mid-span
and select the moment, axial force, and shear as the three redundants X1,
X2, X3.
u = EA
dlN
EI
dlM
22
22
Chapter (3) - Consistent Deformations 263
3X
u
= 0
2X
u
= 0
1X
u
= 0
Figure (57)
Hence:-
A
L
X
NN
I
dL
X
MM
33
= 0 ……(1)
A
L
X
NN
I
dL
X
MM
22
= 0 ……(2)
A
L
X
NN
I
dL
X
MM
11
= 0 ……(3)
From F to C (0 < X < 2)
M = X3 – x .X2
3X
M
= 1,
2X
M
= -x,
1X
M
= 0
N = X1
3X
N
= 0,
2X
N
= 0,
1X
N
= 0
From C to B (2 < X < 6)
M = X3 – x .X2 – 10(x-2)
3X
M
= 1,
2X
M
= -x,
1X
M
= 1
N = X1
3X
N
= 0,
2X
N
= 0,
1X
N
= 1
264 Chapter (3) - Consistent Deformations
From B to A (0 < y < 6)
M = X3 – y .X1 – 6 .X2 -40
3X
M
= 1,
2X
M
= -6,
1X
M
= -y
N = -10 – X2
3X
N
= 0,
2X
N
= -1,
1X
N
= 0
From F to d (0 < x < 6)
M = X3 + x .X2
3X
M
= 1,
2X
M
= x,
1X
M
= 0
N = – X1
3X
N
= 0,
2X
N
= 0,
1X
N
= -1
From d to E (0 < y < 6)
M = X3 + 6 .X2 - y .X1
3X
M
= 1,
2X
M
= 6,
1X
M
= -y
N = X2
3X
N
= 0,
2X
N
= 1,
1X
N
= -1
Setting up Eqn.1
6
2 1
23
2
0 1
232
)1)(2010.(2
)1)(.(E
dxxXxX
E
dxXxX
Chapter (3) - Consistent Deformations 265
6
0 1
23
6
0 1
2132
)1)(.()1)(406.(I
dxXxX
E
dyXXyX
6
0 1
123 )1)(.6(I
dyXyXX = 0
We obtain 6
2
2
2
2
3
2
0
2
2
3 )202
102
.(2
1)
2.(
2
1
X
xX
xxXX
xxX
6
2
2
2
3
6
0
21
2
3 )2
.(2
1)40.6
2.(
X
xxXyyXX
yyX
6
0
2
123 )2
6.(
yXyXyX = 0
Then
X3 - 2 X1 = 0 ……..(1)
Setting up Eqn.2 and 3and solving 1, 2 and 3, we can get X1, X2, X3. The
results show that the effect of axial forces is very small and maybe
neglected.
17. TORSION OF FIXED BEAM
The fixed beam shown in Fig.55
with torsion force. The statically
indeterminate beam fixed at two
ends (6 times indeterminate) but in
case of torsion moment (t.m/m) the
solution independent on bending
moment only while (10 = 0). Hence
for torsion moments for fixed beam
is once statically indeterminate, the
primary structure (Mt0) and Mt1 due
to X1 = 1t.m/m are shown in Fig.58.
Then
10+X1. 11 = 0
X1 =11
10
Figure (58)
266 Chapter (3) - Consistent Deformations
10 = L
t
ttGI
dxMM
010 .
Mt0 = L
t dxxm0
)(
Mt1 = 1
Hence:-
10 = L x
t
t
dxdxxmGI 0 0
)).((1
= t
c
GI
XLA )(
11 = L
t
tGI
dxm
0
21 =
tGI
L
Hence
X1 = L
XLA )(
It must be noted that the X1 is equal to the reaction at this point of a
simple beam loaded with the original tm diagram as a load, the torsion
moment at end A is then.
MtA = A - X1 = A - L
XLA )( =
L
Axc
The final torsion moment diagram is then similar to the S.F.D. of a simple
beam.
Example (41)
Draw T.M.D. for the shown
fixed beam in Fig.56
Solution
Figure (59)
MtA = 6
5.12)75.4)(5.24(
= 7.42 t.m
MtB =0.58 t.m
Chapter (3) - Consistent Deformations 267
The S.F.D. for simple beam which is the T.M.D.
Figure (59)
268 Chapter (3) - Consistent Deformations
PROBLEMS
1. Draw the S.F. and B.M.Ds for the following structures due to
a) Given loads
b) Settlement and temperature changes as goven
c) Calculate the deflection at n.
a) B = 2 cm
EI =10000 t.m2 4 t/m
5t
nA
Bc
b) Kb = 200 t/m
EI =12000 t.m2 3t 3t
A B c
springsupport
c) t = 20o
h = 120 cm
E =210 t/cm2
B = 3 cm
A = 0.003 rad
4 t/mA B
n
d) B = 1 cm
EI =8000 t.m2
A = 0.002 rad
e) t = 30o
h = 0.8 m
EI =8000 t.m2
f) I =32000 cm
4
E =2000 t/cm2
K = 6 t/cm
t = 20o
h = 0.5 m
Chapter (3) - Consistent Deformations 269
g) A = 0.004 rad
C = 0.002 rad
EI = 9000 t.m2 B
A C
3t/m
I
8t
2I In
h) EI =10000 t.m
2
K = 3 t/cm
i) A = 0.001 rad
EI = 6000 t.m2
B = 3 cm
12t.m
n
0 5t
A B
3I I
A
j) B = 2 cm
A = 0.01 rad
EI =14000 t.m2
0A
A B
A
2. For the following frames
a) Find the reactions and draw B.M, S.F. and N.F.Ds.
b) Compute the vertical deflection at point n and horizontal displacement
at m and B
a) EIframe =10000 t.m2
EAtie =10000 t
270 Chapter (3) - Consistent Deformations
b) EIframe=20000 t.m2
EAtie =30000 t
3t
tie
A B
3t
3t
3t
c) EI =10000 t.m
2
3t/m
A B
I
m
4I
4t/m
d) EI =16000 t.m
2
EA =8000 t
GAr = 4000 t
Uniform rise in temp
t = 20o
E = 200 t/cm2
h = 100 cm
e) Find the
deflection at
springs D & E
EI =12000 t.m2
KD = 400 t/m
KE = 350 t/m
Chapter (3) - Consistent Deformations 271
3) Find the reaction and Draw B.M.d., S.F.D., N.F.D. for the following
frames: due to:
1. Given loads
2. Vertical downward settlement at B of 2 cm.
3. Rise in temp. t = 200 in CD
4. Rotation of 0.003 rad at fixed support A
a) EI =
30000t.m2
b) EI = 20000 t.m2
EA = 10000 t
c)
272 Chapter (3) - Consistent Deformations
d)
4. Find the reactions and Draw B.M.D., S.F.D., N.F.D. for the following
frames.
a) EI = 30000 t.m2
EA = 10000 t (For link members)
2t/m2t/m
b) EI =16000 t.m2
Chapter (3) - Consistent Deformations 273
c) EI = 40000 t.m2
EA = 10000 t (For links)
2t/m
I
2I 2I
d)
2t/m
10t
AB C
e) EI = 10000 t.m2
EAlink = 4000 t
274 Chapter (3) - Consistent Deformations
f) EI = 20000 t.m2
5. Draw B.M.D., S.F.D., N.F.D. for the following frames due to:
a. Given load
b. Rotation at A of 0.003 rad.
a) EI = 8000 t.m2
A
B
m
10t
6t
b) EI = 40000 t.m2
EA = 10000 t
c) For girder EI = 3000 t.m2
For links A = 20 cm2, E = 2100 t/cm
2
Chapter (3) - Consistent Deformations 275
d) Rise in temp.
At external
fibers t1 = 200
and at internal
fiber t2 = 100
4 t/m
4 t/m
3I I2I
E=200t/cm2
3I3I
6. Draw B.M.D., S.F.D., N.F.D. for the following frames:
a) EI = 20000 t.m2
EAlink = 10000 t
10t
5t
A B
10t
5t
EI=20000 t.m
EA=10000 tLinse
b) Vertical settlement at A of 2 cm, rotation at B of 0.001 rad. clockwise,
horizontal displacement at c of 3 cm to left
EI = 16000 t.m2
c) Due to rise of
temperature t= 20o of
the outer side. and
rotation at B of 0.001
rad. Clockwise
276 Chapter (3) - Consistent Deformations
7- Analyze each of the following trusses due to
1. Given loads
2. Rise of temperature t = 40o at top chord.
3. Settlement at B = 2 cm .
E = 20 x 107 t.m
2,
A
L = 10
-1
a)
A
1
2 4 B 6 8 10 12 14 16
19171513119753
20t
C
b) 1 3 5 7 9
BA2 4 6
15t
c) 5t 5t10t 10t
B
1 3 7
CA2 4 6
5
45°
d) 4t 8t
AB
C
4t8t 8t
Chapter (3) - Consistent Deformations 277
8. Analyze each of the following trusses due to given loads and rise of
temperature t = 30o at top chord and due to settlement as shown.
A
L is assumed constant, E = 21 x 10
7 t.m
2,
A
L = 10
-1
a)
A
1
2 4 B 6 8 10 12 14
19171513119753
30t
CD
b)
A B
1 973 5
10t
2 4 6
c) 10t 10t
31 5 9
2 4
B
6
C
45°
d)
278 Chapter (3) - Consistent Deformations
e)
f)
A
1
2 4
B
6
973 7
10t 10t
g)
h)
5 INFLUENCE LINES OF
STATICALLY INDETERMINATE
BEAMS AND FRAMES
1. INTRODUCTION
An influence Line for a certain function such as reaction, moment, shear,
normal forces, or deflection; is line or curve the ordinate of which, at any
point gives the value of the function when a unit load is placed at that
point.
For example Fig.1 shows the influence lines for the reaction at supports A
& B shear at n in a continuous beam. The ordinate Y in that influence line
at point n is equal to the value of the reactions at A & B when a unit load
is placed at n.
Figure (1)
To construct the influence line for any function one method is to place the
unit load at several positions along the structure, and compute the value Y
of the function for each position of the unit load, and line joining these
ordinates Y is the required influence line.
Chapter (5) - I.L.of Indeterminate Beams and Frames 279
Because this method is time consumed time, then the most general
method for constructing influence lines is presented by Muller Breslau’s
principle method. This method is based on Maxwell’s reciprocal theorem
and Betti’s low of deflection.
It must be noted that, the influence lines for reactions and internal forces
of statically determinate structures are straight lines which are calculated
from the equilibrium conditions or by virtual work method. For statically
indeterminate structures the influence lines are generally curves. Which
are determined from the equilibrium conditions and deformation
conditions.
The influence lines can be obtained also experimentally by using a model
of beam made of any suitable material as steel. The influence lines be
identical in shape as deflected structures.
2- INFLUENCE LINES FOR DETERMINATE BEAMS BY
MULLER-BRESLAU PRINCIPLE
By the principle of Muller-Breslau very simple method for constructing
the influence lines for beams. It can be stated as follows;
1- To obtain an influence Line for the reaction of any statically
determinate beam, remove the support and make a positive
unit displacement of its point of application. The deflected
beam is the influence line for the reaction. Fig.2.a.
2- To obtain an influence line for the shear at a section of any
statically determinate beam, cut the section and induce a unit
relative transverse sliding displacement between the portion to the
left of the section and the portion to the right of the section keeping
all other constrains (both external and internal) intact. The
deflected beam is the influence line for the shear at the section,
Fig.2.b.
3- To obtain the influence line for the moment at a section of any
statically determinate beam, cut the section and induce a unit
rotation between the portion to the left of the section and the
portion to the right of the section keeping all other constrains (both
external and internal) intact. The deflected beam is the influence
line for the moment at the section, Fig.2.c.
280 Chapter (5) - I.L.of Indeterminate Beams and Frames
The proof of Muller-Breslau principle can be establish using virtual work
method the procedure of proof is generally applicable to more
complicated beams. Fig.2 shows a simple beam subjected to a unit
moving load. To find the reaction at A by the method of virtual work, we
remove the constrain at A, substitute YA for it, and let A travel a small
virtual displacement A along YA. We then have a deflected beam A- B,
as shown in fig.2, 2.a, where (Y) indicates the transverse displacement at
the point of unit load. Applying the virtual-work equation, we obtain
Figure (2)
YA. A - 1 (y) =0
i.e. YA = A
y
If we put A = 1
Then YA = y
Since y is, on the one hand, the ordinate of the deflected beam at the point
where the unit load stands and is, on the other mean at the point where the
unit load stands and is, on the other hand, the value of function YA due to
the unit moving load (i.e., the influence ordinate at the point), we
Chapter (5) - I.L.of Indeterminate Beams and Frames 281
conclude that the deflected bean A- B of Fig.2.a is the influence line for
YA if A is set to be unity.
To determine the shearing force at any beam cross section S, we cut the
beam at S and let the two parts AS and SB have a relative virtual
transverse displacement S at S without causing relative rotation between
the two parts. This is equivalent to rotating AS1 and BS2 the same small
angle about A and B respectively. Applying the virtual work equation, we
obtain:-
QS (S)-1 (y) = 0
i.e. QS = S
y
If we put S = 1
Then Q S = y
This proves that the deflected beam AS1, S2B of Fig.2.b is the influence
line for QS. It should be pointed out that the virtual displacement is
supposed to be vanishing small and that, when we say S =1, we do not
mean that S = 1 meter. Or cm., but one unit of very small distance for
which the expressions.
SS1 = L
a
SS2 =L
b
Shown in Fig.2.b are justified.
To determine the moment at any beam cross section S by the method of
virtual work, we cut the beam at S and induce a relative virtual rotation
between the two parts AS and SB at S without producing relative
transverse sliding between the two. Thus by virtual work;
(MS) () – (1) (y ) = 0
i.e. MS =
y
If we put = 1 rad.
MS = y
282 Chapter (5) - I.L.of Indeterminate Beams and Frames
This prove give that; the deflected beam ASB at Fig.2.c is the influence
line for MS. Note that when we say S = 1, we do not mean that S =1
radian. One unit of S may be small as 100
1radian, for which it is
justified to write
AA- = a. S = a. units
BB- = b. S =b. units, as indicated in Fig.2.c
Example (1)
Figure (3) shows a simple beam with an overhang. Construct the I.L. for
YA , YB, (QA)L, (QA)L, (QA)r, QS, MS and MA by the virtual work method.
Figure (3)
Solution:
To construct the I.L. for YA, we remove the support at A and let it move a
unit distance upward. The deflected beam C- A
- B, shown in Fig.3.a is the
influence line of YA. The I.L. for YB is obtained in a similar manner, as
shown in Fig.3.a.
To construct the influence line for (QA)r, we cut the section just to the
right of A and let the two parts of the beams have a unit relative
transverse displacement without producing relative rotation. To do this,
end A of Ac cannot move because of the presence of the support at A,
however, it is allowed to rotate about the hinge at A. we therefore, first
raise the end A of AB a unit distance to A-
and then turn AC to AC-
parallel to A-B The deflected beam so arrived at, as shown in Fig.3.b by
C--A A
--B, is the I.L. (QA)r.
To draw the I.L. for (QA)L, we cut the section just to the left of A and let
the left part have a unit relative displacement with respect to the right part
at
Chapter (5) - I.L.of Indeterminate Beams and Frames 283
Figure (3)
284 Chapter (5) - I.L.of Indeterminate Beams and Frames
The cut point without causing relative rotation between the two. Since the
part to the right of the cut section is a simple beam; it remains stable and
rigid. Only the left part can go down a unit distance. Thus, the influence
line for (QA)L is C- A
- A C Fig.3.c.
To construct the I.L. QS, we cut the beam at S and let the two parts SA
and SB have a relative transverse displacement equal to unity the two are
kept parallel to each other so that no relative rotation is introduced. Then
the deflected beam C- S1 S2 B of Fig.3.e is the I.L. QS the slope of the
deflected beam is 6
1, with which the influence ordinates can easily be
calculated.
The influence line for MS, as shown in Fig.3.f by the deflected beam C- S
-
B. it results from cutting the beam at S and letting SC and SB have a unit
rotation at S without allowing relative translation between the two. We
find the rotation of part SB about support B is 3
1 and the rotation of part
CS about A is 3
2.
Similarly, the I.L. MA, as shown in Fig.3.g by C-
AB by cutting the
section just to left of A and putting the left part have a unit relative
rotation with respect to the right part of the beam at A.
Chapter (5) - I.L.of Indeterminate Beams and Frames 285
Example (2)
Draw influence lines for YA, Q S , MS , Qn, for a compound beam shown in
Fig.4.
Figure (4)
Figure (4)
286 Chapter (5) - I.L.of Indeterminate Beams and Frames
Solution
To construct the I.L. for YA, we remove support A and move end A up a
unit distance. The deflected beam A- C B shown in Fig.4.a is the I.L. Note
that the part CB is a cantilever and will remain un-removed.
To construct the I.L. for QS, we cut the beam through S and let the left
part of beam have a relative transverse displacement equal to unity w.r.t.
the right portion of beam at S without causing relative rotation between
the two. The deflected beam AS1, S2 CB shown in Fig.4.b is the I.L.QS.
To construct the I.L. MS, we cut the beam through S and let the left part
of beam rotate a unit angle with respect to w.r.t. the right portion at S. the
deflected beam AS CB of Fig.4.c is the I.L. for MS.
The I.L. Qn is shown in Fig. 4.d by AC- n
- n B, which results from cutting
the beam through n and moving the left part of beam down a unit distance
w.r.t. right part of beam at n, while keeping the deflected protein c- ,n
-
parallel to B n.
The I.L. Mn is shown Fig.4.e by A C- n B, which results from cutting the
beam through n and rotating the left protein of beam a unit angle w.r.t. the
right part of beam at n. point n is kept fixed in the original position.
3. MULLER-BRESLAU’S PRINCIPLE FOR INDETERMINATE
STRUCTURES:
Muller-Breslau principle`s states that “for a beam, the influence line for
reaction, shear, or moment is the same as deformed shape of the beam
when that beam is loaded by the reaction, shear, or moment respectively,
but after removed; the capacity of the beam to resist the applied force, so
the beam can deformed when the force is applied. For statically
indeterminate beams, the influence lines for reactions, shear, and moment
are generally curves.
3.1. I.L. For Reactions:
This method is considered an easy for construct the influence lines. If its
required to draw the influence line for YA (as shown in Fig.5.e), then the
support at A must be removed and YA is applied with a unit value. The
elastic line shown in Fig.6.a with ordinate AA at as shown in Fig.6.a
divided by AA in order to that the deflection at A becomes equal to
unity
Chapter (5) - I.L.of Indeterminate Beams and Frames 287
Figure (5)
and the figure become the influence line of YA. If applying the
Maxwell’s reciprocal theorem (as previous example) then; (we=0).
YA. AA + 1. 1n = 0 …..(1)
Then
YA= AA
n1
…..(2)
If AA = 1.0, YA = - n1
The above equation proves that the ordinate of the elastic line of Fig.6.b
at point n means that this elastic line is the influence line for YA.
3.2. Sign convention of reaction
In general an ordinate of the influence line is positive when elastic line is
deflected upwards and vice versa. A positive reaction means a reaction in
the chosen assumed direction.
288 Chapter (5) - I.L.of Indeterminate Beams and Frames
3.3. Influence Lines For Shear at m
By Muller-Breslau’s principle the beam is assumed cut at m as shown in
Fig.6 and by positive unit shear force at m, with equal slope on each side
of m, the deflected curve represents to I.L. of Qm. Using the force
method and Maxwell’s theorem of reciprocal displacement, however, it
can be shown that: (we=0).
Qm. mm + 1. n1 = 0
i.e. Qm = n1 mm
1 , if m 1, then : Qm = n1
Figure (6)
3.3. Influence Lines For Bending Moment
Muller-Breslau’s principle can be used to construct the influence line for
bending moment. For example it is required to draw the influence line
for bending moment at support B for the given continuous beam shown in
Fig.8. two moments MB are applied at left and right of point B. after
introducing of hinge at B as shown in Fig.7.a.
The continuous beam is analyzed to find the value of MB which produces
a unit rotation at B, B=1 rad. The corresponding elastic line is the
influence line for MB.
Mb. bb + 1.Yn = 0
Mb = - bb
1
. Yn
Mb = -Yn , i.e. the elastic curve is I.L.MB
Chapter (5) - I.L.of Indeterminate Beams and Frames 289
Figure (7)
Example (3)
For the given beam shown in Fig.8. It is required to draw the influence
lines of YB, YA, MB, Mn and Qn .
Figure (8)
Solution
1- I.L YB:-
Remove the support at B and apply by a load YB = 1t , draw the elastic
line for this case. The ordinates of elastic line shown in Fig.8.e are
determined by using the conjugate beam method. The ordinates of elastic
line can be obtained as follow; (using conjugate beam method), (EI=1).
