This document provides the details of an assignment to analyze a 48m concrete beam bridge with 5 spans using structural analysis software. It includes:
1) A description of the bridge geometry and assumptions made in the model.
2) 5 questions to calculate shear forces, reactions, and bending moments at various points on the bridge as a 30-tonne lorry moves across it.
3) The results of the calculations from the software in table and graph form, identifying the maximum values requested in each question.
4) Appendices with sample output from the software when the lorry is at a specific position.
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
Torsion tesd
MECHANICS OF MATERIALS
The objective of this experiment is to study the linearly elastic behavior
of metallic material under a torsion test. Torsion test measures the
strength of any material against maximum twisting forces. During this
experiment, a failure testing is done to our testing material which is a
steel. This failure testing involves twisting the material until it breaks
which helps demonstrates how materials undergo during testing
condition by measuring the applied torque with respect to the angle of
twist, the shear modulus, shear stress
At the limit of proportionality. The shear modulus of elasticity G and
Poisson's Ratio are determined for the specimen using torsional stressstrain relationship from the data collected during the experiment. The
fraction surface of our material at the end of the experiment is used to
stablish characteristics of the material,
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
Torsion tesd
MECHANICS OF MATERIALS
The objective of this experiment is to study the linearly elastic behavior
of metallic material under a torsion test. Torsion test measures the
strength of any material against maximum twisting forces. During this
experiment, a failure testing is done to our testing material which is a
steel. This failure testing involves twisting the material until it breaks
which helps demonstrates how materials undergo during testing
condition by measuring the applied torque with respect to the angle of
twist, the shear modulus, shear stress
At the limit of proportionality. The shear modulus of elasticity G and
Poisson's Ratio are determined for the specimen using torsional stressstrain relationship from the data collected during the experiment. The
fraction surface of our material at the end of the experiment is used to
stablish characteristics of the material,
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
Buckling test
MECHANICS OF MATERIALS
A fundamental condition in all problems is the equilibrium of
internal and external forces. If the system of forces is
disturbed owing to a small displacement of a body, two
principal situations are possible: either the body will return
to its original configuration owing to restoring forces during
displacement, or the body will accelerate farther away from
its original state owing to displacing forces. The latter
situation is termed instable equilibrium.
The instability of structural members subjected to
compressive loading (see Fig. 1(b)) may be regarded as a
mode of failure, even though stress may remain elastic, owing to excessive
deformation and distortion of the structure. This mode of failure is termed
buckling and is prevalent in members for which the transverse dimension is
small compared with the overall length
Forces2018 Presentation:The Assessment Of Pile Group Integrity Due To Pile Ec...azhar ahmad
The mode of driving precast reinforced concrete piles on site is without doubt among the most ‘error prone’ trades of a construction process. The short comings of driving pre designated piles at pin point accuracy at exactly the correct position on the ground has given rise to the caption of ‘pile eccentricity’ of nearly all individual piles within a pile group.
This then raises questions of integrity or how safe and reliable are pile caps that has been designed earlier with zero pile eccentricities. Questions of how much an eccentricity limit can be allowed for each pile or rather pile group arrangements such that previous pile cap designs are still safe and applicable has to be addressed. Thus one of the aims of this study is to evaluate the maximum allowable eccentricity of several common pile group arrangements. Results of this study indicates that the norm of adopting a maximum allowable eccentricity value of 75 mm for each individual pile irrespective of pile size, pile working load, pile spacing & column loads is quite misleading and may result in an unsafe pile group performance! Rather, results from this study suggests that the critical factor is not the eccentricity of individual piles but the overall net pile group eccentricity. This causes eccentric moments to act in the pile group which in turn governs the redistributed load to each individual pile within the pile group. This redistributed loads are then compared to the pile safe working load to establish a ‘Pass-Fail’ criteria.
This research paper presents a new technique for the synthesis of complex planar mechanisms. The author
calls this technique ‘nomogram-based synthesis’ since it depends on a kinematic nomogram facilitating the
synthesis of complex planar mechanisms without need to complex optimization procedures. A procedure of five
steps is presented to synthesize the mechanism under study for time ratio up to 4.3, normalized stroke up to 3.33.
The nomogram based synthesis can maintain transmission angle to be within a range from 94 to 120 degrees
indicating the effectiveness of the synthesis approach presented.
Keywords — Nomogram-based mechanism synthesis, 6 bar-2 sliders planar mechanism, successful
mechanism performance.
