2. CE 255 β THEORY OF STRUCTURES
Chapter 1- The Conjugate Beam Method
Proposed by Professor Mueller-Breslau in 1865, the Conjugate Beam Method is a
slightly modified form of the Moment-Area Method (Chapter 2). Conjugate Beam
is defined as the imaginary beam with the same dimensions as that of the original
beam but load at any point on the conjugate beam is equal to the bending moment at
that point of the original beam divided by EI. The Conjugate Beam Method is an
engineering method used to find the slope and deflection of beams.
3. There are two theorems related to the conjugate beam
Theorem 1
The slope at a point in the real beam is equal to the shear at the corresponding point
in the conjugate beam.
Theorem 2
The displacement of a point in the real beam is equal to the moment at the
corresponding point in the conjugate beam.
The two theorems follow from the equations of internal loading and beam theory.
If the intensity of loading on a beam is w, V the shear force and M the bending
moment then
ππ
ππ₯
= π€ πππ π = β« π€ ππ₯ (1.1)
But π =
ππ
ππ
π2
π
ππ₯2
= π€ πππ π = β« (β« π€ππ₯) ππ₯ (1.2)
If π πππ π¦ are slope and deflection at a point on the beam, then from the beam theory
ππ
ππ₯
=
π
πΈπΌ
πππ π = β«
π
πΈπΌ
ππ₯ (1.3)
But π =
ππ¦
ππ₯
π2
π¦
ππ₯2
=
π
πΈπΌ
πππ π¦ = β« [β«
π
πΈπΌ
ππ₯] ππ₯ (1.4)
4. Comparing equations (1.1) and (1.3)
π = β« π€ππ₯
π = β«
π
πΈπΌ
ππ₯
We see that if the load w is replaced by
π
πΈπΌ
, then the shear V corresponds to the
slope π.
Similarly, comparing eqns. (1.2) and (1.4)
π = β« (β« π€ππ₯) ππ₯
π¦ = β« [β«
π
πΈπΌ
ππ₯] ππ₯
We see that if the w is replaced with
π
πΈπΌ
then the bending moment corresponds to the
deflection
5. Conjugate Beam Supports
When the conjugate beam is drawn, it is important that the shear and moment
developed in the conjugate beam correspond to the slope and displacement
conditions in the real beam.
6. PROCEDURE FOR ANALYSIS
1. Draw the Bending Moment Diagram for the given beam.
2. Construct the conjugate beam with the
π
πΈπΌ
loading, Remember that when the
π
πΈπΌ
diagram is positive the loading is upwards and when the
π
πΈπΌ
diagram is
negative, the loading is downwards.
3. Use the equations of equilibrium to solve for the reactions of the conjugate
beam.
4. Solve for the shear and moment at the points or points where the slope and
displacement are desired. If the values are positive, the slope is counter
clockwise and the displacement is upward.
Example of how a real beam is transformed into a conjugate beam
7. Area Properties
The area properties are well known for triangular and rectangular areas. For
parabolic curves, we have
8. Example 1.1
Determine the slope and deflection at B of the cantilever below EI=constant
Solution
First draw the bending moment diagram. We note that for this case. The diagram can
be drawn without first calculating the reactions
Next, draw the conjugate beam and load it with the
π
πΈπΌ
diagram, remembering that
loading is downward because the
π
πΈπΌ
diagram is negative.
9. Cut a section through the beam near B and consider the free body diagram to the left
of the section.
For the vertical equilibrium of forces, we have
π +
1
2
β
ππΏ
πΈπΌ
β πΏ = 0
π = β
ππΏ2
2πΈπΌ
The rotation ππ΅ of the real beam
ππ΅ = β
ππΏ2
2πΈπΌ
The minus sign means that it is a clockwise rotation.
Taking moments about a point at the section
10. π +
1
2
β
ππΏ
πΈπΌ
β πΏ β
2
3
πΏ = 0
π = β
ππΏ3
3πΈπΌ
The deflection
π¦π΅ = β
ππΏ3
3πΈπΌ
The negative sign indicates that deflection is downward.
Example 1.2
Calculate the maximum deflection of the simply supported beam loaded with udl of
intensity w.
Solution
The determination of reactions and drawing the bending moment diagram is trivial
and left as an exercise for the student
11. ο· Construct and load the conjugate beam with the
π
πΈπΌ
diagram
ο· Calculation of Reactions
We note that the loading is symmetrical and therefore each support will take
half of the total load. The total load is equal to the area under the parabola.
π π΄ = π π΅ =
1
2
β
2
3
β πΏ β
π€πΏ2
8πΈπΌ
=
π€πΏ3
24πΈπΌ
For the given system, we know that the maximum deflection occurs at mid-span. We
therefore make a section at the mid-span of the beam and compute the initial
moment.
12. π₯Μ =
3
8
β
πΏ
2
=
3πΏ
16
Taking moments at a point on the section, we have
π +
ππΏ3
24πΈπΌ
β
πΏ
2
β
ππΏ3
24πΈπΌ
β
3πΏ
16
= 0
π =
ππΏ3
24πΈπΌ
(
3πΏ
16
β
πΏ
2
)
= β
5ππΏ4
384πΈπΌ
Max deflection
π¦πππ₯ =
5ππΏ4
384πΈπΌ
(πππ€ππ€πππ)
13. Example 1.3
For the simply supported beam below, determine the deflection at C and the
maximum deflection.
Solution
The maximum moment occurs under the load, with a value
π = 2 Γ 6 Γ
3
6+3
= 4πππ (Student should confirm this by calculating reactions)
Conjugate Beam and Loading
Reactions
15. Maximum Deflection
We note that the maximum deflection
ο· Occurs near mid-span
ο· Occurs where the slope of the elastic curve or shear force is zero
The maximum deflection occurs between A and C, therefore we calculate the shear
force at a section x from support A.