1 = (-6.4 1 + 2
16.0
3
1) = -6.3 (upward)
2 = (- 6.4 2 + 3
2
2
22.1
) = -12 (upward)
3 = (- 6.4 3 + 3
3
2
38.1
) = -16.5 (upward)
b = (- 6.5 4 + 3
4
2
44.2
) = -19.2 (upward)
4 = (- 5.6 5 + 3
5
2
52
) = -19.67 (upward)
290 Chapter (5) - I.L.of Indeterminate Beams and Frames
5 = (-5.6 4 + 3
4
2
46.1
) = -18.13 (upward)
6 = (- 5.6 3 + 3
3
2
32.1
) = -15 (upward)
7 = (-5.6 2 + 3
2
2
28.0
) = -10.67 (upward)
8 = (-5.6 1 + 3
1
2
14.0
) = -5.53 (upward)
9 = ( 5.6 1) = 5.6 (downward)
d = (5.6 2) = 11.2 (downward)
By dividing the ordinate of elastic line by ( b = 19.2) to obtain the
ordinate of influence line for (YB) as shown in Fig.9.e.
2- I.L. YA :-
YA = YAo + x1. YA1
The determination of the influence line of (YA) can be obtain by knowing
I.L. of YB . It is known that from consistent deformation method:
YA = YAo + (YB) YA1 [or YA = Yo + X1 Y1]
Where:
(YAo) is I.L of reaction of (A) on the main system and (YA1) is value of
reaction at (A) due to YB = 1t at (B) and using the superposition of two
diagrams hence;
I.L. YA = I.L. YAo – 0.6 I.L.YB
3- I.L. MB :-
I.L. MB = I.L. Mb0 + MB1 I.L. YB ( YB = X1)
= I.L. Mb0 – 2.4 I.L.X1
as shown in Fig.9.h and Fig.8.i.
4- I.L. Mn :-
I.L. Mn = I.L Mno + Mn1 I.L.YB
= I.L. Mno – 1.6 I.L. YB
as shown in Fig.8.k and Fig.8.l.
5- I.L. Qn :-
I.L Qn = I.L. Qno + Qn1 I.L. YB
= I.L. Qno + 0.4 I.L . YB
Chapter (5) - I.L.of Indeterminate Beams and Frames 291
as shown in Fig.8.m and Fig.8.n.
Figure 1
Figure (8)
292 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (8)
Chapter (5) - I.L.of Indeterminate Beams and Frames 293
Example (4)
For the shown beam in Fig.9 required :-
a) I.L. Ya
b) I.L. Mb
c) I.L. Yd.
Figure (9)
Solution (1)
1- I.L. YA :- (Fig.9.a) 1. 111 X , )( 1 AYX
11 = (EI
M21 )dl = 1
1152
3
29)12(111
2
X
EIEI
1152
1X1
1)1152(1152
1a (upward)
7.03
3
2
3331201152
1152
11
(upward)
406.03
6
2
6661201152
1152
12
(upward)
.168 03
9
2
9991201152
1152
13
(upward)
08.03
9
2
99929
1152
14
(downward)
093.03
6
2
66629
1152
15
(downward)
058.03
3
2
33324
1152
16
(downward)
06.03241152
1
c (upward)
294 Chapter (5) - I.L.of Indeterminate Beams and Frames
I.L. YA as shown in Fig.9.a.
Figure (9)
2- I.L. Mb:- (Fig.9.b)
I.L. Mb = I.L. Mbo + Mb1 I.L. YA (X1 = YA)
= I.L. Mbo + 12 I.L. YA
Figure (9)
Chapter (5) - I.L.of Indeterminate Beams and Frames 295
3- I.L. YD as determinate structure
Figure (9)
Solution (2)
Another Main system, Fig.10.a
1- I.L. Mb:-
EI
82
3
12112
11
6.03
3
2
35.032125.0
1
(upward)
125.13
6
2
65.062125.0
2
(upward)
984.03
9
2
975.092125.0
3
(upward)
75.0)32(125.0 e
(downward)
I.L. Mb as shown in Fig.10.b.
296 Chapter (5) - I.L.of Indeterminate Beams and Frames
2- I.L. YA:- I.L. YA = I.L. YAo + YA1 I.L. x 1 (X1 = MB)
= I.L. YAo + (-1/12) I.L x 1 , as shown in Fig.10.e.
2- I.L. YD as determinate beam, Fig.10.d
Figure (10)
Figure (10)
Chapter (5) - I.L.of Indeterminate Beams and Frames 297
Example (5):
For the shown continuous beam in Fig.11, Construct the I.L. for Mn and
Qn
Figure (11)
Solution:
1- Choose the main system as shown in Fig.11.a. with the
reaction at C and moment at A as redundant. Draw M1,
M2.Ds
2- Draw the elastic curve due to unit displacement at C
EI
5128
3
168
3
8 22
11 = EI
dLM 2
1
EI
33.21
2
18
3
1612
EI
33.51
3
16 2
22
The compatibility equations at c are:-
1212111
XX
0222121
XX
EI X X 21
33.21512
033533.2121 X .X
Solve to get EI
X67.426
1 ,
EIX
67.1062
Assume EI = 426.67
X 11 , X 4
2
MXMXM21F 21
Additional moment = 426.67
298 Chapter (5) - I.L.of Indeterminate Beams and Frames
0562.03
4
2
42
3
42
2
41243
67.426
11
150.03
8
2
84
3
82
2
82482
67.426
12
1687.03
12
2
126
3
122
2
1236121
67.426
13
425.067.4263
4
2
44464
67.426
14
00.167.426
67.426
C
The I.L.Yc is shown in Fig.11.b.
Figure (11)
Chapter (5) - I.L.of Indeterminate Beams and Frames 299
Figure (11)
3- Draw the elastic curve due to unit rotation at C
212111 XX = 0
222121 XX = 1.0
EI X X 21
33.21512
033533.2121 X .X
Solve to get EI
X67.106
1 ,
EIX
44.42
Assume EI = 106.67
X 11 , X 025.24
2
MXMXM21F 21
Additional shear at (A) = 106.67
4.243
2
2
462418
3
4
2
42467.106
67.106
11
4.283
2
2
8124812
3
8
2
84867.106
67.106
12
2.182
121861264
2
1261267.106
67.106
13
300 Chapter (5) - I.L.of Indeterminate Beams and Frames
30.03
4
2
44467.106
67.106
14
I.L.MA is shown in Fig.11.c.
Figure (11)
I.L.Mn= I.L.Mno + 4 I.L.YC – 0.50 I.L.MA
I.L.Mn as shown in Fig.11.d.
4. I.L. Qn:-
I.L.Qn= I.L.Qno + 0.50 I.L.YC – 16
1 I.L.MA
I.L.Qn as shown in Fig.11.e.
Chapter (5) - I.L.of Indeterminate Beams and Frames 301
Figure (11)
302 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (11)
Example (6)
For the shown Continuous beam in Fig.12, it is required to draw the
influence lines for Ya , Yb , Ma & Mc
Figure (12)
Solution First we choose a main system by introducing hinges at supports B, C, D.
From M1 , M2 & M3 Diagrams Find δ11 ,δ22 ,δ33 ,δ12=δ21 ,δ23=δ32 &
δ13=δ31, hence;
δ11= δ22 = δ33 =1*1*10/3 *2 = 6.6666667
δ12=δ21=δ23=δ32=1*1*10/6 = 1.6666667
δ13=δ31=0.0
For I.L. X1 (Mb)
Δ1=1,Δ2=Δ3=0
6.6667 X1 + 1.6667 X2 = 1
1.6667 X1 + 6.6667 X2 +1.6667 X3 = 0
1.6667 X2 + 6.6667 X3 = 0
Chapter (5) - I.L.of Indeterminate Beams and Frames 303
solving we get
X1 =0.1607 , X2=-0.043 , X3 = 0.0107
Figure (12)
M1. D.
M2. D.
M3. D.
Mb. D.
304 Chapter (5) - I.L.of Indeterminate Beams and Frames
From the chosen main system each span is considered a simple beam
having one or two concentrated moments at its to ends then the conjugate
beam is solved to get the deflections as follows:-
Beam A-B
0.000
0.628
1.0040.879
0.000
0 2.5 5 7.5 10
Figure (12)
Beam B-C
station X Mrord mlord Y Theta
start 0.0000 0.0000 -0.1607 0.0000 -0.4643
1 2.5000 0.0107 -0.1205 0.7115 -0.1261
2 5.0000 0.0214 -0.0804 0.7366 0.0848
3 7.5000 0.0321 -0.0402 0.3934 0.1685
end 10.0000 0.0429 0.0000 0.0000 0.1250
0.711 0.737 0.393
0.0000 2.5000 5.0000 7.5000 10.0000
Beam C-D
station X mrord mlord Y Theta
start 0.0000 0.0000 0.0429 0.0000 0.1250
1 2.5000 -0.0027 0.0321 -0.1925 0.0346
2 5.0000 -0.0054 0.0214 -0.2009 -0.0223
3 7.5000 -0.0080 0.0107 -0.1088 -0.0458
end 10.0000 -0.0107 0.0000 0.0000 -0.0357
station X Mrord mlord Y Theta
start 0.0000 0.0000 0.0000 0.0000 -0.2679
1 2.5000 -0.0402 0.0000 0.6278 -0.2176
2 5.0000 -0.0804 0.0000 1.0045 -0.0670
3 7.5000 -0.1205 0.0000 0.8789 0.1842
end 10.0000 -0.1607 0.0000 0.0000 0.5357
Chapter (5) - I.L.of Indeterminate Beams and Frames 305
-0.193 -0.201-0.109
0.0000 2.5000 5.0000 7.5000 10.0000
Beam D-E
station X mrord mlord Y Theta
start 0.0000 0.0000 -0.0107 0.0000 -0.0357
1 2.5000 0.0000 -0.0080 0.0586 -0.0123
2 5.0000 0.0000 -0.0054 0.0669 0.0045
3 7.5000 0.0000 -0.0027 0.0418 0.0145
end 10.0000 0.0000 0.0000 0.0000 0.0179
0.059 0.067 0.042
0.0000 2.5000 5.0000 7.5000 10.0000
Figure (12)
For I.L. X2 (Mc) :-
1=0, 2=1, 3=0
6.6667 X1 + 1.6667 X2 = 0
1.6667 X1 + 6.6667 X2 +1.6667 X3 = 1
1.6667 X2 + 6.6667 X3 = 0
solving we get
X1 =X3 =-0.0429 , X2 =.1714
306 Chapter (5) - I.L.of Indeterminate Beams and Frames
Applying the same procedure we can draw Mc as shown
Figure (12)
For I.L. X1 (Md)
1=0, 2=0, 3=1
6.6667 X1 + 1.6667 X2 = 0
1.6667 X1 + 6.6667 X2 +1.6667 X3 = 0
Figure (12)
b) MC. D.
d)
c)
Chapter (5) - I.L.of Indeterminate Beams and Frames 307
1.6667 X2 + 6.6667 X3 = 1
solving we get X3=0.1607 , X2=-0.043 , X1= 0.0107
It is obviously clear that Md is the same as Mb but mirrored about point c
After constructing the three redundant Influence lines we can now
proceed to find any required function as follows
For I.L. Ya
Figure (12)
Ya1=-0.1 & Ya2=Ya3= 0.0
So
For I.L. Yb, Yb1=0.2 , Yb2= -0.1 & Yb3= 0.0
Figure (12)
e)
f)
308 Chapter (5) - I.L.of Indeterminate Beams and Frames
4. INFLUENCE LINE OF TRUSSED BEAM
It is required to draw the influence line for the normal force X in member
44`, the displacement condition to be satisfied in this case is nn =1
where nn is the relative displacement at point n. The elastic line due to
the force X after cutting the member 44 at center line is the influence line
for X. The elastic line may be straight portions in case of panel floor and
indirect loading.
It is required to draw the influence line for internal forces (Mm and Qm) at
section m in girder AB as shown in Fig.13.
Figure (13)
From virtual work method generally, M = Mo + X1. M1 then;
I.L. Mm = I.L. MO + L.L. X1. M1
Similary;
Qm = Qo + X1. Q1
Hence;
I.L. Qm = I.L. Qo + I.L. X1. Q1
Also
Nm = X1
Chapter (5) - I.L.of Indeterminate Beams and Frames 309
i.e. L.L. Nm = I.L. X1
Example (7)
For the given Trussed Beam shown in Fig.14, calculate
a) I.L. Nn
b) I.L. Qm
c) I.L. Mm
Figure (14)
Where
E= 2100 t/cm2, Alink= 30 Cm
2, I girder= 200000cm
4
Abeam = 60 cm2.
Solution
EI = 2100 200000 104 = 42000 t.m
2.
EAlink = 2100 30 = 63000 t.
EAbeam = 2100 60 = 126000t.
LEA
N
EA
NdL
EI
M
LinksBeam
21
21
21
11
011587.05.26)6464(3
5
3
)5(42 222
221
dL
EI
M
422
1 10984.1126000
25)1(
dLEA
N
Beam
To get LEA
N
Links
21 for links, as given in the following table :-
310 Chapter (5) - I.L.of Indeterminate Beams and Frames
Member L/EA N1 21N
EA
LN21
A-3`, B- 3`
410016.163000
4.6 1.282 1.6435 1.67 10
-4
3`- 4` 5105978.863000
385.5 1.077 1.16 10 10
-5
4` – 5` 510863000
5 1 1 8 10
-5
1` – 3` 51035.663000
4 - 0.4 0.16 1.016 10
-5
2` - 4` 510524.963000
6 - 0.4 0.16 1-524 10
-5
6.6 10-4
421 106.6 L
EA
N
link
012445.0106.610 1.984 0.011587 4 -4
11
1111 X
X1 = 80.351
235.03
5.2
2
5.225.250
42000
351.802
(downward)
446.03
5
2
54550
42000
351.803
(downward)
6118.03
5.2
2
5.2125.15.24167.4
2
545.750
42000
351.804
(downward)
717.03
5
2
525.25467.6
2
541050
42000
351.805
(downward)
753.025.165.2167.42
52554167.9
2
545.1250
42000
351.806
(downward)
24.05.25042000
351.801 (upward)
Chapter (5) - I.L.of Indeterminate Beams and Frames 311
48.055042000
351.800 (upward)
a) I.L Nm = I.L. X1
b) I.L Qm = I.L. Qmo + Q1 I.L. x 1
= I.L. Qmo + 0.4 I.L. x 1
c) I.L. Mm = I.L. Mmo + Mm1 I.L. x 1
= I.L. Mmo + 5 I.L x 1
Influence Lines are shown in Figs.12.a, 12.b & 12.c
Figure (14)
312 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (14)
Example (8)
Figure (15)
For the given trussed Beam (Fig.15), determine:
1- I.L. F1.3 (I.L. Nn)
2- I.L. M4
3- I.L. Q4 right.
(EI beam = 40000 t.m2, EA link = 3000t, EA girder = 20000t)
Chapter (5) - I.L.of Indeterminate Beams and Frames 313
Solution
1- I.L. X1= I.L. Nn (Fig.15.a)
a) Cut member (1-3) and apply by X1 = 1t, then draw M1. D and get N1
for truss members as shown in Fig.15.a to d.
Hence:-
LdLdLEI
M
LinkEA
N
EA
N
21
Beam
21
21
11
Where: 11 is the relative displacement at cut point get the summation of
EA
LN 2
1 and determine the value of EA
dLa
EI
dLM 2
121 N nd , then get 11
3221 1025.23)3(
3
633
40000
2
dL
EI
M
422
1 1092000
18(1)
dL
EI
N
The values of Llinks
21
EA
N are given in the following table :-
Member L/EA F1 2
1F EA
LF 21
1-3
2 10-3
1 1 2 10-3
1-2 1 10 –3
- 0.5 0.25 0.25 10-3
3-4 1 10-3
- 0.5 0.25 0.25 10-3
1-4 2.236 10-3
1.12 1.2544 2.8 10-3
3-b 2.236 10-3
1.12 1.2544 2.8 10-3
8.103 10-3
linksEA
LN 21 = 8.103 10
-3
01125.010103.81091025.2 343
11
apply Muller- Breslau’s condition at point n, hence:-
314 Chapter (5) - I.L.of Indeterminate Beams and Frames
1111 X
X1 = 88.88
Calculate the deflection by using elastic load, Fig.15.e.
115.03
3
2
35.1 318
40000
88.881
(up word)
2.03
6
2
63 618
40000
88.882
(up word)
23.05.13352
63 918
40000
88.883
(up word)
Then, I.L.Nn = I.L.X1 , as shown in Fig.13.f.
I.L. M4 = I.L. M4o + (M4)1 I.L.X1
2- I.L. M4 = I.L. (M4)0 – 3 I.L.X1
3- I.L. Q4 night = I.L Q4o Q1 + I.L.X1
= I.L. Q4o + I.L.X1
I.L. of M4 and I.L. of Q4 are shown in Fig.15.h and k
Figure (15)
Chapter (5) - I.L.of Indeterminate Beams and Frames 315
Figure (15)
316 Chapter (5) - I.L.of Indeterminate Beams and Frames
Example(9)
For the given arched truss structure which shown in Fig.16. If the load is
transmitted to the horizontal membrs as shown in Fig.16.a.
Figure (16)
Required:
1- I.L. Mn , I.L. Nn , I.L.Qn.
2- I.L. Mm , I.L. Qm , I.L. Nm.
Where:
For arch: EI= 50000 t.m2
EA= 100000 t
For tie: EA= 60000 t
Solution
The given structure is statically indeterminate to the first degree. A
possible main system may be obtained by cutting the tie (ab) at any
section along its length, and the redundant (X1) is then the force in the tie
Fig.16.a.
Cas 1 = 0.8412
Sin 1 = 0.540757
Cos 2 = 0.94174
Sin 2 = 0.33633 , the length of members as shown in Fig.16.a.
Draw the normal force and bending moment diagrams for arch and also
normal force for ties.
Get the value of 11 by using consistence deformation
Where:
LEA
N dL
EA
N dL
EI
M
Link
2
1
Beam
2
1
2
1
11
Chapter (5) - I.L.of Indeterminate Beams and Frames 317
0.0201999.035 (1) 60000
1
5.3)1(43.7(0.941) 8.32 )841.0(100000
2
5.3)7(5.47)5.4()7(3
43.7
3
32.8)5.4(
5000
2
2
222
2222
11
by using Muller-Breslau condition
11 x 1 =1.0
02.0
11
11
1
X
X1 = 50
The corresponding deflected shape of the arched truss which is also the
influence line for the relative displacement at the cut section it’s value
given by using virtual work method at different joint in the truss.
a) Put (1t) at point (1) and calculate the deflection for the main system
Fig.16.d and e.
dLEA
NnL
EA
Nndl
EI
MM
linkbeam
ff
111
1
M = X1 M1 = 50 M1
zeroEA
NN
link
1
N = X1 N1 = 50 N1 , hence:-
556.00.81 8.32 0.108 0.841 0.4326 8.32100000
50
3
32.84.15.4
1.4) 7 4.5 (2.8 0.5 4.5 1.4 2.8 7 3
7.43 7 7
2
4.2 2.8
7) 5.6 4.2 4.2 ( 0.5 4.2 7 4.5 (5.6 3
7.43
3
8.32 4.5 5.6
50000
50- 1
318 Chapter (5) - I.L.of Indeterminate Beams and Frames
b) Put (1t) at point (2) and calculate the deflection.
LEA
NL
EA
NndL
EI
Mm
linkbeam
2222
n
8867.0 7.433 0.941 0.1345 7.433 0.941 0.2018
0.216 8.32 0.841 0.841 8.32 3244.0
100000
50
3
32.88.25.4
2.8) 7 4.5 (5.6 0.5 2.8 4.5 5.6 7 3
7.43 7 7
2
8.4 5.6
4.5) 4.8 7 4.2 ( 0.5 8.4 7 4.2 (4.5 3
7.43
3
8.32 4.2 4.5
50000
50- 2
hence the I.L. X1 as shown in Fig.16.f.
Also;
I.L. Mn = I.L. Mno + Mn1 I.L X1
= I.L Mno – 7 I.L. X 1 (Fig.16.g)
I.L. Nn = I.L. Nno + Nn1 I.L. X 1
= I.L. Nno – 1 I.L. X1 (Fig.16.h)
I.L. Nn = - I.L. X1
I.L. Qn = I.L. Qno + Qn1 I.L. X1
= I.L Qno + (Zero) I.L. X1 (Fig.16.i)
I.L. Qn = I.L Qno
I.L. Mm = I.L. Mmo + Mm1 I.L. X1
= I.L. Mmo - 5.75 I.L. X1 (Fig.16.j)
I.L. Nm = I.L. Nmo + Nm1 I.L. X1
= I.L. Nmo - 0.94179 I.L. X1 (Fig.16.k)
I.L. Qm = I.L. Qmo + Qm1 I.L. X1
= I.L. Qmo – 0.33634 I.L X1 (Fig.16.L)
Chapter (5) - I.L.of Indeterminate Beams and Frames 319
Figure (16)
320 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (16)
Chapter (5) - I.L.of Indeterminate Beams and Frames 321
Figure (16)
322 Chapter (5) - I.L.of Indeterminate Beams and Frames
5. INFLUENCE LINE FOR FRAME
It is required to draw the influence lines for YA, Yc , YB , and Mc for the
given frame as shown in Fig.17.