97th transportation research board meeting presentation-poster session 583Ozgur Bezgin
This presentation introduces the concept of impact reduction factor and a method both developed by Dr. Niyazi Özgür Bezgin that can estimate vertical impact forces on railways due to changes in track profile. The Bezgin Impact Factors KB1 and KB2 are introduced.
Research paper on indoor drone application with acoustic localization. Paper was accepted to the ISEEE 2019 conference (International Symposium on Electrical and Electronics Engineering).
Aplanning algorithm offive-axis feedrate interpolation based on drive and jer...IJRES Journal
CNC technology marks the core of modern manufacturing, and CNC interpolation module is one of the most important numerical control technology modules. Avery important feature of the CNC is to implement the feed rate that consists in producing the set points based on a NC program. In the high speed machining, the feed rate is restricted by the velocity, acceleration, and jerk. And the NURBS curve is a free curve, due to the many advantages of NURBS curves, it can be well applied to the CNC feed rate interpolation. The algorithm can get more smooth feed rate curves, which makes better use of kinematical characteristics of the machine. Finally, according to each machine axis capability, one can use the feed rate control method which is verified by simulation analysis and processing to test this method. The results show that the algorithm can effectively control the speed, acceleration and jerk.
Robots play important roles in day to day
activities of human endeavour and can perform
complex tasks speedily and accurately. Robots are
employed to imitate human behaviours and then
apply these behaviours to the skills that lead to
achieving a certain task in solving the challenges
faced by impaired people in society. This robotic arm
was achieved using light-weight steel iron for the
frames, a moderate torque MG995 Towerpro, and
servo motor. Two Atmega328 Arduino
microcontroller was employed to control the motors
through the use of pulse width modulation
technique. Mathematical models were developed for
the mechanism to represent the kinematics involved
at each joint with mathematical variables. Then, the
stability of the system was carried out using a step
input signal being a type zero system.
SAIF ALDIN ALI MADIN
سيف الدين علي ماضي
S96aif@gmail.com
Buckling test
MECHANICS OF MATERIALS
A fundamental condition in all problems is the equilibrium of
internal and external forces. If the system of forces is
disturbed owing to a small displacement of a body, two
principal situations are possible: either the body will return
to its original configuration owing to restoring forces during
displacement, or the body will accelerate farther away from
its original state owing to displacing forces. The latter
situation is termed instable equilibrium.
The instability of structural members subjected to
compressive loading (see Fig. 1(b)) may be regarded as a
mode of failure, even though stress may remain elastic, owing to excessive
deformation and distortion of the structure. This mode of failure is termed
buckling and is prevalent in members for which the transverse dimension is
small compared with the overall length
Forces2018 Presentation:The Assessment Of Pile Group Integrity Due To Pile Ec...azhar ahmad
The mode of driving precast reinforced concrete piles on site is without doubt among the most ‘error prone’ trades of a construction process. The short comings of driving pre designated piles at pin point accuracy at exactly the correct position on the ground has given rise to the caption of ‘pile eccentricity’ of nearly all individual piles within a pile group.
This then raises questions of integrity or how safe and reliable are pile caps that has been designed earlier with zero pile eccentricities. Questions of how much an eccentricity limit can be allowed for each pile or rather pile group arrangements such that previous pile cap designs are still safe and applicable has to be addressed. Thus one of the aims of this study is to evaluate the maximum allowable eccentricity of several common pile group arrangements. Results of this study indicates that the norm of adopting a maximum allowable eccentricity value of 75 mm for each individual pile irrespective of pile size, pile working load, pile spacing & column loads is quite misleading and may result in an unsafe pile group performance! Rather, results from this study suggests that the critical factor is not the eccentricity of individual piles but the overall net pile group eccentricity. This causes eccentric moments to act in the pile group which in turn governs the redistributed load to each individual pile within the pile group. This redistributed loads are then compared to the pile safe working load to establish a ‘Pass-Fail’ criteria.
This research paper presents a new technique for the synthesis of complex planar mechanisms. The author
calls this technique ‘nomogram-based synthesis’ since it depends on a kinematic nomogram facilitating the
synthesis of complex planar mechanisms without need to complex optimization procedures. A procedure of five
steps is presented to synthesize the mechanism under study for time ratio up to 4.3, normalized stroke up to 3.33.
The nomogram based synthesis can maintain transmission angle to be within a range from 94 to 120 degrees
indicating the effectiveness of the synthesis approach presented.