At a section x metres from A, The intensity of load y can be calculates using similar
triangles
π¦
π₯
=
4
6
β π¦ =
2
3
π₯
Summing vertical forces,
π(π₯) +
8
πΈπΌ
β
1
πΈπΌ
β
1
2
π₯ β
2
3
π₯ = 0
π(π₯) +
8
πΈπΌ
β
π₯2
3πΈπΌ
= 0
π(π₯) = β
8
πΈπΌ
+
π₯2
3πΈπΌ
16. At maximum deflection, π(π₯) = 0
π₯2
3πΈπΌ
=
8
πΈπΌ
π₯2
= 24 β π₯ = 4.899π
ππππ₯ =
8
πΈπΌ
β 4.899 +
1
πΈπΌ
β
1
2
β
4.899
6
β 4 β 4.899 β
4.899
3
=
β26.13
πΈπΌ
πππ₯πππ’π πππππππ‘πππ ππ
26.13
πΈπΌ
πππ ππππ’ππ 4.899π ππππ π΄
BEAMS OF VARIABLE RIGIDITY
The conjugate beam can be also be used to calculate the slope and deflection of beam
of variable rigidity. This is illustrated in the example below.
Example 1.4
Calculate the slope and deflection at the free end of the cantilever beam of Example
1.1 if the moment of inertia (2nd
moment of area) varies as shown below.
17. Solution
The fact that the beam has variable rigidity has no effect on the bending moment
diagram.
We note that, using similar triangles, the moment at C is -PL/2
When loading the conjugate beam, the moments between A and C are divided by
1
2πΈπΌ
and those between C and B are divided by
1
πΈπΌ
. This gives the following
loaded conjugate beam.
The slope at B is the shear force at B, the total load on the beam.
ππ΅ = (π΄πππ ππ π‘πππππ§ππ’π πππ‘π€πππ π΄ πππ πΆ
+ π΄πππ ππ π‘πππππππ πππ‘π€πππ πΆ πππ π΅)
18. = β [
1
2
(
ππΏ
2πΈπΌ
+
ππΏ
4πΈπΌ
) β
πΏ
2
+
1
2
β
ππΏ
2πΈπΌ
β
πΏ
2
]
= β
3ππΏ3
16πΈπΌ
β
ππΏ3
8πΈπΌ
= β
5ππΏ3
16πΈπΌ
π¦π΅
= β(ππππππ‘ ππ π‘πππππ§πππππ ππππ
+ ππππππ‘ ππ π‘ππππππ’πππ ππππ) ππππ’π‘ π πππππ‘ ππ π π πππ‘πππ π‘βπππ’πβ π΅
Since the centroid of the trapezium is not known the trapezium can be divided into
a. 2 triangles
b. A triangle and a rectangle
And their moments combined β the principle of superposition
Moment of trapezoidal load using 2 traingles
Trapezium is divided into an upper triangle of area
1
2
β
ππΏ
2πΈπΌ
β
πΏ
2
and the distance of
its centroid from B is
2
3
β
πΏ
2
+
πΏ
2
19. Theref6re πππ’ = β
1
2
β
ππΏ
2πΈπΌ
β
πΏ
2
(
2
3
β
πΏ
2
+
πΏ
2
) =
β5ππΏ3
48πΈπΌ
And a lower triangle of area
1
2
β
πΏ
2
β
ππΏ
4πΈπΌ
with distance of centroid from B
1
3
β
πΏ
2
+
πΏ
2
Therefore πππΏ = β
1
2
β
ππΏ
4πΈπΌ
β
πΏ
2
(
1
3
β
πΏ
2
+
πΏ
2
) =
βππΏ3
24πΈπΌ
Total moment ππ = πππ’ + πππΏ
=
β5ππΏ3
48πΈπΌ
β
ππΏ3
24πΈπΌ
=
β7ππΏ3
48πΈπΌ
Alternatively we may calculate the moment of the trapezoidal load using a rectangle
and a triangle
Following the same procedure as before
πππ’ = β
1
2
β
ππΏ
4πΈπΌ
β
πΏ
2
(
2
3
β
πΏ
2
+
πΏ
2
) =
β5ππΏ3
96πΈπΌ
20. πππΏ = β
ππΏ
4πΈπΌ
β
πΏ
2
(
1
2
β
πΏ
2
+
πΏ
2
) =
β3ππΏ3
32πΈπΌ
Total Moment ππ = πππ’ + πππΏ
=
β5ππΏ3
96πΈπΌ
β
3ππΏ3
32πΈπΌ
=
β14ππΏ3
96πΈπΌ
β7ππΏ3
48πΈπΌ
As we see, two methods yield the same results.
Finally we calculate the moment of the triangular load between C and B
about B.
π2 = β
1
2
β
ππΏ
2πΈπΌ
β
πΏ
2
β
2
3
β
πΏ
2
= β
ππΏ3
24πΈπΌ
21. Deflection at B
π¦π΅ = π1 + π2
=
β7ππΏ3
48πΈπΌ
β
ππΏ3
24πΈπΌ
=
β9ππΏ3
48πΈπΌ
22. EXERCISES
P1.1
Determine the slope and deflection at the free end of the cantilever beam below
P1.2
For the beam below, calculate the maximum deflection within the span A-B
P1.3
Calculate the rotation just to the left and just to the right of B. Compute the deflection
at D
23. CHAPTER 2
THE MOMENT-AREA METHOD
The Moment-Area Method was developed by Otto Mohr in 1868 and presents
powerful tool for finding the deflection of structures subjected primarily to bending.
Its ease of finding deflections of statically determinate structures makes it ideal for
solving statically indeterminate structures, using compatibility of displacements.
THEORETICAL BASIS
We consider the length AB of abeam in its undeformed state (page 22). From the
diagram, we note.
1. AB is the original unloaded length of the beam and AβBβ is deflected position
of AB when loaded.