I.L. YA
In this case the movable support at A is removed and YA is applied with
a value just enough to make the vertical displacement A equal to unit,
A =1, the resulting elastic line is the influence line for YA, Fig.17.a.
I.L. YC
Also to find the influence line for vertical component of reaction at C,
YC, as shown in Fig.17.b. , a unit vertical displacement is imposed at c,
without rotation or horizontal displacement. The elastic line of frame is
the influence line for Yc.
Figure (17)
Chapter (5) - I.L.of Indeterminate Beams and Frames 323
I.L.XB
To construct the influence line for XB the horizontal component of
reaction at B, XB, of the given frame. In this case, the hinge at B is
replaced by a roller support as shown in Fig.17.c and XB is applied with a
value just enough to make a horizontal displacement SB = 1. the elastic
line for this case is the influence line for XB as shown in Fig.17.c.
I.L.MC
To draw the influence line for the moment reaction at c; Mc; the fixed
support at c is replaced by a hinge as shown in Fig.17.d and Mc is applied
at c with a value such that the angle of rotation Sc (or c) equals to unity.
The resulting influence line is the influence line for Mc is shown in
Fig.17.d.
Figure (17)
From the previous cases solved it is clear that the procedures for construct
any influence line of any function are according to the following.
1- The structure is modified in such a way that the function can do work.
2- The function is doing work through a unit displacement.
3- The resulting elastic line is the required influence line.
324 Chapter (5) - I.L.of Indeterminate Beams and Frames
6. ANALYSIS OF STATICALLY INDETERMINATE
FRAMES (Using Muller- Breslau’s principle)
The procedures are;
1. Choose the main system and find the redundant reaction components;
X1 and X2 for the given frame as shown in Fig.16.
2. To find the influence line for any function, the influence lines of the
redundant reaction components should be obtain at first. And the
influence line of other functions can then be obtained by
superposition, or static relations.
3. Find the values of , , , and , using the virtual work
method and hence find the magnitudes of redundant X1 and X2 .....
etc; which satisfy the two displacement conditions imposed by
Muller- Breslau principles.
4. To draw influence line of X1, the displacement conditions at A& B
are;
= 1 (at A)
= 0 (at B) , hence
Chapter (5) - I.L.of Indeterminate Beams and Frames 325
X1 11 + X2 12 = 1
get X1
X1 21 + X2 22 = 0
The above equations give the values of X1 and X2 which are used to
find the B.M.D. as follows :-
M = X1.M1 + X2.M2
Hence, the elastic line produced by this B.M.D, as elastic load; is the
influence line of X1.
5. To draw influence line of X2 the displacement conditions are;
= 0 (at A)
= 1.0 (at B)
Hence:
X1. 11 + X2. = 0
get X2
X1. + X2. = 1
and
M= X1.M1 + X2. M2
The influence line is the elastic line produce by the second M.
Incase of frame with three time indeterminate, in this case the
analysis includes three sets of there simultaneous equations as
follows:
1
33332 2311
233222211
133122111
Xfor
0 = . X .X + . X
0 = . X . X + . X
1 = . X . X + . X
and
326 Chapter (5) - I.L.of Indeterminate Beams and Frames
2
333322311
233222211
133122111
Xfor
0 = . X . X + . X
1 = . X . X + . X
0 = . X . X + . X
and
3
33332 2311
233222211
13 3122111
Xfor
1 = . X .X + . X
0 = . X . X + . X
0 = .X . X + . X
The B.M.D for the three sets are obtained from the following
equation;
M = X1 . M1 + X2 . M2 + X3 . M3
The influence line can be obtained using M.D.
6. I. L. for any other function (R) such as, reaction, moment, shear, and
normal force can then be obtained by use of conditions of
superposition or by equilibrium as follows;
I.L.R = I.L.Ro + R1 (I.L.X1) + R2 (I.L.X2) + Rn (I.L.Xn)
Where:
I.L.Ro is the influence lime of function R in main system.
and
R1, R2, ..... Rn are the values of R due to:
X1 = 1
X2 = 1
.
.
.
.
Xn = 1 respectively
Chapter (5) - I.L.of Indeterminate Beams and Frames 327
7. In case of once statically in determinate frames;
X1 11 = 1 and M = X1 . M1
Example(10)
For the given frame shown in Fig.18, determine : -
I.L Xa 2- I.L Mn and Qn
Figure (18)
328 Chapter (5) - I.L.of Indeterminate Beams and Frames
Solution
1) Choose the determinate main system as shown in Fig.18.a, then find
the M1.D. as shown in Fig.18.b.
by apply X1 = 1t at A.
2) Calculate 11 form M1.D. then;
EI
106.67 4
3
12 4 2
3
4 4 4
EI
1 11
3) Muller Breslau condition at A
1X
106.67
EI
1 X
11
4) The ordinates of elastic line of part CDE are obtain using elastic
equilibrium by knowing the elastic load, M/EI as shown in Fig.18.c
Draw the elastic curve by knowing the slope and deflection using the
elastic load Method, conjugate beam method Fig.18.d as follows :-
0.125- 1 3
2 4 2 8-
106.67
EI 5
(upward)
0.2- 2 3
4 4 4 8-
106.67
1
4
2 (upward)
0.225- 3 3
4 6 6 8-
106.67
1 3
(upward)
0.15- 2 8 106.67
1 e (upward)
I.L Xa = I.L X1 as shown in Fig.18.e, also
I.L Mn = I.L Mno + Mn1 I.L X1
= I.L Mno – 4 I.L X1
I.L Mno shown in Fig.18.f
I.L Mn shown in Fig.18.h, and also
Chapter (5) - I.L.of Indeterminate Beams and Frames 329
I.L Qn = I.L Qno + Qn1 I.L X1
= I.L Qno + zero I.L X1
= I.L Qno
I.L Qn = I.L Qno as shown in Fig.17.g
Example (11)
For the shown frame in Fig.18, draw I.L. of Ms
EI= 30000 t.m2
Figure (19)
Solution
The frame is once statically indeterminate structure, hence:
EI
.dLM
21
11
=
44 6 4
3
2
2
4 4
EI
2
= EI
67.234
1.0 .X 111 , hence; I.L.X1 as shown in Fig.19.d.
I.L.Ms:-
Ms = Mso + X1.M1s
I.L.Ms = I.L.Mso + I.L.X1 (-4)
330 Chapter (5) - I.L.of Indeterminate Beams and Frames
I.L.Mso:
1 ton between c-s
Mso = 8Ybo
I.L.Mso = 8 I.L.. Ybo
1 ton between s-d
Mso = 4. Yao
I.L.Mso = 4.I.L.Yao
I.L.MS as shown in Fig.19.e.
Figure (19)
Chapter (5) - I.L.of Indeterminate Beams and Frames 331
Figure (19)
Example (12)
For the shown frame in Fig.20, Construct the I.L. for YA , MA , Mn , Qn
and Nn .
Figure (20)
Solution:
1- Choose the main system as shown in Fig.20.a. with the vertical
reaction at C and rotation at A as redundant;
EI
3888 218
3
18 211 = EI
dLM 2
1
332 Chapter (5) - I.L.of Indeterminate Beams and Frames
EI
270 118
3
18118
2
1812
= EI
dLMM 21
EI
24 11
3
18118122 = EI
dLM 2
2
From 11 (to get elastic curve due to unit displaceent) hence:-
1212111 XX
0222121 XX
EI X X 21
2703888
02427021
X X
Solve to get EI
X50.850
1 ,
EIX
60.752
Let EI = 850.50
11 X , 25.112 X
MM 2211 XXM F
Additional moment at A = 850.50
884.06
5.4688.1
3
5.4812.2
2
5.44375.85.850
5.850
1 222
1
607.06
9375.3
3
963.5
2
962.55.850
5.850
1 222
2
2765.06
5.1306.5
3
5.1344.8
2
5.138125.25.850
5.850
1 222
3
1407.0 6
5.1306.550.1325.20
5.850
1 2
4
1607.06
9375.3925.20
5.850
1 2
5
10.06
5.4688.15.425.20
5.850
1 2
6
Chapter (5) - I.L.of Indeterminate Beams and Frames 333
Figure (20)
334 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (20)
3- 1A
0270388821
X X
EI X X 21
24270
Solve to get EI
X60.75
1 ,
EIX
25.52
Let EI = 75.60
11 X , 40.142 X
MM 2211 XXM F
77.2 3
5.46.3
2
5.48.10
6
5.49.05.46.75
60.75
1 222
1
893.2 3
92.7
2
92.7
6
98.196.75
60.75
1 222
2
567.13
5.138.10
2
5.136.3
6
5.137.25.136.75
60.75
1 222
3
84.06
5.137.25.138.10
60.75
1 2
4
964.06
98.198.10
60.75
1 2
5
603.06
5.49.05.48.10
60.75
1 2
6
Chapter (5) - I.L.of Indeterminate Beams and Frames 335
I.L.MA as shown in Fig.20.c.
Figure (20)
Example (13)
For the shown frame in Fig.21, it is required to draw the influence
lines for Ya , Ma , Nn & Qn
Figure (21)
336 Chapter (5) - I.L.of Indeterminate Beams and Frames
Solution
First we choose a main system
Figure (21)
From M1 & M2 Diagrams Find δ11 ,δ22 & δ12=δ21
δ11= 118+1120/3=14.6667
δ22= 8820+2888/3=1621.3333
δ12=δ21=-(818/2+8120/2)=-112
to draw I.L. for X1 (Ma) Put 1=1 & 2=0 then;
δ11X1+δ12X2 =1 ….(1)
δ21X1+δ22X2 =0 ….(2)
14.667X1-112X2=1
-112X1+1621.33X2=0
solving the above equations we get
X1=0.1443 , X2=0.009968
From the Above values we draw the final moment M1 final on the frame
then using Conjugate beam method we find the elastic curve (I.L) for X1
(Ma) as shown in Fig.21.5.
Figure (21)
Chapter (5) - I.L.of Indeterminate Beams and Frames 337
Figure (21)
Station El. Load ord. B M (Y)
E - -0.65823
1 0.06456 0.00000
2 0.05013 0.20962
3 0.03570 0.21873
4 0.02127 0.08506
5 0.00684 -0.13367
6 -0.00759 -0.37975
7 -0.02203 -0.59544
8 -0.03646 -0.72304
9 -0.05089 -0.70481
10 -0.06532 -0.48304
11 -0.07975 0.00000
F - 1.26582
Similarly to find I.L. for X2 (Xb) put Δ1=0 & Δ2=1
338 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (21)
Solving
we get X1=0.00997 , X2=0.0013
station El. Load ord. B M (Y)
E - 0.15190
1 -0.00047 0.00000
2 -0.00147 -0.07434
3 -0.00247 -0.14278
4 -0.00347 -0.20136
5 -0.00446 -0.24608
6 -0.00546 -0.27294
7 -0.00646 -0.27797
8 -0.00745 -0.25718
9 -0.00845 -0.20658
10 -0.00945 -0.12218
11 -0.01044 0.00000
F - 0.28481
After getting the two redundant Influence lines we can easily draw any
Function by Just substituting in the following relation:-
I.L. F = I.L F0 + F1 I.L.X1+ F2 I.L.X2
So to draw I.L Ya we should construct I.L. Ya0 and find Ya1, Ya2 when
X1=1 & X2 =1 respectively as follows:-
Ya1=-.05, Ya2= 0.0, I.L YA as shown in Fig.21.d.
Chapter (5) - I.L.of Indeterminate Beams and Frames 339
Figure (21)
station I.L. Ya
e 1.2
1 1
2 0.89
3 0.79
4 0.7
5 0.61
6 0.52
7 0.43
8 0.34
9 0.24
10 0.12
11 0.00
f -0.26
340 Chapter (5) - I.L.of Indeterminate Beams and Frames
I.L. For Nn :-
Nn1=0.0, Nn2= -1.0 & I.L.Nn0 = 0.0
So I.L.Nn =-1 I.L.X2 = - I.L. Xb, as shown in Fig.21.c.
I.L. For Qn :-
Qn1=-0.05 Qn2= 0.0, I.L. as shown in Fig.21.e.
Figure (21)
station I.L. Qn
e 0.2
1 0
2 0.11
nleft 0.21
nright 0.79
4 0.7
5 0.61
6 0.52
7 0.43
8 0.34
9 0.24
10 0.12
11 0.00
F -0.26
Chapter (5) - I.L.of Indeterminate Beams and Frames 341
7. MAXIMUM EFFECT USING INFLUENCE LINE:
For the given continuous beam, Fig.22.a and from the sketch of shape of
the influence line for reaction at B (for example) as shown in Fig.22.b;
the maximum reaction due to live loads is as follows :-
Figure (22)
Max. +ve YB will occur at B when spans AB, BC, and DE are loaded as
shown in Fig.22.b. similarly the maximum values of bending moment at
support C, shear at S, moment at S will occur due to the loading shown in
Fig. C, D and S respectively. For multistory building frame Fig.23, the
influence line can be also use very useful in determining the loading
pattern in the case of live.
342 Chapter (5) - I.L.of Indeterminate Beams and Frames
Figure (23)
Absolute Bending Moment Diagram:
For the design load purpose, the absolute BMD may be required. Fig.24
shows the absolute BMD for the given beam.
Figure (24)
Chapter (5) - I.L.of Indeterminate Beams and Frames 343
PROBLEMS
Obtain the influence lines for reactions, and indicated internal forces for
each of, the given statically indeterminate structures; hence calculate the
value of Mn due to moving live load 2 t/m`.
344 Chapter (5) - I.L.of Indeterminate Beams and Frames
Chapter (5) - I.L.of Indeterminate Beams and Frames 345
For the given structures, draw the I.L. of Ya, Mn, Qn, and Nn.
6 INFLUENCE LINES
OF STATICALLY INDETERMINATE
TRUSSES
1. GRAPHICAL DETERMINATION OF TRUSS
DISPLACEMENTS
1.1. INTRUDUCTION
Truss displacements were obtained by the method of virtual work. The
use of virtual work method is limited, as it gives only the deformations at
certain points. The use of graphical method gives graphically the
deformations of all the truss joints in addition to constructing easily the
influence line of statically indeterminate trusses.
1.2. THE DISPLACEMENT DIAGRAM
Assume the triangle truss shown in Fig.(1.a) the displacement 1 and
2 of
both joints a and b respectively are assumed to be known. The change in
length of any member is calculated as follows;
eTemperatur
Force Axial
LtAE
LN
It is required now to obtain the displacement cc’ of joint c
The procedure could be summarized as follows;
Assume that the triangle abc is opened only at c and member
ac moves parallel to itself to a new position by a’c1 and its
elongation c1c3 is equal to ac
. Similarly, member bc moves to b’c2
parallel to itself with elongation (or contraction) bc
.
To close the triangle, c3 moves on an arc with center at a’ and
c4 moves on an arc with center at b’. The intersection point is c’ and
cc’ is the required displacement. Because the displacements are
very small if compared with the length of the members, the arcs can
be replaced by straight lines normal to the members.
Chapter (6) - I.L.of Indeterminate Trusses 347
The displacement can be drawn as a separate diagram
Fig.(1.b), from the origin point o, the displacement aa’ and bb’ are
drawn as vectors oa’ and ob’. From a’ draw ac
in the direction of
ac, ac
may be elongation or contraction, and a line normal to it is
drawn. Similarly, for bc
. The intersection point c’ of the two
normal determines the displacement cc’ of the joint cc’ of the joint
c which is represented by vector oc’= 3
.
1.3. WILLIOT DIAGRAM
In the case of a truss consists of triangles, the position of one panel point
and a direction of one member remain unchanged. The displacement of
the other panel points can be found by repeating the previous
displacement diagrams several times and the final diagram is called
Williot diagram. In order to draw the Williot diagram, we must know two
points in the Williot as a’ and b’ .This is achieved if we know the
displacements 1
and 2
or we know the relative displacement 21
between the two joints a and b, see Fig.(1).
Figure
(1.a)
Figure (1.b)
348 Chapter (6) - I.L.of Indeterminate Trusses
1.3.1. Cases Of Williot Diagram
a. Trusses with two joints fixed
Cantilever truss, 021 , Fig.(2.a & b)
To construct the Williot diagram for this case apply the following
steps
1- First of all, find out the internal forces N0 in all members due
to the external loads.
2- Calculate the member deformations for all members due
to the internal forces N0. The type of deformations (may be
extension of contraction) should be considered. The usual
practice is to use +ve sign for extensions and –ve sign for
contraction as shown in the given truss.
eTemperatur
Force Axial
0 LtAE
LN
.
Figure (2.a)
Figure (2.b)
Chapter (6) - I.L.of Indeterminate Trusses 349
3- Select a joint (or joints) in the truss, which is fixed. Now start
the construction of Williot diagram as given.
4- The vertical (V6) as well as the horizontal (H6) displacements
of point 6 (for example) may now be obtained from the Williot
diagram as shown
Example (1)
A given crane truss has two hinged supports at joints A & D. The
values of both internal forces and deformations due to the applied
loads are indicated around each member. Find the horizontal as well
as vertical displacement of joint C using the displacement diagram
method. Given EA=80000 ton for all members.
Solution 1. Find the internal force in each member due to the
given loads.
2. Calculate the member deformations due to the internal
member forces.
Member L (m) EA (ton) F (ton) (cm) Remarks
AB 8.49 80000 34.17 0.36 Tension
BC 7.71 80000 25.71 0.25 Tension
CD 11.28 80000 -37.59 - 0.53 Compression
DA 6.00 80000 0.00 0.00 Zero Member
Figure (3.a) Figure (3.b)
350 Chapter (6) - I.L.of Indeterminate Trusses
DB 6.00 80000 -15.37 - 0.12 Compression
3. Choose a convenient scale to enlarge the displacement
values.
4. Select a member of fixed direction (member AD) and
fixed joint on either end of the selected member (joint A).
5. Point a’ (corresponding to joint A) is located first on a
sheet paper.
6. Point d’ is drawn relative to a’ horizontally (away to
a’ if the member AD elongates or towards a’ if AD shortens
and parallel to AD), in this case, point d’ coincides to a’
because AD is zero member.
7. Select a triangle such that two joints are previously
located while the third one is required. This is achieved in
ADB in which both joints A & D are known but joint B is
required.
8. From a’ draw a’b1 of length=0.36 cm parallel to AB
and in the direction of AB because FAB is Tension.
9. From d’ draw d’b2 of length=0.12 cm parallel to DB
and in the direction of BD because FBD is Compression.
10. The intersection of the normals to a’b1 and d’b2 at b1
and b2 respectively gives joint B which represented by b’.
11. Select a triangle BCD in which both joints B & D
are known but joint C is required.
12. From b’ draw b’c1 of length=0.25 cm parallel to BC
and in the direction of BC because FBC is Tension.
13. From d’ draw d’c2 of length=0.53 cm parallel to DC
and in the direction of CD because FCD is Compression.
14. The intersection of the normals to b’c1 and d’c2 at c1
and c2 respectively gives joint C which represented by c’.
Chapter (6) - I.L.of Indeterminate Trusses 351
15. Measure horizontally the distance between a’ and c’
and divide by the scale to find Hc=1.59 cm.
16. Measure vertically the distance between a’ and c’ and
divide by the scale to find Vc=2.02 cm.
b. Williot diagram for three hinged trusses
0BA , Fig.(4)
To draw the Williot diagram, start from A’ or B’ as fixed points,
then find C’. From A’ and C’ find 5’. From A’ and 5’ find 1’. From
1’ and 5’ find 6’. From 5’ and 6’ find 3’ …………etc. The above
procedure is applicable only when AC and BC are straight lines.
c. Williot diagram for symmetrical trusses
Figure (3.c)
Figure (4)
352 Chapter (6) - I.L.of Indeterminate Trusses
To construct the Williot diagram for symmetrical trusses of
symmetrical loading, consider the given truss in Fig.(5.a). For this
case, assume point 4 (or point 3) as fixed points and direction 3-4 is
fixed, then Williot diagram is as shown in Fig.(5.b), point 4’
coincides to the origin 0. In reality, point A at hinged support
remains in place not point 4.
Hence, the vectors A’1’, A’4’, A’3’, …………etc. Each
displacement may be resolved into a vertical component V and a
horizontal component H. For example, the vertical displacement
component of point 4 is equal to V4 while the horizontal
displacement component of point 4 is equal to H4 as shown in
Fig.(5.b).
For other cases of truss symmetry as shown in the following
Fig.(6.a), assume point A as a fixed point and direction 4-6 is the
fixed direction. Then complete the Williot diagram as shown in
Fig.(6.b)
Figure(5.a
)
Figure (5.b)
Chapter (6) - I.L.of Indeterminate Trusses 353
Example (2)
For the given truss shown in Fig.(7) find the vertical and horizontal
displacement of point C. Given EA=80000 ton for all members.
Solution
1. Find the internal force in each member due to the
given loads.
2. Calculate the member deformations due to the internal
member forces.