Keywords — Nomogram-based mechanism synthesis, 6 bar-2 sliders planar mechanism, successful
mechanism performance.
97th transportation research board meeting presentation-poster session 583Ozgur Bezgin
This presentation introduces the concept of impact reduction factor and a method both developed by Dr. Niyazi Özgür Bezgin that can estimate vertical impact forces on railways due to changes in track profile. The Bezgin Impact Factors KB1 and KB2 are introduced.
Research paper on indoor drone application with acoustic localization. Paper was accepted to the ISEEE 2019 conference (International Symposium on Electrical and Electronics Engineering).
Aplanning algorithm offive-axis feedrate interpolation based on drive and jer...IJRES Journal
CNC technology marks the core of modern manufacturing, and CNC interpolation module is one of the most important numerical control technology modules. Avery important feature of the CNC is to implement the feed rate that consists in producing the set points based on a NC program. In the high speed machining, the feed rate is restricted by the velocity, acceleration, and jerk. And the NURBS curve is a free curve, due to the many advantages of NURBS curves, it can be well applied to the CNC feed rate interpolation. The algorithm can get more smooth feed rate curves, which makes better use of kinematical characteristics of the machine. Finally, according to each machine axis capability, one can use the feed rate control method which is verified by simulation analysis and processing to test this method. The results show that the algorithm can effectively control the speed, acceleration and jerk.
Robots play important roles in day to day
activities of human endeavour and can perform
complex tasks speedily and accurately. Robots are
employed to imitate human behaviours and then
apply these behaviours to the skills that lead to
achieving a certain task in solving the challenges
faced by impaired people in society. This robotic arm
was achieved using light-weight steel iron for the
frames, a moderate torque MG995 Towerpro, and
servo motor. Two Atmega328 Arduino
microcontroller was employed to control the motors
through the use of pulse width modulation
technique. Mathematical models were developed for
the mechanism to represent the kinematics involved
at each joint with mathematical variables. Then, the
stability of the system was carried out using a step
input signal being a type zero system.
International Journal of Engineering Research and Applications (IJERA) is an open access online peer reviewed international journal that publishes research and review articles in the fields of Computer Science, Neural Networks, Electrical Engineering, Software Engineering, Information Technology, Mechanical Engineering, Chemical Engineering, Plastic Engineering, Food Technology, Textile Engineering, Nano Technology & science, Power Electronics, Electronics & Communication Engineering, Computational mathematics, Image processing, Civil Engineering, Structural Engineering, Environmental Engineering, VLSI Testing & Low Power VLSI Design etc.
Using Matlab software we designed a suspension controller for buses. If there is any bump is there then there is a chance for
movement of the seat due to this the passengers feels discomfort .so we reduce the time for the movement of seat less than 5 seconds by using feedback signal.
Increasing life of spur gears with the help of finite element analysisijmech
The Focus of this research is on mathematical analysis of life of gears and reducing noise frequency of gears due to change of material from C-45 to 19mncr5. Calculations for gears life was done with the help of Lewis equation and Buckingham formula. Basically life of a gear is depending upon the stress, more the stress on gear lesser life of gear will be. In this paper some major condition to perform a gear without failure is achieved i.e. tangential force should be less than tangential load to sustain static load, dynamic
load should be less than endurance load to sustain dynamic load and wear load should be less than static
load to sustain wear load. After calculation of 19mncr5 material we evaluate that endurance load acting on the gear which is greater than the dynamic load so our gear come out be safe. Also this study shows declination of noise level in 19mncr5 material compare to C-45 material.
Critical Thinking Physics Problem
Beberapa contoh Problem fisika berkaitan dengan berpikir kritis yang diperlukan pada kurikulum 2013.
1. Physics Toolkit
2. Representing Motion
3. Accelerated Motion
4. Forces in One Dimension
5. Forces in Two Dimensions
6. Motion in Two Dimensions
7.Gravitation
8. Rotational Motion
I'll upload the answers if anyone request me via mehdishaheen005@gmail.com
or
+92-345-6024498
If I have get time then upload the answers booklet soon. :)
it contains the basic information about the shear force diagram which is the part of the Mechanics of solid. there many numerical solved and whivh will give you detaild idea in S.f.d.