2. The angle subtended at the centre of arc AβOBβ is Σ¨ and is the change in slope
from Aβ to Bβ
3. PQ is a very short length of the beam, measured as dS along the curve and dx
along the x-axis
4. dӨ is the change in slope from P to Q and is also the angle subtended at the
centre of the arc dS.
5. M is the average bending moment over the portion dx between P and Q.
6. The distance β is known as the vertical intercept and is the distance from Bβ
to the produced tangent to the curve at Aβ which crosses under Bβ at C. It is
measured perpendicular to the undeformed neutral axis.
24.
25. MOHRβS FIRST THEOREM (Mohr 1)
Noting that the angles are small and measured in radians, we have
ππ = π β ππ
π =
ππ
ππ
From the Euler-Bernoulli Theory of Bending, we know
1
π
=
π
πΈπΌ
Hence ππ =
π
πΈπΌ
ππ
But for small deflections, the chord and arc length are similar, i.e. ππ β ππ₯, giving
ππ =
π
πΈπΌ
ππ₯
The total change in slope between A and B is thus
β« ππ
π΅
π΄
= β«
π
πΈπΌ
ππ₯
π΅
π΄
πππ΅π΄ = ππ΅ β ππ΄ = β«
π
πΈπΌ
π΅
π΄
ππ₯
[πΆβππππ ππ π ππππ]π΄π΅ = [π΄πππ ππ
π
πΈπΌ
ππ’πππππ]
π΄π΅
Usually the beam is prismatic and so E and I do not change over the length AB,
whereas the bending moment M will change thus
ππ΄π΅ =
1
πΈπΌ
β« π ππ₯
π΅
π΄
26. [πΆβππππ ππ π ππππ]π΄π΅ =
[π΄πππ ππ
π
πΈπΌ
ππ’πππππ]
π΄π΅
πΈπΌ
This is Mohrβs First theorem (Mohr 1)
ο· The change in slope between any two points on an elastic curve is equal to the
area of the bending moment diagram between the points divided by EI.
MOHRβS SECOND THEOREM (Mohr II)
From the diagram we can see that
πβ= π₯ β ππ
But ππ =
π
πΈπΌ
ππ₯
Therefore πβ=
π
πΈπΌ
β π₯ β ππ₯
And for the portion AB, we have
β« πβ
π΅
π΄
= β«
π
πΈπΌ
β π₯ β ππ₯
π΅
π΄
βπ΅π΄= [β«
π
πΈπΌ
β ππ₯
π΅
π΄
] π₯Μ
= πΉπππ π‘ ππππππ‘ ππ
π
πΈπΌ
πππππππ ππππ’π‘ π΅
This can be interpreted as
[
ππππ‘ππππ
πΌππ‘ππππππ‘
]
π΅π΄
= [
π΄πππ ππ
π
πΈπΌ
ππ’πππππ
]
π΅π΄
β [
π·ππ π‘ππππ ππππ π΅ π‘π πππ‘ππππ ππ
(
π
πΈπΌ
)
π΅π΄
πππππππ
]
27. This is Mohrβs second theorem and may be stated as:
ο· For an originally straight beam subjected to bending moment, the vertical
intercept between one terminal and the tangent to the curve of another terminal
is the first moment of the
π
πΈπΌ
diagram about the terminal where the intercept is
measured.
Two crucial things must be noted from this definition;
1. Vertical intercept is not deflection. It is the distance from the deformed
position of the beam to the tangent of the deformed shape of the beam at
another location
Thus
ββ πΏ
2. The moment of the curvature diagram must e taken about the point where the
vertical intercept is required. That is
βπ΅π΄β βπ΄π΅
28. Example 2.1
For the cantilever beam shown, find the slope and deflection at B
Solution
29. For Mohr 1,
[πΆβππππ ππ π ππππ]π΄π΅ = [π΄πππ ππ
π
πΈπΌ
ππ’πππππ]
π΄π΅
ππ΅ β ππ΄ =
1
2
β πΏ β
ππΏ
πΈπΌ
But ππ΄ = 0
Therefore ππ΅ =
ππΏ2
2πΈπΌ
In this case, because the tangent from A is horizontal, the vertical intercept βπ΅π΄ is
equal to the deflection S at B
Since the intercept is measured at B, the first moment of the
π
πΈπΌ
diagram must be
taken from this point
30. Thus from Mohr II, we have
βπ΅π΄= (
1
2
β πΏ β
ππΏ
πΈπΌ
) β
2πΏ
3
And so the deflection at B is
πΏπ΅ =
ππΏ3
3πΈπΌ
Example 2.2
For the following simply supported beam, calculate the slope at A using Mohrβs
theorems
Solution
In the Moment-Area Method, the deflected shape diagram is used to identify
relationships between vertical intercepts and slopes
31. The key to the solution here is that we calculate βπ΅π΄ using Mohr II but from the
diagram we see that we can use the formula π = π π for small angles
βπ΅π΄= πΏππ΄
Once we know βπ΅π΄ from Mohr II, we can find ππ΄ =
βπ΅π΄
πΏ
β
To calculate βπ΅π΄ using Mohr II, we need the
π
πΈπΌ
diagram
33. GENERAL PROCEDURE FOR FINDING DEFLECTIONS
To find deflection at any location x from a support, use the following relationships
between slopes and vertical intercepts.
1. Use Mohr II to find the slope at the support
2. For the location x and from the diagram we have
πΏπ₯ = π₯ β ππ΅ β βππ΅
MAXIMUM DEFLECTION
We know that the maximum deflection occurs at a slope π = 0
34. To find where the slope is zero
1. Calculate slope at some point, say support A, using Mohr II
2. Using Mohr I determine at what distance from the point of known slope (ππ΄)
the change in slope (Mohr I), πππ΄ equals the known slope, (ππ΄)
3. This is the point of maximum deflection since
ππ΄ β πππ΄ = ππ΄ β ππ΄ = 0
Example 2.3
For the following beam of constant EI
a. Determine ππ΄, ππ΅ and πΏπΆ
b. What is the maximum deflection and where is it located?