Member L (m) EA (ton) F (ton) (cm) Remarks
AB 8.00 80000 -13.33 - 0.13 Compression
BC 5.00 80000 16.67 0.10 Tension
Figure(6.a)
Figure (6.b)
Figure(7.a
)
Figure (7.b)
354 Chapter (6) - I.L.of Indeterminate Trusses
CA 5.00 80000 16.67 0.10 Tension
3. Choose a convenient scale to enlarge the displacement
values.
4. Select a member of fixed direction (member AB) and
fixed joint on either end of the selected member (joint A).
5. Point a’ (corresponding to joint A) is located first on a
sheet paper.
6. From a’ draw a’b’ of length=0.13 cm parallel to AB
and in the direction of BA because FBA is Compression.
7. Select a triangle ABC in which both joints A & B
are known but joint C is required.
8. From a’ draw a’c1 of length=0.10 cm parallel to AC
and in the direction of AC because FAC is Tension.
9. From b’ draw b’c2 of length=0.10 cm parallel to BC
and in the direction of BC because FBC is Tension.
10. The intersection of the normals to a’c1 and b’c2 at c1
and c2 respectively gives joint C which represented by c’.
11. Measure horizontally the distance between a’ and c’
and divide by the scale to find Hc=0.065 cm.
12. Measure vertically the distance between a’ and c’ and
divide by the scale to find Vc=0.25 cm
Chapter (6) - I.L.of Indeterminate Trusses 355
d. Williot diagram for trusses having only one fixed joints
In the case of unsymmetrical loading, we cannot draw Williot diagram
until we assume either the direction of joint G or joint B with respect to
joint A is fixed. Strictly speaking, either of the two assumptions are
wrong, since the joint B and G are found to have vertical as well as
horizontal displacement, under the action of the external loading, Fig.8.
In order to start the Williot diagram, we have to make either of two
assumptions stated above. The usual practice in such case is that the
direction of G with respect to joint A is first assumed to be fixed and then
the Williot diagram for the whole structure is drawn. After completing the
diagram, we have to apply the necessary correction for the wrong
assumption we made first. This correction is applied by drawing another
Figure (7.c)
Figure (8)
356 Chapter (6) - I.L.of Indeterminate Trusses
diagram called “Mohr diagram”. The combined Williot and Mohr
diagrams is known as Williot-Mohr diagram.
e. Mohr diagram, Fig.9.
For example, consider the unsymmetrical loaded truss shown in the above
figure with joint A as a fixed point and assume member A2 has a fixed
direction, hence draw Williot diagram. From Williot diagram, the
displacement at roller support B does not satisfy the boundary conditions
at B. This support can only move horizontally to satisfy this condition. So
we must rotate the deformed shape of truss with respect to point A. Each
joint will rotate with a radius from A to the joint by such an amount that
point B’ will reach the horizontal line AB as shown in Fig.(9.d) while
Fig.(9.c) shows the deformed shape of truss according to Williot diagram
(before correction).
The actual displacement of point B’ and other points are obtained from
Fig.(9.b) named A’ 2” B” 3” 1” in which A’B” is taken equal to the
vertical component A’B”. The actual displacement of each joint is then
the distance between the dashed letter (for example B’ in Williot diagram)
and the same double dashed one (for example B” in the rotated deformed
shape of truss).
Figure (9.a)
Figure (9.c)
Figure (9.d)
Figure (9.b)
Chapter (6) - I.L.of Indeterminate Trusses 357
1.4. WILLIOT-MOHR DIAGRAM
In the case of having a fixed point but no fixed direction, Williot-Mohr
diagram have to be constructed. Consider the unsymmetrical loaded truss
as shown in Fig.(10.a). Assume joint 2 as a fixed point and member 2-4 as
a fixed direction (member 2-4 has minimum change in slope at bottom
chord). Hence draw both Williot and Mohr diagrams to satisfy the
boundary conditions at A and B. The support at B moves horizontally,
then the horizontal displacement at B is equal to Hb at Williot-Mohr
diagram. Similarly, point A’ must be taken as an origin instead of point
2’. The final displacement of any joint, say joint 3, will be equal to the
vector connecting the two points on Williot and Mohr diagrams (3’3” for
joint 3) and similarly the other joints.
Example (3)
Figure (10.a)
Figure (10.b)
358 Chapter (6) - I.L.of Indeterminate Trusses
A given Warren truss shown in Fig.(11) is subjected to external loads and
the extensions as well as contractions in different members are given as
shown. Draw the Williot-Mohr diagram to find the vertical deflection at
joint C. Given EA=80000 ton for all members.
Solution
1. Find the internal force in each member due to the given loads.
2. Calculate the member deformations due to the internal member
forces.
Member L (m) EA (ton) F (ton) (cm) Remarks
AB 6.00 80000 23.33 0.17 Tension
BC 6.00 80000 50.00 0.38 Tension
CD 6.00 80000 16.67 0.13 Tension
EF 6.00 80000 -46.67 - 0.35 Compression
FG 6.00 80000 -33.33 - 0.25 Compression
AE 4.24 80000 -33.00 - 0.17 Compression
EB 4.24 80000 33.00 0.17 Tension
BF 4.24 80000 -4.71 - 0.02 Compression
FC 4.24 80000 -23.57 - 0.12 Compression
CG 4.24 80000 23.57 0.12 Tension
Figure (11.a)
Chapter (6) - I.L.of Indeterminate Trusses 359
GD 4.24 80000 -23.57 - 0.12 Compression
3. Choose a convenient scale to enlarge the displacement values.
4. Since there is no member having a fixed direction, assume that
member AB has a fixed direction and then start with fixed joint on
either end of the selected member (joint A).
5. Point a’ (corresponding to joint A) is located first on a sheet paper.
6. From a’ draw a’b’ of length=0.17 cm parallel to AB and in the
direction of AB because FAB is Tension.
7. Select a triangle ABE in which both joints A & B are known but
joint E is required.
8. From a’ draw a’e1 of length=0.17 cm parallel to AE and in the
direction of EA because FEA is Compression.
9. From b’ draw b’e2 of length=0.17 cm parallel to BE and in the
direction of BE because FBE is Tension.
10. The intersection of the normals to a’e1 and b’e2 at e1 and e2
respectively gives joint E which represented by e’.
11. Select the next triangle BEF in which both joints B & E are
known but joint F is required.
12. From b’ draw b’f1 of length=0.02 cm parallel to BF and in the
direction of FB because FFB is Compression.
13. From e’ draw e’f2 of length=0.35 cm parallel to EF and in the
direction of FE because FFE is Compression too.
14. The intersection of the normals to b’f1 and e’f2 at f1 and f2
respectively gives joint F which represented by f’.
15. Select the next triangle BFC in which both joints B & F are
known but joint C is required.
360 Chapter (6) - I.L.of Indeterminate Trusses
16. From b’ draw b’c1 of length=0.38 cm parallel to BC and in the
direction of BC because FBC is Tension.
17. From f’ draw f’c2 of length=0.12 cm parallel to FC and in the
direction of CF because FCF is Compression.
18. The intersection of the normals to b’c1 and f’c2 at c1 and c2
respectively gives joint C which represented by c’.
19. Select the next triangle CFG in which both joints C & F are
known but joint G is required.
20. From c’ draw c’g1 of length=0.12 cm parallel to CG and in the
direction of CG because FCG is Tension.
21. From f’ draw f’g2 of length=0.25 cm parallel to FG and in the
direction of GF because FGF is Compression.
22. The intersection of the normals to c’g1 and f’g2 at g1 and g2
respectively gives joint G which represented by g’.
23. Select the last triangle CDG in which both joints C & G are
known but joint D is required.
24. From c’ draw c’d1 of length=0.13 cm parallel to CD and in the
direction of CD because FCD is Tension.
Figure (11.b)
Chapter (6) - I.L.of Indeterminate Trusses 361
25. From g’ draw g’d2 of length=0.12 cm parallel to GD and in the
direction of DG because FDG is Compression.
26. The intersection of the normals to c’d1 and g’d2 at d1 and d2
respectively gives joint D which represented by d’.
27. The vertical distance in the Williot diagram between joints d’ and
a’ must be zero (to satisfy the roller supporting conditions), so, joint d’
is displaced towards a’ vertically (draw D” above a’ such that d’D” is
Figure (1.c)
362 Chapter (6) - I.L.of Indeterminate Trusses
parallel to the direction of roller displacement) by the value d”a’. All
joints of truss must be displaced a distance proportional to its spacing to
joint A and the length d”a’ , this is achieved by redrawing the whole
truss vertically such that the lower chord AD of the original truss
coincides completely to the length d”a’ in the Williot diagram to obtain
the Williot-Mohr diagram.
28. The actual displacement of each joint is then the distance between
the dashed small letter (for example c’) and the same double dashed
capital one (for example C”).
29. Measure horizontally the distance between c’ and C’’ and divide by
the scale to find Hc=0.55 cm.
30. Measure vertically the distance between c’ and C’’ and divide by
the scale to find Vc=1.43 cm
2. INFLUENCE LINES FOR STATICALLY
INDETERMINATE TRUSSES
The principle of Muller Breslau is applied for the influence lines of
indeterminate trusses. For the given truss shown in Fig.(12.a), the
influence lines for X1 is found as follows;
1. Apply X1 = 1 ton at the main system by cutting the member 4-7,
then get the values of N1 for each member.
2.
3. Compute the values of due to N1 from the equation
Force Axial
1
AE
LN
for each member.
4. Draw the Williot or Williot-Mohr diagram and draw the elastic line
of the loaded chord which is the required I.L.X1 .
Chapter (6) - I.L.of Indeterminate Trusses 363
5. The influence line for a force in any member can be obtained from
the following equation 110
X.L.INN.L.I.N.L.I , where I.L.N0 is
the influence line of the force at main system and N1 is the force in the
member due to X1 = 1 ton.
6. In cases of trusses with n degree of indeterminacy and
indeterminate beams or frames, the same procedure is followed.
Example (4)
For the shown continuous truss shown in Fig.(13.a) determine:
I. L. X1
I. L. N2-5
Solution
Figure (12)
Figure (13.a)
364 Chapter (6) - I.L.of Indeterminate Trusses
1. Remove the vertical support at B and apply a force of 1 ton
vertically at B, and then calculate the internal force in each member due
to this external load.
2. Calculate the member deformations due to the internal member
forces.
3. Draw the Williot diagram using these internal deformations as
stated in the previous examples.
Member L (m) EA (ton) F (ton) (cm) Remarks
A—1 5.00 100 0.50 2.50 Tension
2—3 5.00 100 0.00 0.00 Zero Member
4—5 5.00 100 0.00 0.00 Zero Member
B—6 5.00 100 0.00 0.00 Zero Member
1—3 5.00 100 0.50 2.50 Tension
3—5 5.00 100 0.50 2.50 Tension
5—6 5.00 100 1.50 7.50 Tension
A—2 5.00 100 0.00 0.00 Zero Member
2—4 5.00 100 -1.00 - 5.00 Compression
4—B 5.00 100 -1.00 - 5.00 Compression
1—2 7.07 100 -0.71 - 5.02 Compression
2—5 7.07 100 0.71 5.02 Tension
5—B 7.07 100 -0.71 - 5.02 Compression
Figure (13.b)
Chapter (6) - I.L.of Indeterminate Trusses 365
Figure (13.c)
4. From the Williot diagram, the elastic curve of the loaded chords
(lower chords) can be drawn and then divided by the value of vertical
deflection at B to get the I. L. X1
5. Draw the I. L. N(2-5)0
i. When 1 ton is right to joint 4,
N(2-5)0 = - YA-Left
I.L.N(2-5)0= - I.L.YA-Left ii. When 1 ton is left to joint 2,
N(2-5)0 = + YA-Right
I.L.N(2-5)0 = + I.L.YA-Right
6. Draw the I. L. N(2-5)
I.L.N(2-5)= I.L.N(2-5)0 + N(2-5)1 I.L.X1
I.L.N(2-5)= I.L.N(2-5)0 + 0.71 I.L.X1
366 Chapter (6) - I.L.of Indeterminate Trusses
Example (5)
For the given truss shown in Fig.(14) determine:
I. L. X1
I. L. N2-4
Given: EA=100 ton for all members.
: The unit load moves along the lower chords of truss.
Figure (14.a)
Figure (13.d)
Chapter (6) - I.L.of Indeterminate Trusses 367
Figure (14.a)
Solution
1. Cut the member 4-7 and apply a tensile unit force in it and then
calculate the internal force in each member due to this external load.
2. Calculate the member deformations due to the internal member
forces.
Member L (m) EA (ton) F (ton) (cm) Remarks
4—6 4.00 100 -0.71 - 2.84 Compression
5—7 4.00 100 -0.71 - 2.84 Compression
4—5 4.00 100 -0.71 - 2.84 Compression
6—7 4.00 100 -0.71 - 2.84 Compression
4—7 5.66 100 1.00 5.66 Tension
5—6 5.66 100 1.00 5.66 Tension
Figure (14.b)
368 Chapter (6) - I.L.of Indeterminate Trusses
3. Draw the Williot diagram using these internal deformations as
stated in the previous examples.
4. From the Williot diagram, the elastic curve of the loaded chords
(lower chords) can be drawn and then divided by the value of 4-7 =
19.39 to get the I. L. X1
5. Draw the I. L. N(2-4)0
i. When 1 ton is right to joint 2,
N(2-4)0= + YA
I.L.N(2-4)0= + I.L.YA
ii. When 1 ton is left to joint 2,
N(2-4)0 = + 4 YB
I.L.N(2-4)0 = + 4 I.L.YB
6. Draw the I. L. N(2-4)
I.L.N(2-4) = I.L.N(2-4)0 + N(2-4)1 I.L.X1
I.L.N(2-4) = I.L.N(2-4)0 + 0.00 I.L.X1
Figure (14.c)
Chapter (6) - I.L.of Indeterminate Trusses 369
Figure (14.d)
370 Chapter (6) - I.L.of Indeterminate Trusses
PROBLEMS
For the given trusses, find graphically the vertical and horizontal
displacements of joints C, D, E and horizontal displacement of roller
support at B. Given: A = 10 cm2 , E = 2000 ton/ cm
2.
(Ex.1.a) (Ex.1.b)
(Ex.1.c)
(Ex.1.d)
Chapter (6) - I.L.of Indeterminate Trusses 371
2. For the following trusses, draw the I. L. for the marked members.
(Ex.1.e)
(Ex.1.f)
(Ex.2.a)
372 Chapter (6) - I.L.of Indeterminate Trusses
(Ex.2.b)
(Ex.2.c)
(Ex.2.d)
Chapter (6) - I.L.of Indeterminate Trusses 373
(Ex.2.e)
(Ex.2.f)
(Ex.2.g)
7 THE MOMENT
DISTRIBUTION METHOD
Introduction
This method was originated by Prof. Hardy Cross in 1930 in a
paper entitled “Analysis of Continouous Frames by Distributing Fixed-
End Moments”. It is the method normally used to analyze all types of
statically indeterminate beams and rigid frames (Fig. 1) in which the
members are primarily subjected to bending. All the methods discussed
previously involve the solution of simultaneous equations, which
constitutes a major part of the computational work. The method of
moment distribution usually does not involve as many simultaneous
equation and is often much shorter than any of the other methods. It has
the further advantage of consisting of a series of cycles, each converging
on the precise final result; therefore the series can be terminated
whenever one reaches the degree of precision required by the problem at
hand. We know that the moment acting on the end of a member is the
sum of four separate effects.
(1) The moment due to the external loads if the member is considered
as a fixed-end beam (F.E.M.).
(2) The moment due to the rotation of the near end while the far end is
fixed.
(3) The moment due to the rotation of the far end.
(4) Them moment due to the relative translation between the two ends
of the member.
375 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
In this method, all the members of a structure are first assumed to be
fixed in position and direction and fixed and moments due to external
loads are obtained. Now all the hinged joints are released, by applying an
equal and opposite moment and their effects are evaluated on the opposite
376 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
joints. The unbalanced moment at a joint, is distributed in the two spans
in the ratio of their distribution factors. This process is considered simple
and understand and has scientific and systematic approach and used in the
design offices. The method of moment distribution can be applied to
structures composed of prismatic members (Uniform I) or no prismatic
members with or without joint translation.
Sign Convention:
Though different types of sign conventions are adopted by different
authors in their books, yet the following sign conventions, which are
widely used and internationally recognized, will be used.
“All the clockwise and moments and member rotations are taken as
positive and vice verse.”
Note:
The F.E.M. represents the action of the joints on the member.
Stiffness of Member:
For a member of uniform section (Constant EI), the stiffiness
(rotational stiffness) is defined as the end moment required to produce a
unit rotation at one end of the member while the other end is fixed.
Consider member AB in Fig. 2 with a constant section. End B is fixed
and end A is allowed to rotate (continuous support). The end moment
required at end A to rotate θA = 1 while θB = 0 is given as follows:
377 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
By using the method of conjugate beam; and from the condition of
geometry Fig. 3, θB = 0 then :
θB1 = θB2 ---------------- (1)
θA = θA1 - θA2 ---------- (1) (Note θB1 = 2
1θA1)
Therefore:
θB1 = EI6
L.M
EI2
L.M
3
1W3
1 ABAB1
θB2 = EI3
L.M
EI2
L.M
3
2W
3
2 BABA2
Substitute in eqn. 1
EI3
L.M
EI6
L.M BAAB
MBA = 2
1MAB ------------------- (3)
378 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Also θA = θA1 – θA2 (Note θA2 = 2
1θB1)
θA = EI6
L.M
EI3
L.M BAAB
θA = EI4
L.MAB
Or
The moment produce θA = 1 is given by
MAB = L
EI4
This moment is defined as “Absolute stiffness” and will be denoted
by K, thus
K = 4E L
I
= 4E S ……………. (4)
Where L
I= s being the “Stiffness Factor” or “Relative Stiffness”
Member with one hinged end
θA = EI3
L.MAB
MAB = L
EI4 θA
379 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
θAB = L
EI3. θA
K = L
EI3 = 4
3K
And S = 4
3 L
I
The modified stiffness K at end A when end B is hinged support is
three quarters the absolute stiffness K
Member of symmetry:
From symmetry
θA = - θB
M = θL
EI2
K = K2
1
L
EI2
And S = 2
1 * L
I
380 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Member of antisymitry:
θA = θB
MAB = M = AθL
EI6
K = K3
2
L
EI6
S = 2
3 L
I
Carry over Factor (C.O.F) and carry over moment (C.O.M)
we have already discussed that the moments are applied on all the
and joints of structure, whose effects are evaluated on the other joints.
The ration of moment produced at a joint to the moment applied at the
other.
Joints (Fig. 4), without displacing it, are called “carry over factor”. The
value of carry over factor for the above beam fig. 4 is equal to 2
1. Then,
the carry over moment MBA is one-half of moments MAB.
381 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MBA = CAB. MAB
= 2
1 MAB
= Aθ.L
EI2
Where CAB is the carry-over factor from A to B. for a member of
uniform EI. If we consider end A as the far end (fixed), and B as the near
end (allowed to rotate), we can, in like manner, prove that.
CBA = CAB = 2
1 (6)
Distribution Factors (D.F.)
Referring to the following figure (Fig. 5), which shows a frame composed
of four members, each with one end fixed and the other end rigidly
connected at joint O whose translation is prevented. If a clockwise
moment M is applied to the joint, it will cause the joint to rotate
clockwise through an angular deformation θ, as shown in Fig. 5. Since 0
is a rigid joint, each tangent.
382 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
(8)
(10)
To the elastic curve of the connected end rotates the same angle θ. The
applied moment M is resisted by four members meeting at the joint. The
resisting moments MoA, MoB, MoC, and MoD, will be induced at the ends of
the four members to balance the effect of the external moment M, as
shown in Fig. 5,c
Equilibrium of the joint 0 requires that Σ Mo = o
and also
MoA = θ.AL
EIoA4
o
= KoA. θ
MoB = θ.BL
EIoB4
o
= KoB. θ
MoC = θ.CL
EIoC4
o
= KoC. θ
MoD = θ.DL
EIoD4
o
= KoD. θ
The above equation 7 shows that, when the external moment is
applied to a joint, the resisting moments developed at the near ends of the
members metting at the joint, while the other ends are all fixed, are in
direct proportion to the rotational stiffness “K”.
Substituting in eqn. 8 in eqn. 7, we obtain
(KoA + KoB + KoC + KoD). θ = M
Thus, θ = K
M
(9)
We see that
MoA = K
KoA
. M = DoA. M
MoB = K
KoB
. M = DoB. M
MoA + MoB + MoC + MoD = M
383 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MoC = K
KoC
. M = DoC. M
DoD = K
KoD
. M = DoD. M
In which the ratio K
KoD
or DoA is defined as the “distribution
factor”. Thus; a moment resisted by a joint will be distributed among the
connecting members is proportion to their distribution factors, only the
relative K or S values for connected members are needed. Thus, in most
cases we are concerned with the “relative stiffness” rather than the
absolute stiffness.