A review on techniques and modelling methodologies used for checking electrom...nooriasukmaningtyas
The proper function of the integrated circuit (IC) in an inhibiting electromagnetic environment has always been a serious concern throughout the decades of revolution in the world of electronics, from disjunct devices to today’s integrated circuit technology, where billions of transistors are combined on a single chip. The automotive industry and smart vehicles in particular, are confronting design issues such as being prone to electromagnetic interference (EMI). Electronic control devices calculate incorrect outputs because of EMI and sensors give misleading values which can prove fatal in case of automotives. In this paper, the authors have non exhaustively tried to review research work concerned with the investigation of EMI in ICs and prediction of this EMI using various modelling methodologies and measurement setups.
Using recycled concrete aggregates (RCA) for pavements is crucial to achieving sustainability. Implementing RCA for new pavement can minimize carbon footprint, conserve natural resources, reduce harmful emissions, and lower life cycle costs. Compared to natural aggregate (NA), RCA pavement has fewer comprehensive studies and sustainability assessments.
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Online aptitude test management system project report.pdfKamal Acharya
The purpose of on-line aptitude test system is to take online test in an efficient manner and no time wasting for checking the paper. The main objective of on-line aptitude test system is to efficiently evaluate the candidate thoroughly through a fully automated system that not only saves lot of time but also gives fast results. For students they give papers according to their convenience and time and there is no need of using extra thing like paper, pen etc. This can be used in educational institutions as well as in corporate world. Can be used anywhere any time as it is a web based application (user Location doesn’t matter). No restriction that examiner has to be present when the candidate takes the test.
Every time when lecturers/professors need to conduct examinations they have to sit down think about the questions and then create a whole new set of questions for each and every exam. In some cases the professor may want to give an open book online exam that is the student can take the exam any time anywhere, but the student might have to answer the questions in a limited time period. The professor may want to change the sequence of questions for every student. The problem that a student has is whenever a date for the exam is declared the student has to take it and there is no way he can take it at some other time. This project will create an interface for the examiner to create and store questions in a repository. It will also create an interface for the student to take examinations at his convenience and the questions and/or exams may be timed. Thereby creating an application which can be used by examiners and examinee’s simultaneously.
Examination System is very useful for Teachers/Professors. As in the teaching profession, you are responsible for writing question papers. In the conventional method, you write the question paper on paper, keep question papers separate from answers and all this information you have to keep in a locker to avoid unauthorized access. Using the Examination System you can create a question paper and everything will be written to a single exam file in encrypted format. You can set the General and Administrator password to avoid unauthorized access to your question paper. Every time you start the examination, the program shuffles all the questions and selects them randomly from the database, which reduces the chances of memorizing the questions.
NUMERICAL SIMULATIONS OF HEAT AND MASS TRANSFER IN CONDENSING HEAT EXCHANGERS...ssuser7dcef0
Power plants release a large amount of water vapor into the
atmosphere through the stack. The flue gas can be a potential
source for obtaining much needed cooling water for a power
plant. If a power plant could recover and reuse a portion of this
moisture, it could reduce its total cooling water intake
requirement. One of the most practical way to recover water
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plant could also recover latent heat due to condensation as well
as sensible heat due to lowering the flue gas exit temperature.
Additionally, harmful acids released from the stack can be
reduced in a condensing heat exchanger by acid condensation. reduced in a condensing heat exchanger by acid condensation.
Condensation of vapors in flue gas is a complicated
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various acids simultaneously occur in the presence of noncondensable
gases such as nitrogen and oxygen. Design of a
condenser depends on the knowledge and understanding of the
heat and mass transfer processes. A computer program for
numerical simulations of water (H2O) and sulfuric acid (H2SO4)
condensation in a flue gas condensing heat exchanger was
developed using MATLAB. Governing equations based on
mass and energy balances for the system were derived to
predict variables such as flue gas exit temperature, cooling
water outlet temperature, mole fraction and condensation rates
of water and sulfuric acid vapors. The equations were solved
using an iterative solution technique with calculations of heat
and mass transfer coefficients and physical properties.
Water billing management system project report.pdfKamal Acharya
Our project entitled “Water Billing Management System” aims is to generate Water bill with all the charges and penalty. Manual system that is employed is extremely laborious and quite inadequate. It only makes the process more difficult and hard.
The aim of our project is to develop a system that is meant to partially computerize the work performed in the Water Board like generating monthly Water bill, record of consuming unit of water, store record of the customer and previous unpaid record.
We used HTML/PHP as front end and MYSQL as back end for developing our project. HTML is primarily a visual design environment. We can create a android application by designing the form and that make up the user interface. Adding android application code to the form and the objects such as buttons and text boxes on them and adding any required support code in additional modular.