35. The first step is to draw the bending moment diagram and draw the deflected shape
diagram with slopes and tangents as indicated.
Slopes at A and B
πΈπΌβπ΄π΅= (
2
3
β 2) (
1
2
β 2 β 53.4) + (2 +
4
3
) (
1
2
β 4 β 53.4)
= 53.4 (
4
3
+
20
3
) = 427.2
Therefore βπ΄π΅= 427.2
πΈπΌ
β
But βπ΄π΅= 6ππ΅
6ππ΅ =
427.2
πΈπΌ
Therefore ππ΅ =
71.2
πΈπΌ
Similarly for the slope at A
πΈπΌβπ΅π΄= (
2
3
β 4) (
1
2
β 4 β 53.4) + (4 +
1
3
β 2) (
1
2
β 2 β 53.4)
= 53.4 (
16
3
+
14
3
) = 534
βπ΅π΄= 534
πΈπΌ
β
36. But βπ΅π΄= 6ππ΄
Therefore ππ΄ =
89.2
πΈπΌ
Deflection at C
To find the deflection at C, we use the vertical intercept βπΆπ΅ and ππ΅
From the diagram above
πΏπΆ = 4ππ΅ β βπΆπ΅
From the bending moment diagram and slope at B
πΈπΌπΏπΆ = 4 β 71.2 β (
1
2
β 4 β 53.4) (
4
3
) = 142.4
Therefore πΏπΆ =
142.4
πΈπΌ
37. MAXIMUM DEFLECTION
The first step in finding the maximum deflection is to locate its position. We know
two things;
1. Maximum deflection occurs where there is zero slope
2. Maximum deflection is always close to the centre of span
Based on these facts, we work with Mohr I to find the point of zero slope which will
be located between B and C, as follows.
πΆβπππππ πππ‘ππ‘πππ = ππ΅ β 0 = ππ΅
Since we know that the change in slope is also the area of the
π
πΈπΌ
diagram we need to
find the point x where the area of the
π
πΈπΌ
diagram is equal to ππ΅
πβπ’π πΈπΌ(ππ΅ β 0) = (53.4 β
π₯
4
) β
1
2
β π₯
πβπ’π πΈπΌ(ππ΅) = (53.4 β
π₯2
8
)
π΅π’π‘ ππ΅ =
71.2
πΈπΌ
, βππππ
39. APPLICATION TO STATICALLY INDETERMINATE STRUCTURES
ο· Moment-Area Method for Built-in-Beams
A beam is said to be built in or encastre when both ends are rigidly fixed so
that the slope at the ends remain horizontal
It follows that, if EI is constant
ο· Change in slope from end to end is zero and Mohr I gives
β π΄π = 0
ο· The vertical intercept are zero at both ends and Mohr II gives
β π΄π π₯Μ π = 0
Where π΄π are the areas under the bending moment diagram and π₯Μ π the distances of
the centroids to the end where the intercepts are being measured.
It is convenient to show the bending moment diagram to any load such as below as
the algebraic sum of 2 parts β one due to loads, treating the beam as simply supported
and the other due to end moments, introduced to bring the slope back to zero.
40. Mohr I states that the sum of the areas, positive and negative is zero
π΄1 β π΄2 = 0 β π΄1 = π΄2
And Mohr II gives
π΄1π₯Μ 1 = π΄2π₯Μ 2
These equations can be used to solve for the unknown fixed-end moments ππ΄ and
ππ΅. We illustrate this by the following examples.
41. Example 2.4
For the built-in beam shown, determine the end moments and the deflection under
the load (maximum deflection)
Solution
The bending moment diagram is of the form
Due to symmetry, ππ΄ = ππ΅ = π
Draw the free moment and fixed moment diagrams
42. From Mohr I, the area of the free moment diagram is equal to that of the fixed
moment diagram
πβπ’π
πΏ
2
β
ππΏ
4
= π β πΏ
π‘βπππππππ π =
ππΏ
8
Since ππ΄ = ππ΅ = π , application of Mohr II s redundant, However for
unsymmetrical loading, ππ΄ β ππ΅ and a second equation is obtained from Mohr II
to solve for the two unknowns ππ΄, ππ΅
43. Deflection
Taking moments at C where the intercepts is measured
πΈπΌβπΆπ΄= (
1
2
β
πΏ
2
β
ππΏ
4
) β
1
3
β
πΏ
2
β (
πΏ
2
β
ππΏ
8
) β
1
2
β
πΏ
2
=
ππΏ3
96
β
ππΏ3
64
= β
ππΏ3
192
πΏπππ₯ = βπΆπ΄= β
ππΏ3
192πΈπΌ
Note that the same results are obtained measuring the intercept βπ΄πΆ
44. APPLICATION TO INDETERMINATE STRUCTURES β USE OF
PRINCIPLE OF SUPERPOSITION AND DISPLACEMENT
COMPATIBILITY
Generally, we can use the principle of superposition to separate indeterminate
structures into primary and reactant structures.
For the built-in beams of the previous section, the primary structures is the statically
determinate simply-supported beam with the given load (Free moment) and the
reactant structure is the simply-supported beam loaded with the moment reactions
(Fixed Moments).
ο· For these structures, we can calculate the deflections at a point for which the
deflection is known for the original structure.
ο· We then use compatibility of displacement to equate the two calculated
deflections to the known deflection of the original structure.
ο· Doing so will yield the redundant reaction chosen for the reactant structure.
Once this is known, all other load effects (bending moment, shear force, deflections
and rotations) can be calculated. We illustrate this in the following example:
Example 2.5
For the propped cantilever shown, determine the maximum deflection.