Fixed End Moment (F.E.M.)
the application of the mothed of moment distribution requires
knowledge of the moments developed at the ends of loaded beams with
both ends. These moments are called “Fixed-End Moments”, often
denoted by the symbol F.E.M. in the examples.
The determination of fixed-end moment proveiously (3 moment
eqn.). for a straight prismatic member the fixed-end moments due to
common types of loading are given in the following Table (1).
384 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
385 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
386 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Application to various types of continouous Beams
In the previous articles, we have studied the principles of the
moment distribution mothod. First of all, all the fixed-end moments are
387 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
found for all the spans. The unbalanced moment at a support is
distributed among the two spans in the ratio of their stiffness factors or
relative stiffness (L
I or
4
3 L
Ior
2
1
L
I or
2
3 L
I) and their effects are
evaluated on the opposite joints. This process is continued, till we reach
the required degree of accuracy.
Non-Prismatic Members
The members have not uniform cross-Section are known, non prismatic
members.
The fixed end moments, stiffness, cary over factor, and distribution
factors for these members are not the same values as prismatic members.
To obtain these values, the method of column analogy or method of
consistant deformation, or conjugate beam method must be used.
Example (1): For the given beam, draw B.M. and S.F. Ds
388 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Solution:
At first, let us consider the continuous beam ABC be split into two fixed
beams AB and BC as shown in Figure (6).
1- Fixed end Moments.
Span AB: F.E.MAB = - 12
WL2= -
12
62 2 = - 6 t.m
F.E.MBA = + 12
WL2 = - 6 t.m
Span BC: F.E.MBC = 8
L.P= -
8
612 = - 9.0 t.m
F.E.MCB = + 9.0 t.m
2- Stiffness (or relative stiffness):
SAB = 6
1
L
I
SBC = 6
1
L
I
3- Distribution Factors (D) for member BA and BC will be 2
1and
2
1or
6/16/1
6/1
= 0.5
Now draw the beam and fill up the distribution factors and F.E.M.S
as shown in the following figure.
389 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
We obtain the F.E.MBA is +6.0 t.m and that in span BC F.E.MBC is 9.0.
thus there is an unbalanced moment at joint B equal to –9 + 6 = -3.0 t.m.
Now distribute this unbalanced moment (equal to –3.0) into the span BA
and BC in the ratio of their distribution factors i.e. + 1.5 and 1.5. Now
carry over the effects of these distributed moments (or Balanced moment)
at A and D equal to 2
1× 1.5 = +.75 then distribute the unbalanced moment
at B. (in this case, there is no carry over moment from A or C at B. So the
distribution of moment at B is zero). Now find out the final moment at A,
B, and C in the spans AB and BC by algebraically adding the respective
values. Calculate the bending moment in the spans AB and BC by
390 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
considering them as simply supported beams. Also calculate the reactions
at supports A, B, and C by considering the free body diagram for each
span. Now we can draw both shearing force and bending moment
diagrams as shown in the previous figures.
391 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
A continuous Beams with simply supported ends:
Sometime, a continuous beam is simply supported over one or both
of its ends. We know that the fixing moment on a simply supported end is
zero. Therefore, in such a case, the simply supported ends are released by
applying equal and opposite moments, and their effects are carried over
on the opposite joints as follow.
392 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
393 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
394 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
395 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Or by using the following table:
-
Joint B C D
Member BA BC CB CD DC DE
Relatives 6
1
4
3
10
1
10
1
12
1
12
1
6
1
4
3
D.F. 0.56 .44 .55 .45 0.4 .6
F.E.M +6.75 -6.75 +16.67 0 0 -13.5
D.M. +5.55 +4.37 -9.17 -7.5 +5.4 +8.1
.CO.M. 0 -4.585 +2.185 +2.70 -3.75 0
D.M. +2.56 +2.025 -2.685 -2.20 +1.5 +2.25
C.O.M. 0 -1.34 1.01 +.75 -1.1 0
D.M. +.75 +.59 -.97 -.79 .66 .44
C.O.M. 0 -.48 +.30 +.33 -.40 0
D.M. +.27 +.21 -.35 -.28 +.16 +.24
C.O.M. 0 -.175 +.105 +.08 -.14 0
D.M. .10 .075 -.1 -.085 +.08 +.06
Final
Moment
+15.54 -15.98 +6.99 -6.99 +2.41 -2.41
Average 15.72
Beams with end span overhanging
Sometimes, a beam is overhanging at its one or both the end
supports. In such a case, the bending moment at the supports near the
overhanging end will be due to the load over the cantilever portion and
will remain constant (Determinate), while the moments on the other far
support is one half of the overhanging moment plus or minus the fixed
end moment due to the load acting on the span. It is thus obvious, that the
396 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
distribution factors over the support having one span overhanging will be
1 and 0.
Moreover this support is considered as a simply supported for the
purpose of calculating the distribution factors in the span, adjoining the
overhanging span.
Example (6): A beam A B C D 9 M long is simply supported at A,
B and C such that the span AB is 3 m, span BC is 4.5
m and the overhanging CD is 1.5 m. It carries a
uniformly distributed load of 1.5 t/m in span AB and a
point load of 1 ton at the free end D. The moment of
inertia of the beam in span AB is I and that in the span
BC is 2I. Draw B.M., S.F.Ds.
397 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
398 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
399 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (8): for the given loaded beam ABCDE fixed at A
and roller at B, C, and D, DE being a
cantilevr. AB = 7 m, BC – 5, CD = 4 m and
DE = 1.5 m. the values of I, are 3I, 2I, I and I
respectively Draw B.M.D.
Solution:
400 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
3-10 Beams with settlement and rotation of supports:
For some cases one of the supports of a continuous beam
sinks down, with respect to others, as a result of loading. As a
result of differential settlement between the supports, additional
moments are caused on the supports, in addition to the moments
due to loading. Knowing that the moments due to settlement ∆ at
support B for the following figure, at A and B are: M = 2L
EI6 ∆,
while in case of left hand support A.
Sinks ∆ with respect to B the fixed end moment on both supports
is, M = + 2L
EI6. ∆
If support A has a rotation θ A, then F.E.M is
MAB = - θALAB
EI4
Example (9): A continuous beam is fixed at A and is carried
over roller at B and C as shown. Draw B.M.,
S.F.Ds due to given loads and settlement at B,3
cm.
401 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
E = 2 × 105 kg/cm
2, I = 2 × 10
6 cm
4
Solution:
402 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (10): A continuous beam ABC shown in the
following Figure. Draw B.M. and S.F. Ds due to given loads and
settlement at support B by 4 cm below A and C. E = 2 × 107
t/m2, I = 3 × 10
-4 m
4
Solution:
403 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1-Due to ∆ t = 20o (t2 > t1)
F.E.M.
MBA = - 1.5 h
.t.EI = -
8.0
10120800025.1 5 =-6 t.m
MBC = + h
.t.EI = -
8.0
10208000 5 =+2t.m
MCB = - h
.t.EI = =+2t.m
MCD = + h
.t.EI = +
8.0
102080002 5 =+4t.m
404 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
405 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
2- Due to loads
406 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (12): for the given continuous beam ABCDE. Draw
B.M., S.F.Ds due to ∆ t = - 15o at part BC,
EI = 10000 t.m2
H = 1.0 m, α = 1 × 10-5
(t2 < t1).
407 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (13): for the given continuous beam D.B.M. due to
given loads.
408 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Frames without side sway:
A frame without side sway (i.e. without any translation)
way also be solved by the method of moment distribution in the
same procedure as that for a continuous beam.
Example (14):
For the shown frame ABC Draw, N.f., S.F. and B.M.Ds
Prepare the following table
409 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
410 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
411 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (15): Draw B.M.D. for the shown frame
Solution:
1- Stiffnesses:
SAC = 8
1 = 0.125
SCD = 24
2 =
12
1 = 0.083
SDB = SAC = 0.125
2- Distribution Factors:
Joint – C-
D.FCA = 6.0083.125.0
125.0
D.FCD = 4.0083.125.0
083.0
Also at Joint D
D.FDC = 0.4
D.FDB = 0.6
3- Fixed end moments:
MCD = t.m48012
2410
12
WL22
MDC = +480 t.m
MAC = MDB = 0
412 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
The Previous calculation can be put in the following table:
Joint A C D B
Member AC CA CD DC DB BD
S 8
1
12
1
12
1
8
1
D.F. 0.6 .4 .4 .6
F.E.M. 0 0 -480 +480 0 0
D.M. 0 +288 +192 -192 -288 0
C.O.M +144 0 -96 +96 0 -144
D.M. 0 +57.6 +38.4 -38.4 -57.6 0
C.O.M +28.8 0 -19.2 +19.2 0 -28.8
D.M. 0 +11.52 +7.68 -7.68 -11.52 0
C.O.M +5.76 0 -5.76
F.M. 178.56 357.12 -357.12 +357.12 -357.12 -178.56
413 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Symmetrical Portal Frames:
A symmetrical portal frame is that, in which both the
columns are of a same length, moment of inertia, having similar
and conditions, and modulus of elasticity as wall as subjected to
symmetrical loading. The joints of a portal frames will not be
subjected to any translation or side sway. A simple portal frame
consists of a beam, resting over two columns. The joints of the
beam and column frames are either symmetrical (without side
sway) or unsymmetrical (with side sway).
Example (16): For example 15 taking the symmetry in
consideration. Draw B.M.D.
Solution:
Due to symmetry, we may use the half-frame of the
following figure and take into consideration the modified
stiffness s due symmetry as follows.
414 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
415 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Notes on symmetry and anti – symmetry of structures :
1- From the previous example 16 it is possible to take the
advantage of any symmetry of a structure if it is subjected
to load systems which are themseelves symmetrical or anti
– symmetrical about the same geometric centre line.on
such a symmetrical structure, symmetical liad systems
produce equal and opposite slopes about the centre line,
whilst anti – symmetrical loads cause deflections of equal
magnitude and different sign at corresponding points about
the centre as shown in the following figures;Example
(16):- Draw B.M.D for the given problem.
416 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
417 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Symmetrical loads:
Since these cause deformation, which are mirrored about
the structural centre – line, the slope at that centree line must be
zero. If this occure at a nodal point; that is, if the structure has an
even number of spans; we may regard the structure as being effec
– tively fixed at that point, and complete the calculation for one –
half of the structure only as shown in the shown figures of
beams or frames. If the number of spans is odd, however, as
418 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
given the figure, which show three span with symmetrical loads,
although the slope is zero at centre line, some vertical
displacement will occur, then this point cannot be consifer a
fived and the solution can be completed on the half of beam, take
account the modified stiffness S = 2
1S.
2- Anti – symmetrical loads:
If a symmetrical structure is subjected to loads which are
anti – symmetrical about the centre line as shown in the given
figure, solution of problem will vary depending on the numbert
of spans. Whether this be even or add as shown, the structure will
behave as if hinged support on the centre line ( case of beam) in
which the stiffness of span is (L
I
4
3). whereas in case of the
centre line at mid span of the member. In which the centre span
has a stiffness factor of ( L
I
2
3).
419 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (17): Draw B.M.D. for the give
structure.
420 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (18): find the B.M.D. for the given symmetrical
closed frame.
Solution:
421 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
422 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (19): draw B.M.D. for the symmetrical frame shown
in the given figure under the given anti – symmetrical loading.
Solution:
Now and from anti – symmetrical loading member EB is
split up to two members, each having half the actual moment of
inertia as shown. Then considering one – half of the frome and it
423 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
must noted the equivalent structure is symmetri – acl loading. We
get.
424 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (20):
425 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
To draw B.M.D ising joints equilibrium;
426 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (21):
427 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (22):
428 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (23):
429 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
430 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (24):
For the shown horizontal closed frome of a part of water tank.
Draw B.M.D. for tank.
Solution:
The frame is symmetrical, and symmetrically loaded about the
horizontal axis X-X. Then, it is sufficuent to consifer one half of
the frame only as follows:
431 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
432 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
433 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (25):
Draw B.M.D. for the double span frame shown in the following
Figure calculate reaction at F.
434 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
From Joint Stability:
To get horizontal reaction at F (XF):
From the free body diagram of columns and by applying
435 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (26): Draw the B.M.D. for the double story frame
shown in the following figure. Calculate the
forces in link members.
436 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1-Stiffness factors:
Joint C:
SAC = 4
2 = .5 ; SCD = .25 ; SCE
4
2 = .5
D.FAC = 0.4 ; D.FCD = 0.2 DCE = 0.4
Joint E:
SEC = 4
2 = .5 ; SEF =
16
2 = 0.125
D.FEC = 0.8 , D.FEF = 0.20
Joint D
SDB = 4
1= .25 ; SDC =
16
4 = 0.25 , SDF = 4
1= .25
D.FDB = 0.333 , D.FDC = .333 , D.FDF = 0.333
Joint F
SDB = 4
1= .25 ; SFE =
16
2 = 0.125
D.FFD = .67 D.FFE = .33
2- Fixed end Moments:
MAC = - 12
42 2 = - 2.67 t.m
MCA = + 2.67 t.m
MCD = - 12
164 2 = - 85.33 t.m
MDC = = + 85.33 t.m
437 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MCE = - 12
44 2 = - 5.33 t.m
MEC = = 5.33 t.m
MEF = - 8
1612 = - 24 t.m
MFE = = 24 t.m
MFD = MDB = Zero
Forces in Upper Link Member
H1 = 2
44
h
Story)(UpperM
438 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
= 4
86.3398.203.367.25 + 8 = 9.735 t
Forces in Upper Link Member
H2 = 4
05.1541.3037.780.43 +
2
42
+ 2
44
4
6.253.3686.3321
= 14.18 to
439 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
440 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (27): Draw B.M.D. the given two – span, two-story
frame.
Solution:
Hj = 6
1 (- 1.06 + .92 – 1.94 + .42) = - 1.66 (to right)
441 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
HF = 6
1 (3.8 + 3.94 + 1.97 – 4.68 – 2.29 – 5.73) +
2
65.1 - (- 1.66) = 5.66 (to left).
Structures subjected to Side Sway:
In more general case, however, when the joints are not
laterally supported , the equillubrium position at any joint cannot
be reaches by allowing rotation only at the joints, besides rotation
untill the sum of the forces as well as the moments at each joint
becomes zero. This translation is usually called “SIDE SWAY”.
Generally in case of side sway the final benfing moment diagram
not only due to the exterrnal loads but also due to translation of
joints. The solution of the problems is ussually divided into two
parts:
1- A calculation od end moments produced by the given
lodss, assuming that there aree no lateral movements.
2- A calculation od end moments produced by lateral move –
ments. The bending moments produced from this transla –
tion will be called “SIDE SWAY CORRECTION”.
The moment diatribution can be carried out in the
following steps:
1- Restrain all joints against translation, and carry out the
moment distribution as before.
442 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
2- Calculate horizontal as well as vertical reactions at the
column bases. The algebric sum of the horizontal reaction
will give the magnitude and direction of the sway force F,
which had held the frame against side sway as shown in
the following figures.
3- Remove the force F, which had held the frame, and let the
joints be allowed to sawy as shown in Figure (b). This will
cause a set of fixed end moments. Calculate these fixedenf
moments and distribute them. (This is done fixed by
assuming some suitable arbitrary sway moments and
distributed them). Now find out the horizontal reactions at
the column bases. The algebraic sum of the horizontal
reactions will give the assumed sway force. Find out the
moments and horizontal as well as vertical reactions due
to the actual sway force F, proportionately to the assumed
sway force).
443 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
4- The final mment at each joint maynow be obtained by
adding algebraically the momentss obtained in steps 1 and
3.
5- The horizontal as well as vertical reactions at the column
bases may also be obtained by adding algeebraically the
reactions obtained in steps 1 and 3 M = MO + fO
f1. M1
6- Knowing that the F.E.Ms. in case of translation
(Settlement) are as follow.
a- Case of fixed beam
b- Case of hinged at far end
444 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
- MA = Δ2L
EI3Δ.
2L
EI3Δ.
2L
EI6
Fixed – end moments in Frames due to side sway:
a) Members with fixed ends.
2L2.
2EI6
CDM
2L1.
1EI6
BAM
Δ
Then MBA = MCD 2
12
1
2 .)(L
I
L
L
445 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
b) Members with hinged ends:
2
2
1
2
3
2.
6
1.
EI
LM
EI
LM CDBA
then MBA = MCD 2
2
12
1
2 ).()(L
I
L
L
= 1
2
2
1 .2
3
L
L
S
SM CD
where S1 1
1
L
I and S2
2
2
4
3
L
I
Example (28): Draw the B.M.D. for the shown frame due to the
given loads. Also draw the deformed shape.
446 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Solution:
The frame is unsymmetrical,
theregore it will be
analysed first as a frome
without side sway and then
applying a sway correction .
Fixed end moments:
MBC = - 34.24
5.25.142
2
t.m
MCB = + 40.14
5.25.142
2
t.m
MBA = MCD = Zero
447 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Distribution factors:
SBA : SBC
4
1:
4
1
4
3
0.43 : 0.57
448 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
From MO.D XA = 0.32 , XD = 0.24
Then the horizontal force FO = 0.32 - .24 = .08
We have worked out the moments and reactions, under the
assumption, that a horizontal force FO = 0.08 t is acting at C.
Actually there is no such force acting at c. we know that if
a force of 0.08 t is applied at C, it will neutralise the effect
of force fO = 0.08 little con – sideration will dhow that if a
force of 0.08 at C.A Little con – sideration will show that id a
force of 0.08 t is applied at C, it will cause some sway moments
at the joints B and C of the frame.
Let MBA : MCD
.3
:.3
2
2
2
1
1
L
EI
L
EI
449 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
4
1:
4
1
1 : 1
Assume some arbitrary moments at B and C i .e. (MBA and
MCD) in the ratio 1:1 as already calculated and distribute the same
at other joints also. Let us assume the sway moments as – 2 t.m.
Then complete the following table:
(Use short solution by using antisymitry)
Horizontal reaction at A = 4
33.1
= .33
Horizontal reaction at B = .33
from the free body siagram as dhown we find that the
unbalanced horizontal force at C.
F1 = .33 + .33 = .66
But the actual unbalanced horizontal force is 0.08 t
therefore the actual sway moments in the members due to a sway
force of 0.08 t may be found out by proportion.
Then
M = MO + 1
1
MF
FO
450 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MB = - 1.27 + )33.1(66.
08.
= - 1.11 t.m
MC = - .96 + )33.1(66.
08.
= - 1.12 t.m
Reaction at A and D:
XA = 0.32 + 66.
08.(- .33) = .28 t
XD = -.24 + )33.(066.
08. = 0.28
451 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Solution:
Assumption, that a horizontal force FO =0.08 t is acting at C.
Actually there is no such force acting at c. we know that if
a force of 0.08 t is applied at C, it will neutralize the effect
of force fO = 0.08 little consideration will dhow that if a
force of 0.08 at C.A Little consideration will show that id a force
of 0.08 t is applied at C, it will cause some sway moments at the
joints B and C of the frame.
Let MBA : MCD
.3
:.3
2
2
2
1
1
L
EI
L
EI
4
1:
4
1
452 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1 : 1
Assume some arbitrary moments at B and C i .e. (MBA and
MCD) in the ratio 1:1 as already calculated and distribute the same
at other joints also. Let us assume the sway moments as – 2 t.m.
Then complete the following table:
(Use short solution by using antisymitry)
= .33
Horizontal reaction at B = .33
from the free body diagram as shown we find that the
unbalanced horizontal force at C.
F1 = .33 + .33 =.66
453 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
But the actual unbalanced horizontal force is 0.08 t
Therefore the actual sway moments in the members due to a
sway force of 0.08 t may be found out by proportion.
Then:
MB = - 1.27 + )33.1(66.
08.
= - 1.11 t.m
M = MO + 1
1
MF
FO
454 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MC = - .96 + )33.1(66.
08.
= - 1.12 t.m
Reaction at A and D:
XA = 0.32 + 66.
08.(- .33) = .28 t
XD = -.24 + )33.(066.
08. = 0.28
455 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 27:
A portal frame shown in the following figure is subjected to a
loading as shown. Draw B.M.D.
Solution:
Since the portal frame is unsymmetrical, therefore, it will
be analyzed first by assuming it without sway and then appiy ing
a sway correction.
456 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Horizontal reaction at A and D
XAO = 357.16
75.25.5
457 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
XDO = 79.06
58.116.3
FO = 1.357 – 7.9 = 0.585
We have worked out the moments and reactions under the
assumption that a horizontal force fo = 0.585 t is acting at c
to prevent the side sway: Actually there is no such force acting at
C. We know that if a force of 0.585 is applied at C, it will
neutralize the effect of do at C. If a force 0.585 is applied at,
it will cause some sway moments at joints B and C of the portal
frame.
MBA : MCD
1 : 1
Now assume some arbitrary moments at B, C, A and D in ratio of
1:1 assume M = -10 t.m
458 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
459 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
X1A = 6
55.748.8
= 2.67
X1D = 2.67
F1 = 2.67 + 2.67
= 5.34 ton
Final Moment M = Mo + 1
1
MF
Fo
MA = 2.75 + 34.5
585.0 (-8.48) = 1.82 t.m
MB = 5.5 + 34.5
585. (+7.55) = - 4.67 t.m
MC = - 3.16 + 34.5
585.0 (-7.55) = - 3.98 t.m
MD = + 1.58 + 34.5
585. (+8.48) = 2.51 t.m
460 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 28:
For the given frame.Draw the B.M.D.