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Understanding Inductive Bias in Machine LearningSUTEJAS
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2. 2
ASSI
[Date]
ASSIGNMENT BREAF
The bridge shown above is a 48m long concrete beam bridge across the southern expressway, Sri
Lanka. The first interior support (B) is at 8m from the left embankment (A) while 2nd
and 3rd
interior
supports are at 24m and 40m from A respectively. It may be modelled as a continuous beam.
Assumptions
1- The bridge has one lane of width.
2- Support “A” on the left hand side is a pin support, while support “E” on the right hand side is a
roller.
3- All interior supports are pinned supports, but allows for the continuous beam action between the
two spans.
4- The geometrical cross-section of the bridge is the same from A to E.
5- The materials’ properties of the bridge is the same from A to E.
6- A lorry of 30 tonnes drives from A to E.
7- Assume that the lorry moves as a point load on the bridge.
8- Ignore the effect of self-weight of the bridge for the purpose of establishing the following
3. 3
ASSI
[Date]
QUESTIONS:
Use the ISSD software of structural analysis to establish the following:
1- Consider point “P” which is at 32m from A. Create the following table:
Position of lorry from A (m) Shear force at P (kN)
0
4
8
12
16
20
24
28
32
36
40
44
48
Plot a graph showing the position of the lorry on the x-axis and the shear force at P on the y-axis.
From the graph find the position of the lorry from point A which creates the maximum shearing force
at P.
Comment on the difference between this graph and the shear force diagram.
Follow the same approach as point 1 above to establish the following:
2- The position of the lorry measured from support “A” which will create the maximum uplift reaction
at E. Find the value of this reaction.
3- The position of the lorry measured from support “A” which will create the maximum hogging
bending moment at C. Find the value of this moment.
4- The position of the lorry measured from support “A” which will create the maximum sagging
bending moment at point “Q” which is at 12m from A.
Find the value of this moment.
5- Find the maximum value of sagging bending moment which may develop on the bridge as the
lorry moves from A to E. Find the position of the lorry from support A which will generate this
maximum value.
6. 6
ASSI
[Date]
Note:-
We cannot be obtained a result sheets, when applying the point loads at supports.
Because the point load at the support is act as an axial load for the support & Reaction
also in the same line of axial load. Therefore there is no Shear forces at the other supports
& spans, when load applying on a support.
Fig. 1.8
Fig. 1.7
7. 7
ASSI
[Date]
Results table 01:
Position of lorry from "A" (m)
Shear Force at "P"
(kN)
0 0
4 3.75
8 0
12 15
16 30
20 29.99
24 0
28 68.437
32 157.5
36 57.187
40 0
44 13.125
48 0
Graph of table 01:
Graph 01
Comment: According to the results of ISSD in 4m intervals we obtain the Table 01.As shown in
the graph 01. There should be a maximum Shear force value in magnitude. From ISSD we can
obtain the results in positive & negative values. But when we design the element, we consider the
maximum value in magnitude. So the maximum Shear force at 32m is 157.5 kN in magnitude.
(According to the ISSD)
0 3.75 0
15
30 29.99
0
68.437
157.5
57.187
0
13.125
0
-20
0
20
40
60
80
100
120
140
160
180
0 10 20 30 40 50 60
ShearForceat"32m"(kN)
Possition of the Lorry (m)
Shear Force at 32m away from "A"
10. 10
ASSI
[Date]
Note:-
We cannot be obtained a result sheets, when applying the point loads at supports.
Because the point load at the support is act as an axial load for the support & Reaction
also in the same line of axial load. Therefore there is no Reactions at the other supports,
when load applying on a support.
Fig. 2.7
Fig. 1.3
Fig. 1.1
Fig. 1.1
Fig. 2.8
Fig. 1.3
Fig. 1.1
Fig. 1.1
11. 11
ASSI
[Date]
Results table 02:
Position of lorry from "A" (m)
Maximum Uplift
Reaction at "E" (kN)
0 0
4 -1.875
8 0
12 7.5
16 15
20 15
24 0
28 -31.875
32 -60
36 -58.125
40 0
44 129.375
48 0
Graph of table 02:
Graph 02 (Reaction Positive & Uplift reaction Negative)
Comment: According to the results of ISSD in 4m intervals we obtain the Table 02.As shown in
the graph 02 there should be a maximum uplift reaction. From ISSD we can obtain the results in
1m intervals. So the maximum uplift reaction will be occurred at 34m & its magnitude is
64.453kN (according to the ISSD).