45. Solution
The system is statically indeterminate to the first degree so one of the reactions must
ne release to obtain a statically- determinate primary structure. There are 2
possibilities β either the moment at A or the reaction at B. Letβs settle for the latter.
πΉππππ = πππππππ¦ + π ππππ‘πππ‘
π π΅ ππ π‘βπ π£πππ’π ππ π‘βπ πβππ ππ ππππ’πππππ‘
In the final structure we know that the deflection at B,πΏπ΅, must be zero as it is a roller
support. Therefore from the bending moment diagram that results from the
superposition of the primary and reactant structures, we calculate πΏπ΅ in terms of RB
and solve π πππΏπ΅ = 0Ξ΄
From the deflected shape and bending moment diagram of the primary structure.
βπ΅π΄= πΏπ΅
π
=
1
πΈπΌ
β
1
3
(β256) β 8 β (
3
4
β 8) = β
4096
πΈπΌ
and from those of the reactant structure
βπ΅π΄= πΏπ΅
π
=
1
πΈπΌ
β
1
2
β 8π π΅ β (β256) β 8 β (
2
3
β 8) =
512
3πΈπΌ
π π΅
46. The displacement compatibility at B gives
πΏπ΅ = πΏπ΅
π
+ πΏπ΅
π
= β
4096
πΈπΌ
+
512
3πΈπΌ
π π΅ = 0
512
3πΈπΌ
π π΅ = 4096
π π΅ = 24 ππ
With π π΅ known, we can draw the final bending moment diagram by adding the
BMDs of the primary and reactant structures
LOCATION OF THE MAXIMUM DEFLECTION
Assume the maximum deflection is at a location x from support B. The slope at the
maximum deflection is zero. This means that between B and x, the slope changes by
47. ππ΅ and therefore by Mohr I, the area of the
π
πΈπ
diagram between πΏπππ₯ and B is equal
to ππ΅.
To calculate the required area of the
π
πΈπ
diagram, it is convenient to use the primary
and reactant diagram rather than the final diagram.
πΈπΌππ΅π = β
1
3
β 4π₯2
β π₯ +
1
2
β 24π₯ β π₯ = β
4
3
π₯3
+ 12π₯2
πΈπΌππ΅ = β
1
3
β 256 β 8 +
1
2
β 8 β 24 β 8 =
256
3
πΈπΌππ΅π = πΈπΌππ΅
β
4
3
π₯3
+ 12π₯2
=
256
3
4π₯3
β 36π₯2
+ 256 = 0
π₯ = 3.37
πΈπΌπΏπππ₯ = β
1
3
β 4 β 3.372
β 3.37 β
3
4
β 3.37 +
1
2
β 24 β 3.372
β
2
3
β 3.37
= 177.2
48. πΏπππ₯ =
177.2
πΈπΌ
EXERCISE
P2.1
For a simply-supported beam of span L with a concentrated Load P at mid-span,
shows that the deflection under the load is
πΏ =
ππΏ3
48πΈπΌ
P2.2
For a simply-supported beam of span L loaded with UDL of intensity w, show that
the mid-span deflection is
πΏ =
5ππΏ4
384πΈπΌ
P2.3
Apply Mohrβs Theorem to calculate the end moments of the built-in beams below.
49. P2.4
Assume a simply-supported beam as a primary structure for the propped cantilever
loaded with UDL as shown below. Use the appropriate displacement compatibility
to calculate the moment at A.
P2.5
Find the maximum deflection in span AB and the deflection at C in terms of EI
50. CHAPTER 3
CONTINUOUS BEAMS AND THE THREE MOMENT EQUATION
A beam is used to be continuous when supported on more than 2 supports.
Continuous beams are statically indeterminate. The intermediate supports of a
continuous beam are always subjected to some bending moment. The analysis of a
continuous beam is similar to that of fixed end beam.
The bending moment diagram of a continuous beam, under any set of loading, may
be drawn in two stages:
1.) By considering the beam as a series of discontinuous beams (with simple
supports) and drawing the bending moment diagram for the given loads, (Free
Moment Diagram).
2.) By superimposing the Free Moment diagram to the end moments (Fixed
Moment Diagram)
51. In Fig 3.1, ABC is a continuous beam in which
πΏ1 = π πππ ππ π΄π΅
πΏ2 = π πππ ππ π΅πΆ
πΌ1 = ππππππ‘ ππ πΌππππ‘ππ ππ ππππ ππ ππππ π΄π΅
πΌ2 = ππππππ‘ ππ πΌππππ‘ππ ππ ππππ ππ ππππ π΅πΆ
ππ΄ = ππ’πππππ‘ ππππππ‘ ππ‘ π΄
ππ΅ = ππ’πππππ‘ ππππππ‘ ππ‘ π΅
ππΆ = ππ’πππππ‘ ππππππ‘ ππ‘ πΆ
π΄1 = π΄πππ ππ π‘βπ ππππ ππππππ‘ πππππππ ππ π πππ π΄π΅
π΄2 = π΄πππ ππ π‘βπ ππππ ππππππ‘ πππππππ ππ π πππ π΅πΆ
Fig 3.2 shows the deflected shape. Draw a tangent to the deflected shape (Elastic
curve) at B meeting the vertical through A at D and the vertical through C at E.