461 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Moments assuming no joint transition:
XAO = 6
64.829.17 = 4.32
XDO = 6
59.718.15 = 3.80
FO = 4.32 – 3.8 = 0.53
2- Moments due to horizontal Movement:
Assume arbitrary Moment = -10 t.m and using the results
of previous example then;
F1 = 5.34
462 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Hence:
M = Mo + 1F
Fo (M1)
XA = 4.1 ton
XD = 4.1 ton
Example (29):
463 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
464 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
From Mo we get Fo = 1.67 t
From M1 we get F1 = 3.686
Then M = Mo + 1F
FoM1
465 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example (30):
466 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
467 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 31:
Draw B.M., N.F., and S.F.D. for the given frame due to given
loads.
Solution:
1- Relative Stiffness and D.F.
Joint C:
CA : CD : CF
468 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
4
1 :
9
2 :
3
1
4
3
.25 : 0.22 : .25
.35 : 0.30 : .35 D.F
Joint D:
DC : DB : DE
8
1
4
3:
4
1
4
3:
9
2
0.22 : 0.188 : 0.09
0.44 : 0.37 : 0.19 D.F
2- Fixed end moments
Member CD:
MCD = 12
2WL
= 12
93 2
= - 20.25
MDC = + 20.25
Member DE
Case (1)
469 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
M1DE = 16
3PL
= 16
853
= 7.5 t.m
M1DE = Zero
Case (2)
M2ED = + 2
2WL
= 2
22 2
= 4 t.m
470 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
M2DE = 2
2EDM
= 2
4
= 2 t.m
Then:
MDE = - 7.5 + 2 = -5.5 t.m
MDE = + 4 t.m
Member DF, CA and DB are Zero F.E.M.
Member C-C
MCC = + 62
23 2
3- Frame without side sway:
joint C C
Member C – C C – A C – F C – D D – C D – B D – E
D.F
F.E.M
D.M
C.O.M
+ 6
0
0
.35
0
4.98
0
.35
0
4.98
0
0.30
-20.25
4.29
-3.25
.44
+20.25
-6.49
2.15
.37
0
-5.46
0
.19
-5.5
-2.80
0
471 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
D.M
C.O.M
D.M
0
0
1.14
0
.17
1.14
0
.17
0.97
-.48
.14
-.95
+.48
-021
-.79
0
-.18
-0.41
0
-.09
F.M. +6 6.29 6.29 -18.58 15.23 -6.43 -8.8
4- Horizontal Reactions:
XA = 4
15.329.6
= 2.36 t
472 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
XB = 3
29.6
= 2.09
ΣX = 0
Fo = - (2.36 + 2.0 – 1.6 – 2.09)
Fo = 0.67
5- Moment due to side sway:
Assume arbitrary F.E.M. as follows:
MAC = MCA = .6
2L
EI
=
.16
6EI
MCF =
.3
2L
EI
= .9
3EI
473 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
=
.16
3EI
If we assume any value for EI∆ , say 144 then
MAC = MCA = - 54 t.m
MCF = + 48 t.m
MDB = - 27 t.m
Joint A c D
member AC CA CF CD DC DB DE
D.F
F.E.M
D.M
C.O.M
D.M
C.O.M
D.M
C.O.M
-
-54
0
1.05
0
-1.04
0
.04
0.35
-54
0
2.1
-2.08
0
.07
.35
+48
0
2.1
-2.08
0
.07
.30
0
1.8
5.94
-1.78
-.2
.06
.44
0
0.9
11.88
-.4
-.89
.39
.37
-27
9.99
0
-.33
0
.33
.19
0
5.13
0
-.17
0
.17
F.M. -53.95 -53.91 48.09 6 11.88 -17.01 5.13
474 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
6- Horizontal load for sway:
XA = 4
95.5391.53
= 26.97 t
XB = 4
17.01
= 4.25
475 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
XF = 3
09.48
= 16.03
ΣX = 0
F1 = XA + XB + XF = 47.25 t
7- Final B.M.D. (MF)
MF = Mo + 1
1
MF
F o
= Mo + 125.47
67.0M
= Mo + 0.014 M1
MAC = + 3.15 + .014 (-53.95) = + 2.38 t.m
MCA = - 6.29 + .014 (-53.91) = - 5.53 t.m
MCF = - 6.29 + 0.014 (-48.09) = - 6.96 t.m
MCD = - 18.58 + 0.014 (+6.0) = - 18.50 t.m
476 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
3.098.73
RE= 5.91 t
1.91
4t.m1.66t.m
4t.m16.25
6.67t.m
15.418.52
5.53t.m
20.65
19.6
1.66t
16.25
6.96
1.66
16.25
4t
13.1613.84
1.98
XA=1.98
YA=19.64
2.38t.m
6
Xf=2.32
1.71
1.661.66 1.66t.m2t/m2t/m 3t/m
MDC = - 15.23 + .014 (- 11.88) = - 15.40 t.m
MDB = - 6.43 + 0.014 (+17.01) = - 6.67 t.m
MDE = - 8.8 + .014 ( 5.13) = - 8.73 t.m
477 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
478 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 32:
Draw B.M.D. for the given frame under the shown loading.
Solution:
Neglect the side sway and evaluate the B.M.D. (Mo.D) and
get Fo at point E which prevent the side sway, and solve again the
frame due side sway only (correction of side sway) and get M1D
and F1.Then the final B.M.D. = Mo + 1.1
MF
Fo
1- Moment without side sway
a- Relative stiffness (S or S and D.Fs.)
Joint C
CA : CB
S 5
1 :
8
2
4
3
D.F 0.52 : 0.48
479 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
b- Fixed End Moments
MAC = MCA = 0
M1CB = 64
5
WL
2
6464
25
= -10 t.m
M1CB = 0
Effect of cantilever
M2BC = + 4 t.m
Hence:
MCB = -10 + 2 = -8 t.m
MBC = 4 t.m
c- The Mo.D can be obtained by using the following table.
Joint A C B
Member AC CA CB CD BC BE
480 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
D.F.
F.E.M.
D.M.
C.O.M.
0
1.04
0.52
0
2.08
0.48
-8
1.92
+4
0
+4
-4.0
F.Mo 1.04 2.08 -6.08 +4 +4 -4
d- Horizontal force at E
From free body diagram
481 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
ΣX = 0
Fo – 4 – 12.05 = 0
Fo = 16.05 t
e- Moment due to Side Sway
Tan Y
4
3
Y = 1.33 ∆
482 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
f- Fixed End Moment
MAC = MCA = 2
6
L
EI(1.67 ∆) = -0.40 (EI. ∆)
MCB = + 2
)2(3
L
IE = (1.33 ∆) = 0.125 (EI. ∆)
Assume EI ∆ = 20
Then Assume MAC = MCA = - 8.0 t.m
And = + 2.50 t.m
Joint A C B
Member AC CA CD CB BC BE
D.F.
F.E.M.
D.M.
C.O.M.
-
-8
-
1.43
.52
-8
2.86
0
-
-
-
0.48
+2.5
2.64
- -
F.M. -6.57 -5.14 +5.14
483 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Final bending Moments:
MA = 1.04 + )76.4
05.16( (- 6.57)
= - 21.11 t.m
MCA = - 2.08 + )76.4
05.16( (+ 5.14)
= 15.25 t.m
MCB = - 6.08 + )76.4
05.16( 5.14
= 11.25 t.m
Final Reactions:
YA = 8.26 + )76.4
05.16( (- .64)
= + 6.10 t
YA = 12.05 + )76.4
05.16( (-4.76)
= 4
484 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
YB = 3.74 + )76.4
05.16( (0.64)
= 5.90 ton
Check Σ Y = 0 YA + YB = 8 + 4 0.k
Σ x = 0 YA – 4 = 0 0.k
Example 33:
Draw B.M.D. for the given frame
Solution:
1- S and D.F.
Joint B: BA : BC
S 5
1 :
6
1
D.F .55 : 0.45
Joint C: CB : CD : CE
485 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
S 6
1 :
8
1
4
3:
3
1
4
3
B.F .33 : .49 : .18
2- Fixed End Moments:
MBC = - 4.5 t.m, MCB = + 4.5 t.m
MCE = - 24 t.m
Other moments are equal to zero.
3- Elastic Curve and Sway shape:
Fixed End Moment due to Sway
4- Moments without side sway :
The distribution of moments is according to the following table.
Joint A B C
Member AB BA BC CB CE CD
D.F .55 .45 .44 .18 .49
486 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
F.E.M
D.M
C.O.M
D.M
C.O.M
D.M
C.O.M
0
0
1.24
0
-0.89
0
+.05
0
2.48
0
-1.77
0
+0.09
-4.5
2.02
3.22
-1.45
-0.17
+.08
+4.5
6.44
1.01
-.33
-.73
0.24
-24
3.51
0
-0.18
0
.13
0
9.55
0
-0.5
0
.36
F.M. 0.04 0.80 -0.80 11.13 -20.54 9.41
Determination of Fo
From Σ x = 0 , 4 + YA + XA + XD +Fo = 0
XA = 4
48 = 3 , XD =
3
41.9 = 3.13 t,
Fo = 4 + 3 + 3.13 = 10.13 ton
Correction of Side sway:
487 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
The correction of side sway moments can be correct
according to following table:
Joint A B C
Member AB BA BC CB CE CD
D.F
F.E.M
D.M
C.O.M
D.M
C.O.M
D.M
C.O.M
-
-30
0
4.82
0
-.8
0
0.18
.55
-30
9.63
0
-1.59
0
0.36
.45
12.5
7.87
2.89
-1.30
-.65
0.29
.33
12.5
5.78
3.94
-1.3
-.65
.21
.18
0
3.15
0
-.71
0
.12
.49
-30
8.57
0
-1.93
0
.32
F.M. -25.8 -21.6 21.6 20.48 2.56 -23.04
The final B.M.D. can be drawn as follows
M = Mo + 1
1
MF
Fo
488 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MA = 0.4 + 52.19
13.10 (-25.8) = - 13.02
MBA = -.8 + .52 ( 21.6) = - 10.43
MBC = -.8 + .52 ( 21.6) = - 10.43
MCB = +11.13 + .52 (+ 20.48) = + 21.78
MCD = -20.54 + .52 ( 2.54) = - 19.22
489 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Temperature Effect for Frames without sway:
a- Uniform rise in temp.
In some cases, the temperature variation resulting in an
additional moments at supports. Due to increase of temperature
∆t degree in the shown frame, the different fixed end moments
for each member can be obtain from the geometry of deformed
shape.
MAB = MBA = ABL
EI2
6. ∆1
MBC = MCB = BCL
EI2
6 . ∆2
∆1 = . ∆t. LBC
490 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
∆2 = . ∆t. LBB
For the shown frame
∆1 = . ∆t. L1
∆2 = . ∆t. h1
∆3 = . ∆t. L2
∆4 = . ∆t. (L1+L2)
b- Non uniform rise in tempre. For beams:
The effect can be divided into two stages;
491 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1-Elongation at centre line ∆ = . )2
21(
tt . L
The effect of this elongation can be solved as above in
uniform rise in temperature.
2- Rotation of member for member for free member:
d = EI
dLM .
= dLh
tt.
12
492 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
M = EI h
tt 12
For fixed member AB the restrain of rotation at A and B to
satisfy the fixations create a fixed end moment M equal to;
MAB = + EI. h
tt 12
.
and the bending moment diagram a shown;
IF t1 > t2 MAB = - EI. h
tt 2.
1
and the B.M.D will be as shown;
c- Temperature Effect for Frames with Side sway:
The solution of this type consist of two steps, first step
solve the problem without side – sway, and get Fo. Hence, the
second step; as before, solve the due to sway and get F1.
M = Mo + 1
0
F
F. M1
Example 34:
For the shown frame draw B.M.D due to rise in temp.
∆t = 20O. , EI = 20000 t.m
2
493 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1- Without Side sway
∆1 = . ∆t. (6+10)
∆2 = . ∆t. (10)
∆3 = . ∆t. (6-4)
then get fixed end moment, MO, and F0.
2- Side–Sway, assume the fixed end moment (as before) and
get M1, and F1.
M Final = M0 + 11
1M
F
F
Example 35:
Sketch the elastic Line for the following frames due to uniform
rise in temperature. Sketch B.M.D.
a- Uniform rise in whole frame.
494 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
b- Uniform rise in A B C D E only.
c- Non uniform rise ∆t = 200 frame in t2 – t1 = 20
0
495 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 36 :
Draw B.M. Diagram due to rise in temperature as shown in
figure.
496 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
∆1 = 10–5
2
4020 (4.0) = 1.2 × 10
–3 m
∆2 = 10–5
2
4030 (5.0) = 1.75 × 10
–3 m
∆3 = 10–5
2
3020 (5.0) = 1.25 × 10
–3 m
∆4 = 10–5
2
3020 (10.0) = 2.5 × 10
–3 m
∆5 = ∆4 + 10–5
2
4020 (10.0) = 5.5 × 10
–3 m
MAD = 24
)10000(6 (1.2 × 10
–3) + 10
–5
8.0
2040 (10000) = 2 m.t
MDA = 24
)10000(6 (1.2 × 10
–3) + 10
–5
8.0
2040 (10000) = 7 m.t
MEB=25
)10000(3 (2.5 × 10
–3) - 1.5×0
–5
8.0
2040 (10000) = 1.125m.t
MFC = - 1.5 × 10–5
) - 8.0
2030 (10000) = 1.125m.t
MDE = + 6210
)15000((1.75×10
–3)- 10
–5
0.1
2040 (15000) = -2.505 m.t
MED = 6210
)15000((1.75×10
–3)-1.2×10
–5
0.1
2040 (15000)=-3.495 m.t
MEF = 62)10(
)10000(6(1.75×10
–3)-1.25×10
–3
0.1
2030 (15000)=-1.59 m.t
MFE=62)10(
)10000((1.75×10
–3-1.25×10
–3)+10
–5
0.1
2030 (15000)=-1.05 m.t
497 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
498 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
499 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Frames with Several Degrees of Freedom of Sways:
in all cases of multi – story building frames, vierendeel
girders and any structures, sway take place at more than one
level. For these cases the final solution may be obtained by
superimposing the results of the following cases:
1- Case 1 of no sways get Mo.D and F10, F20, ….. etc F1n.
Where F10,… Dn0 are the horizontal (or vertical) external
force necessary to act at the storey levels as shown in the
following figure ( case of two level of sway or two degree
of freedom).
500 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
2- Case 2 of an arbitrary sway in the first storey case of
M1.D and calculate the horizontal forces at levels (1) and
(2) F11 and F21
3- Case 3 of an arbitrary sway in the second storey (sway2)
as shown in the following figure.
501 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
For this case calculate F12 and F22 from the equation
express the condition that the sum of the horizontal forces at each
level mist be zero.
Now at each level Σx = 0, then:
F10 + X1 F11 + X2 F12 = 0 )
) Get X1 and X2
F20 + X1 F21 + X2 F22 = 0 )
Where X1 is the ratio of the actual Sway at level (1) to the
arbitrary sway in case 2 while X2 is the ratio of the actual sway at
level (2) to arbitrary sway in case(3).
The final bending moment can be obtained from the
following equation:
M = Mo + X1 . M1 + X2. M2
In cases of n degrees of freedom , it is generally required n
sway corrections. For example, the following figure shows case
of three degrees of freedom.
502 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
For this case:
F10 + X1.F11 + X2 F12 + X3 F13 = 0
F20 + X1.F21 + X2 F22 + X3 F23 = 0
F30 + X1.F31 + X2 F32 + X3 F33 = 0
From these equations the values of X1 , X2 , can be
obtained, then, th final moments can be computed as follow.
503 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
M = Mo + X1.M1 + X2.M2 + X3.M3.
Example 37:
For the given frame Draw B.M.D. due to given loading.
Solution:
The frame has two degree of freedom in translation as
follow:
1- Translation of level B E G
2- Translation of level C F
The solution is consist of three cases:
a- Case (1): Fine the B.M.D. (Mo.D) due to given lods
without sway.
504 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
b- Case (2): Find the B.M.D. (M1.D) due to sway of
level B E G, while level C F is prevented from
sway.
c- Case (3): Find the B.M.D. (M2.D) due to sway of
level C F while level B E G is prevented from sway.
1-Stiffness and D.F.
Joint B: BA : BC : BE
S 6
1 :
4
1 :
12
2
D.F. .29 : .42 : .29
Joint C CB : CF
S 4
1 :
12
2
D.F. 0.60 : 0.40
Joint E EB : ED : EG : EF
S 6
1 :
6
1 :
6
1 :
4
1
D.F .4 : .6
Joint G GE : GH
S 6
1
6
1
D.F .5 : .5
505 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
2- case (1): Assume that the frame is prevented from side sway
with the two forces F10 and F20 at the joint G and F. then get the
values of F10 and F20.
Fixed End Moments:
MBE = -15, MEB = + 15
MCF = - 24, MFC = + 24
MEG = - 48, MGE = + 48
The moment distribution is shown in the following tables
506 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Case 1 (Mo. D)
Joint C B E G F
Member CF CB BC BA BE EF ED ED EG GE GH FE FC
D.F
F.E.M.
D.M.
C.O.M.
D.M.
C.O.M
D.M.
C.O.M
D.M.
.40
-24
9.6
-4.8
.66
-2.08
1.74
-.65
.46
.60
0
14.4
3.15
.99
-2.27
2.61
-.49
.68
.42
0
6.3
7.2
-4.55
.5
-.98
1.30
-.80
.29
0
4.35
0
-3.14
0
-.70
0
-.56
.29
-15
4.35
363
-3.14
1.88
-.70
.62
-.56
.22
15
7.26
2.17
3.75
-1.57
1.23
-.35
.39
.34
0
11.22
-7.2
5.78
-3.12
1.90
-.97
.62
.22
0
7.26
0
3.75
0
1.23
0
.39
.22
-48
7.26
-12
3.75
-.90
1.23
-.47
.39
.5
48
-24
3.63
-1.815
1.88
-.49
0.62
-.31
.5
0
-24
0
1.815
0
-.94
0
-.31
0.6
0
-14.4
5.61
-6.25
2.89
-1.93
.95
-1.09
0.4
24
-9.6
4.8
-4.16
.33
1.29
.87
-.73
F.M. -19.07 19.07 8.97 -.05 -8.92 27.88 8.23 12.63 -48.74 27.0 -27.0 -14.22 14.22
Notes: F.M C.O.M.
MAB = 2
MBA +
2
56. = -.30 t.m
507 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MDE = 2
63.12 +
2
39. = 6.51 t.m
MHG = 2
27 +
2
31. = -13.67 t.m
509 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
From Mo. D, we can calculate the F10 and F20 as follows:
From Σx at Level C F:
3-Sway Correction:
Case (2) the displacement ∆1 is due to acting of F11 a point H.
Fixed End Moments:
Assume EI ∆1 = 48
MAB = MAB = 26
6EI.∆1 =
6
1EI ∆1 = 8
510 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MBC = MBC = - 24
6EI ∆1 = -
16
)48(6 = - 18
MEF = MEF = MBC – MCB = - 18
MED = MDE = MGH = MH6 = 6
1EI ∆1 = 8
The moment distribution of Case 2 is according to the
following table:
511 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Case 2 (M1.D)
Joint C B E G F
Member CF CB BC BA BE EB EF ED EG GE GH FE FC
D.F
F.E.M.
D.M.
C.O.M.
D.M.
C.O.M
D.M.
0.4
0
7.2
3.6
-2.28
-1.08
-.98
.6
-18
10.8
2.1
-3.42
-1.365
1.47
.42
-18
4.2
5.4
-2.73
-1.71
0.94
.29
8
2.90
0
-1.89
0
0.65
.29
0
2.90
1.1
-1.89
-0.53
0.65
.22
0
2.2
1.45
-1.07
-0.94
0.62
.34
-18
3.4
5.40
-1.65
-1.59
0.96
.22
8
2.2
0
-1.07
0
0.62
.22
0
2.2
-2
-1.07
-0.28
0.62
.5
0
-4
1.1
-0.55
-0.54
0.27
.5
8
-4
0
-0.55
0
0.27
.60
-18
10.8
1.7
-3.18
-0.82
1.18
.4
0
7.20
3.6
-2.12
-1.14
0.78
F.M. 8.42 -8.42 -11.90 9.66 2.23 2.26 -11.48 9.75 -.053 3.72 3.72 -8.32 8.32
F.E.M. C.O.M.