0 -1.875 0
7.5
15 15
0
-31.875
-60 -58.125
0
129.375
0
-100
-50
0
50
100
150
0 10 20 30 40 50 60
Reactionsatsupports"E"(kN)
Possition of the Lorry (m)
Maximum Uplift Reaction at "E" (kN)
14. 14
ASSI
[Date]
Note:-
We cannot be obtained a result sheets, when applying the point loads at supports.
Because the point load at the support is act as an axial load for the support & Reaction
also in the same line of axial load. Therefore there is no Bending moments at the other
supports & mid spans, when load applying on a support.
Fig. 3.7
Fig. 1.3
Fig. 1.1
Fig. 1.1
Fig. 3.8
Fig. 1.3
Fig. 1.1
Fig. 1.1
15. 15
ASSI
[Date]
Results table 03:
Position of lorry from "A" (m)
Maximum Hogging
Bending moment at
"C" (kNm)
0 0
4 44.99
8 0
12 -179.99
16 -359.99
20 -360
24 0
28 -359.99
32 -359.99
36 -179.99
40 0
44 44.99
48 0
Graph of table 03:
Graph 03 (Sagging Positive & Hogging Negative)
Comment: According to the results of ISSD in 4m intervals we obtain the Table 03. As shown in
the graph 03 there should be a maximum Hogging Bending moment. From ISSD we can obtain
the results in 1m intervals. So the maximum Hogging Bending moment will be occurred at
18m & 30m. Its magnitude is 393.750kNm (according to the ISSD).
0
44.99
0
-179.99
-359.99
-360
0
-359.99
-359.99
-179.99
0
44.99
0
-450
-400
-350
-300
-250
-200
-150
-100
-50
0
50
100
0 10 20 30 40 50 60
BendingMomentat"C"(kNm)
Possition of the Lorry (m)
Maximum Hogging Bending moment at "C" (kNm)
16. 16
ASSI
[Date]
0
-112.499
0
506.249
149.999
18.749
0 0 0 0 0 0 0
-200
-100
0
100
200
300
400
500
600
0 10 20 30 40 50 60
BendingMomentat"Q"
position of the lorry (m)
Maximum Sagging Bending moment at "Q" (kNm)
Question 04:
Bending Moments obtained from ISSD software are as same as the question 03 in fig. 3.1, fig.
3.2, fig. 3.3, fig. 3.4, fig. 3.5, fig. 3.6, fig. 3.7, fig. 3.8.
According to the results;
Results table 04:
Position of lorry from “A” (m)
Maximum Sagging
Bending moment at
“Q” (kNm)
0 0
4 -112.499
8 0
12 506.249
16 149.999
20 18.749
24 0
28 0
32 0
36 0
40 0
44 0
48 0
Graph of table 04:
Graph 04 (Sagging Positive & Hogging Negative)
17. 17
ASSI
[Date]
Question 05:
Bending Moments obtained from ISSD software are as same as the question 03 in fig. 3.1, fig.
3.2, fig. 3.3, fig. 3.4, fig. 3.5, fig. 3.6, fig. 3.7, fig. 3.8. According to the results the maximum
bending moment will occurred when the lorry is at 16m away from “A” & 32m away from “A”.
The Bending Moment Value is 779.99 kNm.
Fig 5.1
Fig 5.2
18. 18
ASSI
[Date]
Results table 05:
Position of lorry from "A" (m)
Maximum Sagging
Bending moment
(kNm)
0 0
4 517.499
8 0
12 506.249
16 779.999
20 566.249
24 0
28 566.25
32 779.999
36 506.249
40 0
44 517.499
48 0
Graph of table 05:
Graph 05 (Sagging Positive)
0
517.499
0
506.249
779.999
566.249
0
566.25
779.999
506.249
0
517.499
0
0
100
200
300
400
500
600
700
800
900
0 10 20 30 40 50 60
MaximumBendingMoment(kNm)
position of the lorry (m)
Maximum Sagging Bending moment (kNm)
19. 19
ASSI
[Date]
Results: Obtained from ISSD software in 4m intervals.
Question 01:
The position of the lorry from point “A” Which creates the maximum Shear force at “P” (“P” is 32m
away from point “A”)
Answer: When the lorry is at 32m from “A” creates the maximum Shear force & value is 157.5 kN.