We note that
52. tan π =
βπ΄
πΏ1
= β
βπΆ
πΏ2
β¦ β¦ β¦ β¦ β¦ ππ. 3.1
From Mohr II
βπ΄ = βπ΄π΅=
1
πΈπΌπ
[(π΄1π₯Μ 1 + ππ΄ β
πΏ1
2
β
πΏ1
3
) + (ππ΅ β
πΏ1
2
β
2πΏ1
3
)]
=
1
6πΈ
(
6π΄1π₯Μ 1
πΌ1
+
ππ΄πΏ1
2
πΌ1
+
2ππ΅πΏ1
2
πΌ1
)
βπ΄
πΏ1
=
1
6πΈ
(
6π΄1π₯Μ 1
πΌ1πΏ1
+
ππ΄πΏ1
πΌ1
+
2ππ΅πΏ1
πΌ1
) ππ 3.2
βπΆ
πΏ2
=
1
6πΈ
(
6π΄2π₯Μ 2
πΌ2πΏ2
+
ππΆπΏ2
πΌ2
+
2ππ΅πΏ2
πΌ2
) ππ 3.3
Substituting eq. 3.2 and eq 3.3 in eq 3.1 we obtain
ππ΄
πΏ1
πΌ1
+ 2ππ΅ (
πΏ1
πΌ1
+
πΏ2
πΌ2
) + ππΆ
πΏ2
πΌ2
= β6 (
π΄1π₯Μ 1
πΌ1πΏ1
+
π΄2π₯Μ 2
πΌ2πΏ2
)
This is known as the three Moment Equation
If the moment of inertia of the beam is constant, the equation reduces to
ππ΄πΏ1 + 2ππ΅(πΏ1 + πΏ2) + ππΆπΏ2 = β6 (
π΄1π₯Μ 1
πΏ1
+
π΄2π₯Μ 2
πΏ2
)
The Three Moment Equation was derived by CLAPEYRON in 1857 and relates the
unknown reactant moments to the free bending moment diagram for each two
53. consecutive spans of a continuous beam. By writing this equation for each adjacent
pair of spans, a sufficient number of equations are obtained pair of spans, a sufficient
number of equations are obtained to solve for the unknown moments.
Example 3.1
A continuous beam ABCD, simply supported at A, B, C and D is loaded as shown
below. Find the support moments and draw the bending moment and shear force
diagram.
Solution
Draw the continuous beam as a series of simply-supported beams and draw the free
moment diagram EI is constant.
54. The degree of redundancy is 2 - ππ΅ πππ ππΆ
We consider the first 2 spans, AB and BC
And calculate the terms π΄1π₯Μ 1 πππ π΄2π₯Μ 2 in the three moment equation. The moment
π΄1π₯Μ 1 is taken at A and π΄2π₯Μ 2 is taken at C. The moments are taken at the exterior
supports and NEVER at the middle supports. The areas π΄1 πππ π΄2 are each divided
into two as indicated by the dotted lines so that the centroids of the resulting triangles
can be easily located.
π΄1π₯Μ 1 =
1
2
β 12 β 2 β
2
3
β 2 +
1
2
β 12 β 4 (2 +
1
3
β 4)
= 16 + 80 = 96
π΄2π₯Μ 2 =
1
2
β 9.6 β 3 β
2
3
β 3 +
1
2
β 9.6 β 2 (3 +
1
3
β 2)
= 28.8 + 35.2 = 64
We can now write the three moment equation for span AB
ππ΄πΏ1 + 2ππ΅(πΏ1 + πΏ2) + ππΆπΏ2 = β6 (
π΄1π₯Μ 1
πΏ1
+
π΄2π₯Μ 2
πΏ2
)
We note that the continuous beam has a simple support at A, i.e. ππ΄ = 0
0 + 2ππ΅(6 + 5) + ππΆ β 5 = β6 (
96
6
+
64
5
)
55. 22 ππ΅ + 5ππΆ = β172.8
Next, we move to spans BC and CD
In calculating π΄1π₯Μ 1, we note that while π΄1 is the same area π΄2 shown in the spans
AB and BC, the moment is taken at the same point. For spans AB, BC the moment
was taken at C while for the present spans, it is taken at B.
π΄1π₯Μ 1 =
1
2
β 9.6 β 2 β
2
3
β 2 +
1
2
β 9.6 β 3 (2 +
1
3
β 3)
12.8 + 43.2 = 56
π΄2π₯Μ 2 =
2
3
β 4 β 6 β
4
2
= 32
We now write the 3 Moment Equations, noting that the unknown moments are
now ππ΅, ππΆ and ππ·. However, ππ· is zero because D is an exterior simple supports
ππ΅ β 5 + 2ππΆ(5 + 4) = β6 (
56
5
+
32
4
)
5ππ΅ + 18ππΆ = β115.2
The Equations (a) and (b) are solved simultaneously to obtain
ππ΅ = β6.84πππ
56. ππΆ = β4.48 πππ
REACTIONS
With the support moments, calculated, the reactions can be calculated from the
simply-supported beams as follows:
Considering span AB
β ππ΅ = 0
6π π΄ β 9 β 4 + 6.84 = 0
π π΄ =
36 β 6.84
6
= 4.86 ππ
π π΅
πΏ
= 9 β 4.86 = 4.14 ππ
58. π πΆ
π
= 3 β 4 β 4.88 = 7.12 ππ
π π΅ = π π΅
πΏ
+ π π΅
π
= 4.14 + 5.27 = 9.41 ππ
π π = π πΆ
πΏ
+ π πΆ
π
= 2.73 + 7.12 = 9.85 ππ
The bending moment diagram can be drawn by superimposing the free moment
diagram on the fixed moment diagram.
The shear force diagram can be constructed from the reactions of the simply-
supported beams.
59. CONTINUOUS BEAM WITH OVERHANG
If a continuous beam has an overhang that end remains statically determine since the
support moment is known. No additional equation needs to be formulated due to the
overhang.
For the above beams, we have only one redundant moment, ππ΅ , A is an end simple
support, ππ΄ = 0 , and at C we observe that ππΆ = βππΏ3, the negative sign indicating
a hogging moment.
For such a structure, we first formulate the three moment equation involving ππ΄, ππ΅
and ππΆ and substitute the known values of ππ΄ and ππΆ.
CONTINUOUS BEAM WITH FIXED END SUPPORT
For a continuous beam with fixed end supports, end moments are developed at the
supports. The rotation at the fixed end does not take place and the support moment
is required to be calculated.