MAB = 8 + 2
65.089.19.2 = 8.83 t.m
MDE = 8 + 2
62.007.12.2 = 8.88 t.m
512 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MHG = 8 + 2
27.055.04 = 5.86 t.m
514 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
To get f12 and f11 from F12 and f11 from Σx = 0 at levels of and
DEH
515 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
516 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Case (3)
The displacement ∆2 is due to acting of F22 at Joint F
Fixed End Moment
Assume EI ∆2 = 48
MBC = MCB = MEF = MFE = 24
6EI 2 = -
8
3EI ∆2 = -18 t.m
The moment distribution of case (3) is according to the following
table:
The horizontal forces F22 and F12 can be obtained as follows:
Σx = 0 at level CF
F22 = - 8.7
F12 = -10.76
517 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Case (3) (M2.D)
Joint C B E G F
Member CF CB BC BA BE EB EF ED EG GE GH FE FC
D.F
F.E.M.
D.M.
C.O.M.
D.M.
C.O.M
D.M.
.4
0
7.2
3.6
-2.95
-1.26
1.12
.6
-18
10.8
3.78
-4.43
-1.55
1.69
.42
-18
7.56
5.4
-3.10
-2.21
1.27
0.29
0
5.22
0
-2.14
0
.88
.29
0
5.22
1.98
-2.14
-.83
.88
.22
0
3.96
2.61
-1.76
-1.07
.7
.34
-18
5.4
5.4
-2.73
-1.84
.81
.22
0
3.96
0
-1.76
0
.7
.22
0
3.96
0
-1.76
-.25
.7
.5
0
0
1.98
-.5
-.88
.44
.5
0
0
0
-.5
0
.44
.6
-18
10.8
2.7
-3.78
-1.36
1.69
.4
0
7.2
3.6
-2.52
-1.45
1.12
F.M. 7.71 -7.71 -9.1 3.96 5.14 4.84 -10.40 2.90 2.66 1.04 1.04 -7.95 7.95
MAB = 2
96.3 = 1.92 t.m
MDE = 2
90.2 = 1.45 t.m
MHG = 2
04.1 = 0.52 t.m
518 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
From the previous 3 cases we get at the two levels X = O as follows:
F10 + X1 F11 + X2 F12 = 0 (at level BEG)
F20 + X1 F21 + X2 F22 = 0 (at level CF)
6.16 + X1 (17.815) + X2 = (- 10.03) = 0
7.0 + X1 (10.033) + X2 (- 8.07) = 0
0.61 – 1.776 X1 + X2 = 0
1.41 – 2.929 X1 = 0
X1 = 0.48
X2 = 0.246
The Final Moment MF = M0 + X1.M1 + X2.M2
MF = M0 + 0.48M1 + 0.246M2
MAB = - .30 + 0.48 (8.83) + 0.246 (1.92) = 4.425 t.m
MBA = - .05 + 0.48 (-9.66) + 0.246 (3.96) = 5.56 t.m
MBC = + 8.97 + 0.48 (-11.90) + 0.246 (-9.1) = 1.0194 t.m
MCB = + 19.07 + 0.48 (-8.42) + 0.246 (-7.71) = 13.13 t.m
MBE = - 8.92 + 0.48 (-2.33) + 0.246 (5.14) = - 6.58 t.m
MEB =+27.88 - 0.48(-2.26)+0.246(4.84) = + 30.155 t.m
MFC = + 14.22 - 0.48(8.32) + 0.246(7.95) = 20.17 t.m
MDE = 6.51 - 0.48 (8.88) + 0.246(7.95) = 20.17 t.m
MED = 12.63 - 0.48 (9.75) + 0.246 (2.90) = 18.02 t.m
MEF =+8.23 - 0.48 (-11.48) + 0.246 (-10.40) = 0.161 t.m
MEG =- 48.74 - 0.48 (-0.53) + 0.246 (2.66) = -48.34 t.m
MGE = 27.0 - 0.48 (-3.72) + 0.246 (1.04) = 25.33 t.m
MHG =- 13.67 - 0.48 (5.86) + 0.246 (0.52) = -10.7 t.m
519 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Frame with n – degree of freedom of Side sway:
Boundary condition:
The sum of the forces at each level will equal to zero, hence;
F10 + X1.F11 + X2F12 + …. + XnF1n = 0
520 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
F20 + X1.F21 + X2F22 + …. + XnF2n = 0
: :
Fn0 + X1Fn1 + X2Fn2 + …. + XnFnn = 0
Solving the above equations to et , X1, X2, …… Xn.
Hence the final bending moment is
M = MO + X1. M1 + X2M2 + …. + XnMn.
Influence Lines by Moment Distribution:
The principle of unit displacement is valid to all stru – ctures either
determinate or indeterminate. The influence lines for inderminate beams
and frames can be solved very easy by the method of moment
distribution. In case of internal forces; M,Q,N; we apply by a unit internal
relative displacement.While for external forces; as reactions, we apply a
unit external displacement. Considering, as an example. The shown fixed
beam;
a- To draw I.L.MA
1- Produce a unit rotation = 1 rad. At A and direction of MA
(-ve moment), keeping all other joints fixes.
521 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
2- Obtain fixed end moment at A.
at A
MA = L
EI4.1
And at B
MB = L
EI2.1
Hence the bending moment diagram can be obtained for this
simple case, and the B.M.D will be used to determine the elastic curve by
using the conjugate beam method. Similarly the I.L.MB can be drawn.
The influence line of any of the internal forces at any section can be
obtained in terms of I.L.MA & I.L.MB.
522 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Case of Continuous Beam:
To draw the influence line of bending moment at B, as an example,
for the given continuous beam.
523 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
procedures (For beams or Frames)
Produce a unit relative rotation at B just to right of B as shown in
the previous fig. , and keeping all other joints fixed. The obtained
moment will be F.E.Ms; as follows;
MBC = L
4EI
MCB =
bcL
2EI
Notice that the unit relative rotation can be produce just to left of
B, in which case F.E.Ms will be.
MBA =
BAL
3EI
The unit relative rotation can also be divided in any arbitrary
suitable ratio between BA, to the levt; and BC; to the right;
2- Get the final B.M.D for all the beam by moment distribution
method as shown in the previous fig (b).
3- To obtain the elastic line, we use the conjugate beam method as
shown in fig . (c), then draw the elastic curve.
4- The above procedures are used in case of frames without sway. In
case of frames having side sway we must obtain the final B.M.D
due to assumed init displacement after making the sway
correction.
524 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
5- To obtain I.L.XA produce a unit horizontal translation at support A in
the direction of XA (assumed). Support A translate without rotation,
while all other joints and supports will remain fixed ; (except support c
wil remain always hinged;). The developing F.E.Ms will be.
Mad = Mda = + ad2L
6EI
Similarly , complete the above procedures.
5- To obtain I.L.YA in the shown frame ,
produce a unit vertical upward translation
at support A without rotation.
This causes a unit translation upward at D and G, in the some time.
For this case F.E.Ms will be;
Mgh = Mhg = gh2L
6EI.1
Similarly;
Mgh = Mhg = de2L
6EI.1
7- To obtain I.L. for N.G.M. at any section;
I.L.for normal force N, required to produce a unit relative axial;
horizontal or vertical; translation. Due to this unit translation at a certain
joint calculate the dived end moment. All other joint are kept fixed. For
an example,
I.L.NDE,
525 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Produce unit horizontal translation at D to right , then, F.E.Ms as
follows;
Mad = Mda = 12L
6EI.1
Mdg = Mgd = s2L
6EI.1
Other method by produce a unit translation at E to right , then joint
F translate unit displacement also , while D is fixed.
I.L.Q
The influence line for shearing force at any section ( say) I.L.Qn,
can be obtained by produce a unit relative vertical translation at the
section. Then calculate the F.E.Ms. notice that at a section a unit vertical
drop in the deflection line.
I.L.M
Produce a unit relative rotation at the section.
526 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 1:
For the shown continuous beam Draw I.L. for the followings;
1- I.L.MB
2- I.L.Mn
3- I.L.YA
4- I.L.YB
5- I.L.Qn
Solution
1- I.L.MB
a- Produce a unit angle of rotation at BA Just to left of B.
F.E.MB4
assume EI = 1
F.E.Ms = 0.25 Multiplied
by 100 equals to 25 use the
conjufate beam method to draw
elastic curve as follow;
θ A = rad(100)EI
EI30
= 100
30= 0.3 RAD
= - 1.067
527 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
y2 = (-30 × 8 + 38.40 )
100
1
= - 1.33
θ Br = 10040
= 0.40 rad
θ c = 100
20= 0.20 rad
y3 = (- 0.20×4 + 15× 5
4) =
100
1
The I.L.MB can be obtained as shown;
Nots:
YA = MB , Mn = YA (6)
I.L.YA = I.L.YA0 + I.L. 12
MB
I.L.Mn = I.L.Mn0 + 2
1I.LMB
I.L.YB = I.L.YB0 + 12
1I.LMB
For beam BA and =
I.L.YBO -8
1 I.L.MB for beam Bc.
Where I.L.YAO is the influence line of YA at Simple beam AB and
I.Lmn0 is the influence line for Mn at simple beam Ab as follows;
I.L.Mn
The influence line of Mn can be obtained by knowing I.L.YB and
I.L.MnO as follows.
528 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
I.L.Mn = I.L.Mn0 + 2
1I.LMB
I.L.YA = I.L.YA0 + 12
1I.LMB
Similarly:
529 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Example 2:
For the given frame, draw the influence lines for;
1- I.L.YA
2- I.L.YB
3- I.L.Me-d
4- I.L.Qn
5- I.L.Md
6- I.L.Mn
Solution:
Solution
Producing a unit vertical
Translation at support A.
MFD. =MFED = -6EI / 100
Put EI 1000
530 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
MFDE = MFED = - 60
1000y1 = - 94.91(2.5)
+ (2/6) (8.295)
(2.5)2 + (2.5)
2/2
(24.89)
= - 39.19
1000y2 = - 94.91(5) -
(18.12/6) (5)2+
(2/6) 16.59* (5)2+
+ (52/2)16.59
= 20.20
1000y3 = - 94.91(7.5) -
(27.31/6) (7.5)2+
(2/6)(24.89)(7.5)2
(7.52/2)(8.295)
= 69.63
1000y4 = 33.92(2.5) +2.52/6
(1.70) - (2/6) (2.5)2
(3.39)-(2.52/2)*10.18
= 47.70
1000y5 = 33.92(5) + (52/6)*3.39
(2/6)*52 (6.79)-(5
2/2)
(6.79)
= 42.27
1000y6 = 33.92(7.5) +7.52/6
(5.09)- (2/6)*7.52
(10.18)-(7.52/2)3.39
= 15.90
I. L. YB
MF = 6EI / L2
EI = 1000
MF = + 60
1000y1 = 43.82(2.5) + (2.52)/6
(12.94)- (2/6)*2.52
(9.76)-(2.52/2)*29.27
=11.23
1000y2 = 43.82(5) +52/6
531 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
(25.88)- (2/6)*52
(19.51)- (52/2)*19.51
- (52/2)*19.51
= -79.53
1000y3 = 43.82(7.5) +7.52/6
(38.82)- (2/6)7.52
(29.27)-7.52/2
(9.76)
= -130.73
1000y4 = - 92.40(2.5) -2.52/6
(14.62)+ (2/6)14.24
(2.5)2+2.5
2/2
(42.72)
= -83.06
1000y5 = 92.40(5) -52/6
(29.24)+ (2/6)2 *8.48
(5)2+ (5
2/2)*28.48
=9.50
1000y6 = - 92.40(7.5) -7.52/6
(43.86)+ (2/6)*42.72
(7.5)2+ (7.5
2/2)*14.24
= 97.31
I. L. Y E-D
MED = 4EI / L
MDE = 2EI / L
EI = 100
MED = 60
MDE = 20
100y1 = - 9.63(2.5) -2/6
(2.41)(2.5)2
-7.22(2.52/2)
6.87(2.52/6)
= -44.4812
100y2 = - 9.63(5) -2/6
(4.82)(5)2
-4.82(52/2)
+13.74(52/6)
= -91.316
532 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
100y3 = - 9.63(7.5) – (3/6)*7.22
(7.5)2-2.41(7.5
2/2)
+ (20.61/6)*7.52
= -82.1625
100y4 = -24.47(2.5)-(1.25/6)*
(2.5)2+ (2/6)*2.45
(2.5)2+ (2.5
2/2)
(7.34)
= -34.435
100y5 = - 24.47(5) – (2.45/6)*
(5)2+4.9(2/6) (5)
2
+4.9(52/2)
= 31.475
100y6 = - 24.47(7.5) -3.68/6
(7.5)2+7.34(2/6) (7.5)
2
+2.45(7.5)2/2
= -11.4937
I. L. Q N
From n-c
Qn = ya
I. L.Qn = L.L.ya
From d-n
Qn = ya – 1
I.L.Qn = I.L.ya – 1
I. L. d-e
MDE = -4EI / L
MED = -2EI / L
EI = 100
MDE = -40
MED = -20
100y1 = - 63.73(2.5) -
(2.38/6)*2.52+
2/6(5.96) (2.5)2
+17.90(2.5)2/2
= -93.458
533 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
1000y2 = - 63.7333(5) -
(4.75/6)*52+11.94
(2/6)*52+11.94
+ (5)2/2
= -89.705
100y3 = -63.733(7.5) – (7.13/6)
(7.5)2+17.90(2/6)
(7.5)+(5.97/2)
(7.5)2
= -41.310
100y4 = 8.88(2.5) + (0.42/6)
(2.5)2-(2/6)*1.14
(2.5)2-3.42(2.5)
2/2
= 9.575
100y5 = 8.88(5) + (.85/6)*
(5)2-2.28(2/6) (5)
2
-2.28(52/2)
= 0.442
100y6 = 8.88(7.5) (1.26/6)
(7.5)2-(1.14/2)(5)
2
= 0.038
534 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
535 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
Problems
1- Using Moment distribution Method to draw B.M.D. and S.F.D. for
the following indeterminate beams due to given lodes, settlement,
and rise in temperature sketch elastic curve.
2- Draw B.M.D., S.F.D., and N.F.D. for the following frames, sketch
elastic curve.
3- Draw B.M.D., S.F.D., N.F.D. for the following frames due to given
loads and settlements. Sketch the elastic curve for each case.
536 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
537 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
4- Draw B.M., S.F. and N.F.Ds for the following frames.
4- Draw B.M.D for the following structure due to shown loads
and rise in temperature. Sketch the elastic curve for each
case.
538 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
5- Draw B.M.D. for the following structures due to given loads and
sketch the elastic curve.
539 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
540 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
541 Chapter (7) - THE
MOMENT DISTRIBUTION
METHOD
8 Approximate Analysis of
Statically
Indeterminate Structures
1. Introduction
In this chapter we will present some of the approximate methods
used to analyze statically indeterminate trusses and frames. These
methods were developed on the basis of structural behavior and their
accuracy in most cases compares favorably with more exact methods of
analysis. Although not all types of structural forms will be discussed here,
it is hoped that enough insight is gained from the study of these methods
so that one can judge what would be the best approximations to make
when performing an approximate force analysis of a statically
indeterminate structure.
If a model used to represent a structure is statically indeterminate,
then the analysis of it must satisfy both the conditions of equilibrium and
compatibility of displacement at the joints. As will be shown in later
chapters of this text, the compatibility conditions can be related to the
loads, provided we know the material's modulus of elasticity and the size
and shape of the members. For design, however, we will not know a
member's size, and so an analysis that provides further simplifying
assumptions for modeling the structure must be made. This analysis is
called an approximate analysis, and throughout this chapter, we will use it
to simplify the model of a statically indeterminate structure to one that is
statically determinate. By performing an approximate analysis, a
preliminary design of the members of a structure can be made, and once
this is complete, the more exact indeterminate analysis can then be
543
Approximate
performed and the design refined. An approximate analysis also provides
insight as to a structure's behavior under load and is beneficial when
checking an exact analysis, or when time, money, or capabilities are not
available for performing a more exact analysis.
Realize that in a general sense, all methods of structural analysis are
approximate, simply because the conditions of loading, geometry, material
behavior, and joint resistance at the supports are never known exactly,
2. Trusses
A common type of truss often used for lateral bracing of a building or
for the top and bottom cords of a bridge is shown in Fig. l-a. When used for
this purpose, this truss is not considered a primary element for the support
of the structure, and as a result it is often analyzed by approximate methods.
In the case shown, it will be noticed that if a diagonal is removed from each
of the three panels, it will render the truss statically determinate. Hence, the
truss is statically indeterminate to the third degree,* and therefore we must
make three assumptions regarding the bar forces in order to reduce the truss
to one that is statically determinate. These assumptions can be made with
regard to the cross diagonals,
Realizing that when one diagonal in a panel is in tension the
P0P0a
b
R1 R2R1
R1V=
FIG.1 (a) , (b)
F1
FaFb
F2
544
Approximate
responding cross diagonal will be in compression. This is evident from i.g.
7-6, where the "panel shear" V is carried by the vertical component of
tensile force in member (a) and the vertical component of compressive
force in member b. Two methods of analysis are generally acceptable.
Method 1: If the diagonals are intentionally designed to
be long and sender, it is reasonable to assume
that they cannot support a compressive force,
otherwise, they may easily buckle the tension
diagonal, whereas the compressive diagonal is
assumed to be a zero-force member.
Method 2: If the diagonal members are intended to be constructed from
large rolled sections such as angles or channels, they may be
equally capable of supporting a tensile and compressive
force. Hence, we can assume that the tension and
compression diagonals each carry half the panel shear.
Both of these methods of approximate analysis are illustrated
numerically in the following examples.
Example 1:
Determine (approximately) the forces in the members of the truss
shown in Fig. Assume the diagonals are slender and there force will not
support a compressive force.
545
Approximate
2t2t2t
3t3t
1 3 5 7 9
642 BA
4*3=12m
Fig.(2-a)
3m
Solution
Reactions;
From symmetry yA = yB = 3 t
The truss is statically to the forth degree thus we can assume the
compression diagonals sustains zero forces, i.e. Can be omitted from the
truss and the remaining truss can easily analyzed.
The zero members are (A-2 , 4-5, 6-13} The remaining member
forces are easily found by method of joints, and are shown in Fig. 2-a-b
2t2t2t
3t3t
0 -3t4.243-1t1.4141.4141t
4.243t
-3t
-3t1 3 -4t 5 -4t 7 -3t 9
642 BA
4*3=12m
Fig.(2-b)
3m
546
Approximate
Example 2:
Determine (approximately ) the forces m the members of the truss
shown in Fig. 3-a. the diagonals are to be designed to support both
tension and compression forces, and there fore each is assumed to
carry half the panel shear. The support reactions have been computed.
5t10t
F E D
CBA3m3m
4m
5t
Fig.(3-a)
10t
Solution
By inspection the truss is statically indeterminate to the second
degree. The two assumptions require the tensile and compressive
diagonals to carry equal forces, that is , FFB=FAE = F.for vertical
section through the left panel, Fig.3-b we have
Fig.(3-c)Fig.(3-b)
F
F
F
F
D
FCD
C
ED
DB
EC
BC
=F
=F
F
F
F
F
AE
FB
AE
AB
=F
=F
F
F
A
AF
5t
10t
0
0
0
0
5t
547
Approximate
0fY )5/4(F2510
t125.3F)5
8(F5
So that
FFB )T(125.3
FAE )C(125.3
At joint F
0FΧ FFE sin125.3
)C(275.1)5
3(125.3
at joint A
F X= 0 FAB sinFAE
)T(87.1)5
3(125.3
F Y=0 )T(5.7)5
4(125.35FAF
A vertical section throught the right panel is shown in Fig. 3-c
F y=0
5)5
4(F2
FDB )T(125.3
FDB )C(125.3
548
Approximate
At joints D
F X=0 FDB = )C(t875.1)5
3(125.3
F y=0 FCD = )C(t5.2)5
4(125.3
At joint C
F X=0 FBC = 3.125 ( )T(t875.1)5
3
3. Building Frames Subjected to Vertical Loads
Building frames often consist of girders that are rigidly connected to
columns so that the entire structure is better able to resist the effects of
lateral forces due to wind and earthquake. An example of such a rigid
framework, often called a building bent, is shown in Fig. 4. In this section
we will establish a method for analyzing (approximately) the forces in
building frames due to vertical loads, and in Sees. 5 and 6 an approximate
analysis for frames subjected to lateral loads will be presented. In all these
cases it should be noticed that most of the simplifying assumptions made to
reduce a frame from a statically indeterminate structure to one that is
statically determinate are based on the way the structure deforms under load.
3.1 Assumptions for Approximate Analysis
Consider a typical girder located within a building bent and
subjected to a uniform vertical load, as shown in Fig. 5-a. The column
supports at A and B will each exert three reactions on the girder, and
therefore the girder will be statically indeterminate to the third degree.
549
Approximate
To make the girder statically determinate, an approximate analysis
will therefore require three assumptions. If the columns are extremely
stiff, no
Fig.4 Typical Building Frame
L
W
(c)
W
0.21L0.21L
LL
momentsPoints of zero Girder
W stiffstiffcolumn column
(a)(b)
A B
550
Approximate
rotation at A and B will occur, and the deflection curve for the girder will
look like that shown in Fig. 5-b. Using one of the known methods an
exact analysis reveals that for this case inflection points, or zero moment
occur at 0.211 from each support. If, however, the column connections
at A and B are very flexible, then like a simply supported beam, zero
moment will occur at the supports, Fig. 5-c. In reality, however, the
columns will provide some flexibility at the supports, and therefore we
will assume that zero moment occurs at the average point between the
above two extremes, i .e., at (0.211+0)/2= 0.11 from each support, Fig.