Question 02:
The position of the lorry from point “A” Which creates the maximum Uplift Reaction at “E” (“E” is
48m away from point “A”)
Answer: When the lorry is at 32m from “A” creates the maximum Uplift Reaction & value is 60 kN.
Question 03:
The position of the lorry from point “A” Which creates the maximum Hogging Bending moment at
“C” (“C” is 24m away from point “A”)
Answer: When the lorry is at 16m, 20m, 28m & 32m from “A” creates the maximum Hogging
Bending moment & value is 360 kNm.
Question 04:
The position of the lorry from point “A” Which creates the maximum Sagging Bending moment at
“Q” (“Q” is 12m away from point “A”)
Answer: When the lorry is at 12m from “A” creates the maximum Sagging Bending moment &
value is 506.249 kNm.
Question 05:
The position of the lorry from point “A” Which creates the maximum Sagging Bending moment of
the bridge
Answer: When the lorry is at 16m, 32m from “A” creates the maximum Sagging Bending moment
& value is 779.999 kNm.
20. 20
ASSI
[Date]
Appendices: 1) Lorry is at 4m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 62.72
Node 2 : 0 0 -48.64
Node 3 : 0 0 12.8
Node 4 : 0 0 -2.56
Node 5 : 0 0 1.28
Node 6 : 0 162559.975 -3.52
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 2 , j= 3) : -164.999984 -44.999992 13.125 -44.999992 0
Member 2 (i= 3 , j= 4) : 44.999996 14.999998 -3.75 14.999998 0
Member 3 (i= 4 , j= 5) : -14.999999 0 1.875 0 0
Member 4 (i= 1 , j= 6) : 0 -517.499904 129.375 -517.499904 0
Member 5 (i= 2 , j= 6) : 165 517.499904 -170.625 517.499904 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 129.375 0
Node 2 : 0 183.75 0
Node 3 : 0 -16.875 0
Node 4 : 0 5.625 0
21. 21
ASSI
[Date]
Node 5 : 0 -1.875 0
2) Lorry is at 12m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 -39.68
Node 2 : 0 0 79.36
Node 3 : 0 0 -51.2
Node 4 : 0 0 10.24
Node 5 : 0 0 -5.12
Node 6 : 0 389759.941 74.08
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 464.999904 -58.125 464.999904 0
Member 2 (i= 3 , j= 4) : -179.999968 -59.999992 15 -59.999992 0
Member 3 (i= 4 , j= 5) : 59.999984 0 -7.5 0 0
Member 4 (i= 2 , j= 6) : -464.999808 -506.249728 242.812 -506.249728 0
Member 5 (i= 3 , j= 6) : 179.999952 506.249856 -57.187 506.249856 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 -58.125 0
Node 2 : 0 300.937 0
Node 3 : 0 72.187 0
22. 22
ASSI
[Date]
Node 4 : 0 -22.5 0
Node 5 : 0 7.5 0
3) Lorry is at 16m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 -40.96
Node 2 : 0 0 81.92
Node 3 : 0 0 -102.4
Node 4 : 0 0 20.48
Node 5 : 0 0 -10.24
Node 6 : 0 778239.93 5.12
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 479.999936 -60 479.999936 0
Member 2 (i= 3 , j= 4) : -359.999968 -119.999992 30 -119.999992 0
Member 3 (i= 4 , j= 5) : 119.999984 0 -15 0 0
Member 4 (i= 2 , j= 6) : -480 -779.999936 157.5 -779.999936 0
Member 5 (i= 3 , j= 6) : 359.999936 779.999872 -142.5 779.999872 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 -60 0
Node 2 : 0 217.5 0
Node 3 : 0 172.5 0
23. 23
ASSI
[Date]
Node 4 : 0 -45 0
Node 5 : 0 15 0
4) Lorry is at 20m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 -21.76
Node 2 : 0 0 43.52
Node 3 : 0 0 -102.4
Node 4 : 0 0 20.48
Node 5 : 0 0 -10.24
Node 6 : 0 435839.925 -76
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 254.999952 -31.875 254.999952 0
Member 2 (i= 3 , j= 4) : -359.999904 -119.999968 30 -119.999968 0