60. In order to analyse such as beam by the Theorem of Three Moment, an additional
equation is required for each fixed end. In such a case, whenever an exterior support
is fixed, an additional imaginary span of length zero with no loads is appended to
the end.
In formulating equation 2 in the above sketch, all terms involving the appended zero
length span are zero.
Thus for span BC and CCβ
Three Moment Equation
ππ΅πΏ1 + 2ππΆ(πΏ1 + 0) = β6 (
π΄1π₯Μ 1
πΏ1
+ 0)
ππ΅πΏ1 + 2ππΆπΏ1 = β6
π΄1π₯Μ 1
πΏ1
61. Example 3.2
For the continuous beam with constant EI, determine the supports moments and
draw the bending moment and shear force diagrams.
π΄πΌ
π΄ ππ π‘βπ πππππππππ¦ π§πππ π πππ
ππππ π΄πΌ
π΄ πππ π΄π΅
π΄1π₯Μ 1 = 0
π΄2π₯Μ 2 =
1
2
β 24 β 3 (2 +
1
3
β 3) +
1
2
β 24 β 2 β
2
3
β 2
= 108 + 32
= 140
65. EXERCISES
P3.1
Analyse the propped cantilever beam below and draw the bending moment and shear
force diagrams. EI is constant.
P3.2
Analyse the fixed beam with internal hinge and draw the bending moment diagram
EI=constant.
66. P3.3
For the continuous beam below, use the three moment theorem to calculate the
unknown moments and draw the bending moment and shear force diagrams.
67. CHAPTER 4
DEFLECTION BY ENERGY METHODS
Energy Methods belong to a class of procedures employing the Principle of
Conservation of Energy to determine the deflections of structures. To this class
belong, among others,
ο· The STRAIN ENERGY METHODS
ο· The PRINCIPLE OF VIRTUAL WORK
ο· CASTIGLIANOβS METHOD
In this course, we shall limit ourselves to the principle of virtual work.
4.1 PRINCIPLE OF VIRTUAL WORK
ο· A virtual displacement is an imaginary displacement imposed on a
structure, compatible with the boundary conditions.
ο· Virtual Force is a set of imaginary forces in equilibrium
The work done by the real force during virtual displacement or the work done by the
virtual force during real displacement is called virtual work.
ο· For virtual work to be done, either the displacement or force must be virtual.
Both cannot be real nor can both be virtual.
68. The Principle of virtual work states that:
ο· A body is in equilibrium if, and only if the virtual work of all forces acting on
the body is zero
INTERNAL AND EXTERNAL VIRTUAL WORK
When a structure deforms, work is done both by the applied loads moving through
a displacement, as well as by the internal stresses moving through corresponding
strains (increase in strain energy) in the structure.
Thus when virtual displacements or forces are causing virtual work, we have:
πΏπ = 0
πΏππΌ β πΏππΈ = 0
πΏππΌ = πΏππΈ
Where;
ο· Virtual work is denoted πΏπ and is zero for a body in equilibrium
ο· External Work done is πΏππΈ , and
ο· Internal Work is πΏππΌ
The Material can be linear or non-linear
The external virtual work is
πΏππΈ = β(πΏπππ β ππππππ πππππππ π£πππ‘π’ππ πππ πππππππππ‘π )
The internal virtual work is the work done by the internal forces on their
corresponding virtual displacements.
69. We shall consider only the axial forces N and moment M among the internal forces.
The effects of shear and torsion are insignificant.
For a length ππ₯ of a member under constant axial load N and constant moment M,
with extension ππΏ and rotation ππ, the internal virtual work.
πΏππΌ = πππΏ + πππ
ππΌ = β« π ππΏ + β« π ππ
70. THE VIRTUAL WORK METHOD
In the Virtual Work Method, also called the Unit Load or Dummy Load Method,
two sets of loading are considered.
SET 1: Structure subjected to actual external loads or temperature changes
SET 2: Unit Load acting on , structure. This is a fictitious or dummy load introduced
for the purpose of calculating the displacements in the structure. The unit load is
placed at the point of the structure and in the direction where displacement is
required.
Impose the displacements due to the first set (real loadings) as virtual displacement
for the unit load. The virtual work done by the unit load.
ππΈ = 1 β β
Where β is the real displacement being sought
1 β β= β« π1 ππΏ + β« π1 ππ
Where β , ππΏ πππ ππ πππ π‘βπ π πππ πππ πππππππππ‘π
And 1, π1 πππ π1 πππ π‘βπ ππππ‘π’ππ πΏπππππππ
Using Hookeβs Law (Refer to Fig 4.1)
ππΏ =
ππ
πΈπ΄
ππ₯, πππ
ππ =
ππ
πΈπΌ
ππ₯
71. Where:
ππ β ππ₯πππ πππππ ππ ππππππ ππππ π‘βπ ππππ π‘ π ππ‘ ππ πππππππ(ππ₯π‘πππππ πππππ )
ππ β πππππππ ππππππ‘ ππ ππππππ ππππ π‘βπ ππ₯π‘πππππ πππππ
ππΌ β ππ₯πππ πππππ ππ ππππππ ππππ π‘βπ π’πππ‘ ππππ
ππΌ β πππππππ ππππππ‘ ππ ππππππ ππππ π‘βπ π’πππ‘ ππππ
β= β«
ππΌππ
πΈπ΄
ππ₯ + β«
ππΌππ
πΈπΌ
ππ₯
From trusses, the bending effects are negligible and
β= β«
ππΌππ
πΈπ΄
ππ₯
Since the axial forces in truss members are constant the above simplifies to
β= β
ππΌπ πππ
πΈπ΄π
πΏπ
π
π=1
Where the summation goes over the number of members
For the beam and for many frames, the axial effect on displacements is very small
and can be omitted; Thus
β= β«
ππΌ ππ
πΈπΌ
πΏ
0
ππ₯
In most cases, for statically determinate structures, the moment diagrams ππΌ and ππ
can be drawn without writing the equations. The Integral β« ππΌ ππ ππ₯ can be
computed graphically.