5-d. Furthermore, an exact analysis of frames supporting vertical loads
indicate- that the axial forces in the girder are negligible.
As a result of the above discussion, each girder of length/may
be modeled by a simply-supported span of length 0.81 resting on
two cantilevered ends, each having a length of 0.11, Fig. 5-e. The i
olio wing three assumptions are incorporated in this model:
1 - There is zero moment in the girder,o. 1 Lfrom the left support.
0.8L
L
momentsPoints of zero Assume
WW
0.1L0.1L
0.1L0.1L
Approximate case Model
A B
(e)(d)
551
Approximate
There is zero moment in the girder,o. 1 Lfrom the right support.
The girder does not support an axial force.
By using static's, the internal loadings in the girders can now
be obtained. The following example illustrates this numerically.
Example 3
Determine (approximately) and exactly the bending moment
diagram for the following frame.
12m
W
DC
A B
Fig. (6-a)
552
Approximate
Fig. (6-c)
Approximate Solution
Assume intermediate hinges as
Shown in Fig.6-b
1.29.61.2
FE
Fig. (6-b)
553
Approximate
19.419.4
19.4
9.72 9.72
19.4
34.56
+
-
-
-
-
Fig. (6-d) 4.
Portal Frames
4.1. Frames
Portal frames are frequently used over the entrance of a bridge and
as a main element in building design in order to transfer horizontal forces
applied at their top joints to the foundation. On bridges, these forces are
caused by wind, earthquake, and unbalanced traffic loading on the bridge
deck. Portals can be pin-supported, fixed-supported, or supported by
partial fixity. The approximate analysis of each case will now be discussed
for a simple three-member portal,
4.2. Pin-Supported
A pin-supported type of portal consists of pin-supported vertical
members having equal length and size and a rigidly connected horizontal
girder, Fig. 7-a. Since four unknowns exist at the supports but only three
equilibrium equations are available for solution, this structure is statically
indeterminate to the first degree. Consequently, only one assumption must
be made to reduce the frame to one that is statically determinate.
The elastic deflection of the portal is shown in Fig. 7-b. This
554
Approximate
diagram indicates that a point of inflection, that is where the moment
changes from positive bending to negative bending, is located
approximately at the girder's midpoint. Since the moment in the girder is
zero at this point, we can assume a hinge exists there and then proceed to
determine the reactions at the supports using statics. If this is done, it is
found that the horizontal reactions at the base of each column are equal
and the other reactions are those indicated in Fig. 7-c. Furthermore , the
moment diagrams for this frame are indicated in Fig. 7-d.
h
L
h
assumed hinge
PP
Fig. (7-b)Fig. (7-a)
hh
L/2 L/2
Ph/2
Ph/2Ph/2
P/2P/2
P/2P/2P
Fig. (7-c)
555
Approximate
Ph/2
Ph/2
Ph/2
Ph/2
B. M. D
+
+
-
-
Fig. (7-c)
4.3. Fixed-Supported
Portals with two fixed supports, Fig. 8-a are statically
indeterminate to the third degree since there is a total of six unknown at
the supports. If the vertical members have equal lengths and cross
sectional areas, the frame will deflect as shown in Fig. 8-b. For this
case we will assume points of inflection occur at the midpoints of all
three members, and therefore hinges are placed at these points. The
reactions and moment diagrams for each member can therefore be
determined by dismembering the frame at the hinges and applying the
equations of equilibrium to each of the four parts. The results are shown
in Fig. 8-c. Note that, as in the case of the pin connected portal, the
horizontal reactions at the base of each column are equal. The moment
diagrams for this frame are indicated in Fig. 8-d.
4.4. Partial Fixity
556
Approximate
Since it is both difficult and costly to construct a perfectly fixed
support or foundation for a portal frame, it is conservative and somewhat
realistic to assume a slight rotation occurs at the supports, Fig. 9-a. As a
result, the points of inflection on the columns lie somewhere between the
case of having a pin supported portal, Fig. 7-a9 where the "inflection
points" are at the supports (base of columns), and a fixed supported portal,
Fig. 8-a, where the inflection points are at the center of the columns. Many
engineers arbitrarily define the location at h/3, Fig. 9, and therefore place
hinges at these points, and also at the center of the girder. Fig. 9-b shows
B.M.D.
h
L
h
assumed hinge
PP
Fig. (7-b) Fig. (8-a)
557
Approximate
h/2
L/2 L/2
Ph/2L
P/2
P/2
P/2P
Ph/2L
Ph/2LPh/2L
P/2
Ph/2L
P/2
Ph/2L
P/2
Ph/2L
Ph/4
P/2
Ph/4
Ph/2L
h/2
Fig. (7-c)
Ph/4
Ph/4
Ph/4
Ph/4
B. M. D
+
+
-
-
+
-
Ph/4 Ph/4
Fig. (7-d)
558
Approximate
h
L
assumed hinge
P
h/3h/3
00
partial fixation
Fig. (9-a)
M
B. M. D
+
+
-
-
+
-
M/2 M/2
MM
M
Fig. (9-b) 4.5.
Trusses
When a portal is used to span large distances, a truss may be
used in place of the horizontal girder. Such a structure is used on large
bridges and as transverse bents auditoriums . A typical example is
shown in fig 10-a.in all cases, the suspended truss is assumed to be
pin connected at its points of attachment to the columns. Furthermore,
the truss keeps the columns straight within the region of attachment
when the portal is subjected to the side sway A, Fig. 10-b.
Consequently, we can analyze trussed portals using the same
assumptions as those used for portal frames, for pin supported columns,
assume the horizontal reactions are equal as in Fig. For fixed
559
Approximate
supported columns, assume the horizontal reactions are equal and an
inflection point (or hinge) occurs on each column, measured midway
between the base of the column and the lowest point of truss member
connection to the column. See Fig. S-c and Fig. 10-b
The following example illustrates how to determine the forces in
the members of a trussed portal using the approximate method of analysis
described above
P/2
Fig. (10-a)
L
P
Fig. (10-b)
L
P
assumed hinge
h
h/2
P/2
5. Lateral Loads on Building Frames
5.1. Portal Method
In Sec. 4 we discussed the action of lateral loads on portal frames
and found that for a frame fixed supported at its base, points of
inflection occur at approximately the center of each girder and column
and the columns carry equal shear loads, fig.8. A building bent deflects
in the same way as a portal frame, fig. 11-a, and therefore it would be
appropriate to assume inflection points occur at the center of the
columns and girders. If we consider each bay of the frame to be
composed of a series. If we consider each bay of the frame to be
composed of a series of portals, fig. 11-b, then as further assumption the
interior columns would represent the effect of two portal columns
560
Approximate
P
Fig. (11-a)
X3X2X1
=inflection point
X3=VX2/2=V
Fig. (11-b)
X2/2=VX1=V
and
would therefore carry twice the shear V as the two exterior columns . In
summary, then the portal method for analyzing fixed supported
building frames requires the following assumptions:
1. A hinge is placed at the center of each girder since
this is assumed u = he a point o* zero moment
2. A hinge is placed at the center of each column s ince
this is assumed to be a point of zero moment.
3. At a given floor level the shear at the interior column
hinges is twice that at the exterior column hinges since
the frame is considered to be a superposition of portals.
561
Approximate
Fig. (12-a)
A C E H
16.0m16.0m16.0m
120 ton B D F G
KJ
O
L
Fig. (12-b)
120 ton
KJ
V L 2V K2V J
LyKyJyIy
These assumptions provide an adequate reduction of the frame to one
that is statically determinate yet stable under loading.
By comparison with the more exact statically determinate
analysis, the portal method is most suitable for buildings having low
elevation and uniform framing. The reason for this has to do with the
structure's action under load In this regard, consider the frame as
acting l ike cantilevered beam that is fixed to the ground. Recall from
mechanics o f materials that shear resistance becomes more important in
the design of short beams whereas bedding is more important if the
beam is long (See. 6. )The portal method accounts for this effect, listed
as assumption 3 above.
The following examples illustrate how to apply the portal method
to analyze a building bent.
Example 5
Determine (approximately) the reactions at the base of the
columns of the frame shown in Fig. 13-a, use the portal method of
analysis.
Solution
Applying the two assumptions of the portal method, we place
562
Approximate
2t
12 ton
Iy=1.5t
6m
MMx=10t8m 10 ton
6m
Jy=0
Iy=1.5t
8m 8m
N
Nx=6t
Ny=1.5t
4t
Fig. (13-c) Fig. (13-d)
6t
6m
Ky=0
1.5t
8m 8m
O
Ox=2t
Ox=1.5t
4t
Fig. (13-e)
8m
6m
Ly 1.5t
2t
2t
1.5t
Fig. (13-f)
hinges at the centers of the girders and columns of the frame. The
locations of these points are indicated by the letters I through O in Fig.
13-a. A section through the column hinges at I, J. K, L yields the free
body diagram shown in Fig. 13-b. Here the third assumption regarding
the column shears. We require
;0Fx 1200 – 6V = 0 v=2t
Using this result, we can now proceed to dismember the frame at
the hinges and determine their reactions. As general rule, always start this
analysis at the corner where the horizontal load is applied. Hence, the
free-body diagram of segment IBM is shown in Fig. 13-c. The three
reaction components at the hinges Iy, Mx and My are determined by
applying ,0Fy .0Fy
The adjacent MJN is analyzed next Fig 13-d followed by segment NKO,
Fig. 13-e, finally segment OL, Fig. 13-f. Using these results, the free
body diagrams of the columns with their support reactions are shown in
Fig. 13-g.
Ax=2t
Ay=1.5t
6m
Fig. (13-g)
2 t
1.5t
Mx=12t.m
Cx=2t
6m
4 t
Mc=24t.m
Cx=2t
6m
4 t
ME=24t.m
Hx=2t
6m
4 t
MH=12t.m
1.5t
Hy
563
Approximate
B CA
20 t
30t
D E F
G H IJ S
M N
PQ
O
J K L
5m
5m
8m8m
Fig. (14-a)
20 t G H IJ S
V
PyOyQy
2VV
2.5m
V
KyJyLy
2VV
3m
5m
30t
20t
Fig. (14-b)
Example 6
Determine (approximately) the reactions at the base of the columns
of the frame shown in fig. 14-a. Use the portal method of analysis.
Solution
First hinges are placed at the centers of the girders and columns of
the frame. The locations of these points are indicated by the letters J
through S in Fig. 14-a. A section through the hinges at O, P, Q and J, K,
L yield the free body diagrams in fig 14-b . The column shears are
calculated as follows:
Using these results, we can now proceed to analyze each part the
frame. The analysis starts with the corner segment OGR, 14-c. The three
564
Approximate
4m4m
S
Sx=5t
Sy=3.125t12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t
12.5t12.5t
12.5t
12.5t
12.5t 12.5t12.5t
12.5t
12.5t
12.5t
12.5t 12.5t
12.5t12.5t
12.5t
12.5t12.5t
12.5t
12.5t
12.5t12.5t
12.5t
12.5t
12.5t12.5t
12.5t
12.5t
12.5t
12.5t
unknowns Oy. Rx and Rx have been calculated using the equations of
equilibrium. With these results segment OJM is analyzed next, fig. 14-d
then segment JA Fig. 14-e ; RPS Fig . 14-h PMNK , Fig 14-g; and KB,
Fig 14-h complete this example and analysze segments SIQ then QNL,
and finally LC, and show that Cx = 12.5 t , Cy = 15.625 t , and Mc = 37.5
t.m.
B.M.D
12.5t12.5t
12.5t12.5t
12.5t 12.5t
12.5t
50t50t
50t
37.5
37.5
7525
50t37.5
37.5 75
565
Approximate
(b)
(C)(T)
beam
(a)
M
building frame
Fig. (15.a,b)
6- Lateral Loads on Building Frames
6-1 Cantilever Method
The cantilever method assumes that the stress in a column is
proportional to its distance from the centered of all the column areas at a
given floor level. This assumption is based on the same action as a
cantilevered beam subjected to a transverse load. It may be recalled from
mechanics of materials that such a loading causes a bending stress in the
in summary , then using the cantilever method , the following
566
Approximate
assumptions apply to a fixed supported frame.
1- A hinge is place at the center of each girder sing this is
assumed to be a point of Zero moment.
2- A hinge is placed at the center of each column since this is
assumed to be a point of Zero moment.
3- The axial stress in a column is proportional to its distance
from the centroid of the cross sectional area of the columns
at a given floor level. Since stress equals per area, then in
the special beam that vanes linearly from the beam's
neutral axis, Fig. 15-a. In a similar manner the lateral loads
on a frame tend to tip the frame over, or cause a rotation of
the frame about a "neutral axis" lying in a horizontal plan
that passes through the columns at each floor level. To
counteract this tipping, the axial forces (or stress) in the
columns will be tensile on one side of the neutral axis and
compressive on the other side, Fig. 15-b. Like the
cantilevered beam, it therefore seems reasonable to assume
this axial stress has a linear variation from the centered of the
column areas or neutral axis. The cantilever method is
therefore appropriate if the frame is tall and slender, or has
columns with different cross-sectional areas. Case of the
columns having equal cross sectional areas, the force in
a column is also proportional to its distance from the
centroid of the column areas.
These three assumptions reduce the frame to one that is both stable
and statically determinate
567
Approximate
The following examples illustrate how to apply the cantilever
method to analyze a building bent.
Example 7
Determine (approximately) the reactions at the base of the columns
of the frame shown in Fig. 16-a. The columns are assumed to have equal
cross-sectional areas. Use the cantilever method of analysis.
Solution
First hinges placed at the midpoints of the columns and girders.
The locations of these points are indicated by letters G through L in Fig.
16-a.
The centroid of the columns' cross-sectional area can be determined by
inspection, Fig. 16-b, ur analytically as follows;
m3AA
)A(6)A(0
A
AXX
The axial force in each column is thus proportional to its distance
6m
3
144,46
4m
4m
15t
30tI
J
KH
LG
EB
DC
(b)
(a)
FA
568
Approximate
from this point. Hence, a section through the hinges H and K at the top
story yields the free-body diagram shown in Fig. 16-c. Note how the
column to the left of the centered must be subjected to tension and the
one of the right is subjected to compression. This is necessary in order to
counteract the tipping caused by the 30 ton force. Summing moments
about the neutral axis (NA) we have :
0M NA 0Hy3)2(30
The unknowns can be related by proportional triangles, Fig. 16-c
that is ,
3
K
3
H yy or Hy = Ky
Thus,
Hy = Ky = 10 ton
3m3m
4m
2m
3m3m
2m
30t
30t
15t
KxHx
LxGx
Hy Ky
NA
NA
(c)
(d)
Gy Ly
569
Approximate
In a similar manner, using a section of the frame through the hinges at G
and Fig. 16-d, we have
0M NA 30(6) + 15(2)-3Gy – 3 Ly =0
Since
3
L
3
G yy or Gy = Ly
Gy = Ly 35 =ton
Each part of the frame can now be analyzed using the above
results. As Examples 5 to 6 , we begin at the upper corner where the
applying loading occurs, i.e ., segment HCI, Fig 16-a . Applying of
equilibrium 0F,0M xI , 0Fy , yields the results for HX , IX
and Iy shown in the free-body diagram in fig, 16-f, followed by HJG ,
Fig. 16-g, then KJL, Fig . 16-h and bottom portions of the columns, Fig.
16-i
570
Approximate
30
30
30
30
30
45
30
45 45
45
75
30
3m
2m
Kx=15t
Ky=10t
10t
15t
10
15
3m
2.5t
7.5t
Lx=22.5t
Ly=35t
35t
22.5t
Fx=22.5t
Mf=45t.m
Fy=35tAy=35t
MA=45t.m.
Ax=22.5t
2m
22.5t
35t
Gy=35t
G=1.5tJy=25t
Jx=7.5t3m
2m
15t10t
I
Ix=15t3m
Iy=10t
30t
Hx=15t
Hy=10t
2m
2m
2m
2m
571
Approximate
Example 8
Show how to determine (approximately) the reactions at base of
the columns of the frame shown in fig h. 17-a . The columns have the
cross-sectional area shown in Fig. 17-b Use the cantilever method of
analysis.
Solution
First hinges are assumed to exist at the centers of the girders and
columns of the frame. The locations of these points are indicated by the
letters E through R in Fig. 17-a . The centroid of the columns' cross-
sectional area is determined from Fig. 17-b as follows:
X = m53.28106810
)10(60)8(20)10(0
A
AX
DCBA
QP
12m L 10in2
M 8 in
I J
N 6 in
K
O 10 in
H 10 in6 inG8in10 in16m E
(a)
8t
10t
2
2 2
22
22
25m15m20m
(b)
25m15m20m
X
10 in6 in8 in10 in2222
572
Approximate
Here the columns have different cross- sectional area , so the axial
stress in a column is proportional to its distance from the neutral axis,
located at X = 28.53m . Hence, a section through the hinges at L, M, N,
O yields the free=body diagram shown in Fig .17-c. Note how the
columns to the left of the centroid are subjected to tension and those on
the right are
Subjected to compression. Why? Summing moments about the neutral
axis, we have
;0M NA
0)47.31(O)47.6(N)53.8(M)53.28(L)6(8 yyyy (1)
8t
8t
10t
Fy=.867t
Oy
OxNx
Ny
Mx
MyLy
Lx
Hx
Hy=4.001tGy=.493tEy=.867t
Ex Fx G
6.478.53
31.47m28.53m
6m
12m
8m
31.47m28.53m
6.478.53
(C)
(d)
Fig. (17-c,d)
573
Approximate
Since any columns stress is proportional to its distance the
neutral axis, we can relate the column stresses by proportional triangles .
Expressing the relations in terms of the force Ly and take the columns
area into consideration, we have
;53.28
53.8LM
)10(
L
53.28
53.8
)8(
M yy My = 0.239LY (
;53.28
47.6LN
)10(
L
53.28
47.6
)6(
N yy Ny = 0.136Ly (3)
;LO53.28
47.31
)10(
L
53.28
47.31
)10(
O yy Oy = 1.103Ly (4)
Solving Equation (1) to (4) yields
Ly = 0.726 t My = 0.173t Ny 35t Oy =35 t
Using this same method, show that one obtains the results in Fig. 17 –d
for the columns at E, F G and H.
We can proceed to analyze each part of frame. As in the previous
examples, we begin with the upper corner segment LP, Fig. 17-e. Using
the calculated results, segment LEI is analyzed next, Fig . 17-f, followed
by segment EA, Fig. 17-g One can continue to analyze the other
segments in sequence, i.e., PQM, then MJFI, then FB, and so on.
3.628t
2.720t
Ax=2.720t
MA=21.760t.m
Ay=3.628t
Fy=3.628t
Fx=2.720t
Iy=2.902t
Ix=8.490t10m
6m
1.210t
0.726tPy=.726t
Px=6.79t10m
P
8t
Lx=1.21t
Ly=.726t
6m
8m
8m
A
(f)
(e)
(g)
Fig.(17-e.f and g)
574
Approximate
PROBLEMS
For the given statically indeterminate structures shown in figs. Draw
N.F. , S.F. & B.M.Ds . by using approximation methods.
10t 10t
5t
10t
1t/m
2t/m
3.06.06.0
6.0
6.0
3.0
4.0
4.0
6.0
8.0
4.0
(b)(a)
(c)
(d)
575
Approximate
5.0
3.0
3.0
6.0
5.05.0
3.0
3.0
4.0
6.06.06.06.0
3.0
4.0
(e)
(f)
2t/
m1t/
m2t/
m1t/
m
10t
10t
10t
5t
10t
10t
15t
576
Approximate
6.0
6.0
3.0
3.0
6.06.0
3.0
3.0
4.0
3.0
3.0
4.0
6.0
(g)
(h)
10t
10t
10t
10t
5t
10t
10t
15t
REFERENCES
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classical to Matrix methods”, Publishing House for University,
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Bazaraa & A.Akl “structural Analysis II”, First edition, 1999.
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publishing company, New York, 1990.
C.H. Norris, J.B. Wilbur, S. Utku, ” Elementary structural
analysis”, Mc Graw-Hill Book comp., 1976.
Emam, H., “Fundamental Theory of Structures”, faculty of
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Mouner Badir, ” Statically Indeterminate Plane Structures",
faculty of Engineering, University of Alexandria, 1980.
Chu-Kai Wang, “Statically Indeterminate Structures”, McGraw-
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A.S. Diwan, A.F.A. ElRahman, Y.M. Mansour, “Statically
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Maaref, Cairo, 1974.
Shaker, “Plane Analysis of Indeterminate structures”, Ain Shams
Univ., Cairo, 1968.
R.C. Coates, M.G. Coutie, F.K. Kong, “Structural Analysis”,
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