Member 3 (i= 4 , j= 5) : 119.999968 0 -15 0 0
Member 4 (i= 2 , j= 6) : -254.999968 -566.24992 68.437 -566.24992 0
Member 5 (i= 3 , j= 6) : 360 566.249856 -231.562 566.249856 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 -31.875 0
Node 2 : 0 100.313 0
24. 24
ASSI
[Date]
Node 3 : 0 261.562 0
Node 4 : 0 -45 0
Node 5 : 0 15 0
5) Lorry is at 28m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 10.24
Node 2 : 0 0 -20.48
Node 3 : 0 0 102.4
Node 4 : 0 0 -43.52
Node 5 : 0 0 21.76
Node 6 : 0 435839.925 76
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 -119.999968 15 -119.999968 0
Member 2 (i= 2 , j= 3) : 119.999968 359.999904 -30 359.999904 0
Member 3 (i= 4 , j= 5) : -254.999952 0 31.875 0 0
Member 4 (i= 3 , j= 6) : -360 -566.249856 231.562 -566.249856 0
Member 5 (i= 4 , j= 6) : 254.999968 566.24992 -68.437 566.24992 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 15 0
25. 25
ASSI
[Date]
Node 2 : 0 -45 0
Node 3 : 0 261.562 0
Node 4 : 0 100.313 0
Node 5 : 0 -31.875 0
6) Lorry is at 32m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 10.24
Node 2 : 0 0 -20.48
Node 3 : 0 0 102.4
Node 4 : 0 0 -81.92
Node 5 : 0 0 40.96
Node 6 : 0 778239.93 -5.12
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 -119.999984 15 -119.999984 0
Member 2 (i= 2 , j= 3) : 119.999992 359.999968 -30 359.999968 0
Member 3 (i= 4 , j= 5) : -479.999936 0 60 0 0
Member 4 (i= 3 , j= 6) : -359.999936 -779.999872 142.5 -779.999872 0
Member 5 (i= 4 , j= 6) : 480 779.999936 -157.5 779.999936 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
Rhor [kN] Rvert [kN] RAng. [kNm]
26. 26
ASSI
[Date]
Node 1 : 0 15 0
Node 2 : 0 -45 0
Node 3 : 0 172.5 0
Node 4 : 0 217.5 0
Node 5 : 0 -60 0
7) Lorry is at 36m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 5.12
Node 2 : 0 0 -10.24
Node 3 : 0 0 51.2
Node 4 : 0 0 -79.36
Node 5 : 0 0 39.68
Node 6 : 0 389759.941 -74.08
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 -59.999984 7.5 -59.999984 0
Member 2 (i= 2 , j= 3) : 59.999992 179.999968 -15 179.999968 0
Member 3 (i= 4 , j= 5) : -464.999904 0 58.125 0 0
Member 4 (i= 3 , j= 6) : -179.999952 -506.249856 57.187 -506.249856 0
Member 5 (i= 4 , j= 6) : 464.999808 506.249728 -242.812 506.249728 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'
27. 27
ASSI
[Date]
Rhor [kN] Rvert [kN] RAng. [kNm]
Node 1 : 0 7.5 0
Node 2 : 0 -22.5 0
Node 3 : 0 72.187 0
Node 4 : 0 300.937 0
Node 5 : 0 -58.125 0
8) Lorry is at 44m from “A”
*************** NODE DISPLACEMENTS : ***************'
X [mm] Y [mm] Ang. [rad]
Node 1 : 0 0 -1.28
Node 2 : 0 0 2.56
Node 3 : 0 0 -12.8
Node 4 : 0 0 48.64
Node 5 : 0 0 -62.72
Node 6 : 0 162559.975 3.52
*************** MEMBER FORCES : ***************'
Mi [kNm] Mj [KNm] Ti [kN] Tj [kN] N [kN]
Member 1 (i= 1 , j= 2) : 0 14.999998 -1.875 14.999998 0
Member 2 (i= 2 , j= 3) : -14.999997 -44.999992 3.75 -44.999992 0
Member 3 (i= 3 , j= 4) : 44.999988 164.999968 -13.125 164.999968 0
Member 4 (i= 4 , j= 6) : -164.999936 -517.49984 170.625 -517.49984 0
Member 5 (i= 5 , j= 6) : 0 517.499872 -129.375 517.499872 0
*************** VALUES OF THE MOMENTS AT MIDDLE DISTANCE FOR MEMBERS WITH UNIFORM LOADS : ***************'
Mi(x=0) [kNm] M(L/5) [KNm] M(2L/5) [KNm] M(3L/5) [KNm] M(4L/5) [KNm] Mj(x=L) [KNm] Mmin [KNm] M=0 for x=
[mm]
*************** REACTIONS : ***************'