73. Example 4.1
Use the unit load method to calculate the mid-span deflection and the slope at the
supports of a simply-supported beam loaded with UDL of intensity w.
Solution
Method 1: Integration
Set1 Loading
ππ =
π€πΏ
2
π₯ β
π€π₯2
2
Set 2 loading
ππ =
1
2
π₯ ; (0 β€ π₯ β€
πΏ
2
)
74. Due to symmetry, the integration can be performed over half the span and the results
multiplied by 2.
β=
1
πΈπΌ
β« ππΌ ππ ππ₯
πΏ
0
=
2
πΈπΌ
β«
1
2
π₯ (
π€πΏπ₯
2
β
π€π₯2
2
)
πΏ
2
0
ππ₯
β=
2
πΈπΌ
β« (
π€πΏπ₯2
4
β
π€π₯3
4
) ππ₯
πΏ
2
0
=
π
πΈπΌ
[(
π€πΏπ₯3
12
β
π€π₯4
16
)]
π
π³
π
=
2
πΈπΌ
[
π€πΏ4
96
β
π€πΏ4
256
]
=
π€πΏ4
πΈπΌ
(
1
48
β
1
128
)
=
5π€πΏ4
384πΈπΌ
Method 2 β Graphical (Preferred)
Set 1 Loading
75. Set 2 loading
Due to symmetry we can deal with the diagrams up to mid-span and double the
results
β΄ β =
2 β π΄ β π
πΈπΌ
= 2 β
2
3
β
πΏ
2
β
π€πΏ2
8
β
5
8
β
πΏ
4
β
1
πΈπΌ
76. =
5π€πΏ4
384πΈπΌ
To calculate the rotation or slope at the support, we apply a unit moment to support
A and draw the ππΌ diagram
ππ΄ =
1
πΈπΌ
β
2
3
β πΏ β
π€πΏ2
8
β
1
2
=
π€πΏ3
24πΈπΌ
77. Example 4.2
For the frame below, determine the vertical deflection at node D. EI is constant for
all members
Solution
For the set 1 loading, letβs use the principle of superposition letting the UDL and
concentrated load act independently.
For the systems on the right, the bending moment diagrams can easily be drawn.
79. Example 4.3
For the truss above, determine the following:
a. The vertical deflection of node 5
b. The rotation of member 1-5
c. The change in distance between nodes 2 and 3
Solution
Sub questions (a), (b) and (c) all make use of the same set 1 Loading. The axial
forces in the members must be determined for the given external loading.
80. a. To calculate the vertical deflection of node 5, put a vertical unit load at node
5 and calculate the axial forces in all members.
Now make and compute the following table
Member Length(L) Area (A) ππΌ ππ ππΌπππΏ/π΄
1-3 πΏ 2
β A 0 P 0
2-5 πΏ 2
β A -1 -2P PL/A
4-5 πΏ 2
β A 0 -P 0
1-2 πΏ 2
β A -1 -P PL/2A
1-5 πΏβ2 2
β π΄β2/2 β2 β2P 2PL/A
3-5 πΏ 2
β A 0 -P 0
3-4 πΏβ2 2
β π΄β2/2 0 β2P 0
β
ππΌπππΏ
π΄
=
7ππΏ
2π΄
Therefore Vertical deflection of node 5
β5
π£
=
7ππΏ
2πΈπ΄
81. (b) We need to subject member 1-5 to a unit moment. Since trusses do not take
moments at the joints, we use a couple (pair of equal but opposite forces) at the ends
of member 1-5 to produce a unit moment. The force at each end, F, is calculated as
πΉ β
πΏβ2
2
= 1
πΉ =
2
β2πΏ
=
β2
πΏ
To calculate the rotation of member 1-5, replace the column containing ππΌ in (a)
with those above and compute the last column in the table as follows:
82. Member Length(L) Area (A) ππΌ ππ ππΌπππΏ/π΄
1-3 πΏ 2
β A 0 P 0
2-5 πΏ 2
β A -2/L -2P 2P/A
4-5 πΏ 2
β A 0 -P 0
1-2 πΏ 2
β A 0 -P 0
1-5 πΏβ2 2
β π΄β2/2 β2/L β2P 2P/A
3-5 πΏ 2
β A 0 -P 0
3-4 πΏβ2 2
β π΄β2/2 0 β2P 0
β
ππΌπππΏ
π΄
=
4π
π΄
β1β5=
4π
πΈπ΄
(c) The nodes 2 and 3 either approach each other or move away from each other.
The unit loads (P=1) act at nodes 2 and 3 along the line joining them but directed
opposite each other. The forces are self-equilibrating and produce no reactions.
83. Member Length(L) Area (A) ππΌ ππ ππΌπππΏ/π΄
1-3 πΏ 2
β A ββ2/2 P ββ2PL/4A
2-5 πΏ 2
β A ββ2/2 -2P β2PL/2A
4-5 πΏ 2
β A 0 -P 0
1-2 πΏ 2
β A ββ2/2 -P β2PL/4A
1-5 πΏβ2 2
β π΄β2/2 1 β2P β2PL/A
3-5 πΏ 2
β A ββ2/2 -P β2PL/4A
3-4 πΏβ2 2
β π΄β2/2 0 β2P 0
β
ππΌπππΏ
π΄
=
7β2 ππΏ
4π΄
β2β3=
7β2 ππΏ
4π΄
Since the value is positive, the nodes approach each other as indicated.
84. EXERCISES
P4.1
Use the unit load method to calculate the vertical deflection at D
P4.2
Calculate the slope at A and the deflection at C
P4.3
For the cantilever truss, calculate the vertical deflection at joints 5 and 3. EA=80,000
kN for all members.