strength of material (shrinked)
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Strength of Materials
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Modulus TypesModulus: Slope of the stress-strain curve
Initial Modulus: slope of the curve drawn at the origin. Tangent Modulus: slope of the curve drawn at the tangent of the curve at some point.
Secant Modulus: Ratio of stress to strain at any point on curve in a stress-straindiagram. It is the slope of a line from the origin to any point on a stress-straincurve.
Stress
Strain
Initial Modulus
Tangent Modulus
Secant Modulus
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Various regions and points on the stress-strain curve.
Strain ( ) (e/Lo)
41
2
3
5
ElasticRegion
PlasticRegion
StrainHardening Fracture
ultimatetensilestrength
Elastic regionslope=Youngs(elastic) modulus yield strength
Plastic regionultimate tensile strengthstrain hardeningfracture
necking
yieldstrength
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1.True elastic limit based on micro strain measurements at strains onorder of 2 x 10 -6 in | in. This elastic limit is a very low value and isrelated to the motion of a few hundred dislocations.
2.Proportional limit is the highest stress at which stress is directlyproportional to strain.
3.Elastic limit is the greatest stress the material can withstand withoutany measurable permanent strain remaining on the complete release ofload. With increasing sensitivity of strain measurement, the value of theelastic limit is decreased until at the limit it equals the true elastic limitdetermined from micro strain measurements. With the sensitivity ofstrain usually employed in engineering studies (10 -4 in | in), the elasticlimit is greater than the proportional limit.
1.The yield strength is the stress required to produce a small-specifiedamount of plastic deformation.The usual definition of this property is the offset yield strength determined by the stress corresponding to the intersection of the stress-strain curve and a line parallel to the elastic part of the curve offset by a
specified strain (Fig. 1).
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Stainless Steel E= 28.5 million psi (196.5 GPa) Aluminum E= 10 million psi Brass E= 16 million psi Copper E= 16 million psi Molybdenum E= 50 million psi
Nickel E= 30 million psi Titanium E= 15.5 million psi Tungsten E= 59 million psi Carbon fiber E= 40 million psi Glass E= 10.4 million psi Composites E= 1 to 3 million psi Plastics E= 0.2 to 0.7 million psi
Stress- strain diagrams for various materials
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Universal Testing Machine
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Area in red indicates intensity of stress
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Equipment to measure Stress-Strain Strainometers: measures dimensional changes that
occur during testing extensometers, deflectometers, and compressometers measurechanges in linear dimensions.
load cells measure load data is recorded at several readings and the results averaged,
e.g., 10 samples per second during the test.
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M ater ial Proper ties
There a 5 properties typically used to describe a materials behavior and capabilities:
1. Strength2. Hardness3. Ductility4. Brittleness5. Toughness
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The ability to resist deformation and maintainits shape
1. Strength
-Given in terms of the yield strength, s y, or theultimate tensile strength, s ult
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The ability to resist indentation, abrasion, and wear
2. Hardness
STRENGTH and HARDNESS are related! A high-strength material is typicallyresistant to wear and abrasion...
- For metals, this is determined with the RockwellHardness or Brinell tests that measure indentation/
penetration under a load
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Material Brinell Hardness
Pure Aluminum 15
Pure Copper 35
Mild Steel 120
304 Stainless Steel 250
Hardened Tool Steel 650/700
Hard Chromium Plate 1000
Chromium Carbide 1200
Tungsten Carbide 1400
Titanium Carbide 2400
Diamond 8000
Sand 1000
A comparison of hardness of some typical materials:
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The ability to deform before ultimate failure
3. Ductility
Ductile materials can be pulled or drawn into pipes, wire,and other structural shapes
Ductile materials include copper, aluminum,and brass
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The inability to deform before ultimate failure
4. Brittleness
Brittleness is the LACK of ductility ...
- The opposite of ductility, brittle materials deform little before ultimately fracturing
- Brittle materials include glass and cast iron
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The ability to absorb energy
5. Toughness
Toughness and Ductility/brittleness are related!
Brittle things. ...are not tough!
- Material Toughness (slow absorption)- not a readily observable property- Defined by the area under the stress-strain curve
- Impact Toughness (rapid absorption)- Ability to absorb energy of an impactwithout fracturing
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StiffnessStiffness is a measure of the materials ability to resist deformation under load asmeasured in stress.
Stiffness is measures as the slope of the stress-strain curve
Hookean solid: (like a spring) linear slope
steel
aluminumiron
copper
Stiffness is usually measured by the Modulus of Elasticity(Stress/strain)
Steel is stiff (tough to bend).
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Analysis and Designof Beams for Bending
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Introduction
Beams - structural members supporting loads atvarious points along the member
Objective - Analysis and design of beams
Transverse loadings of beams are classified asconcentrated loads or distributed loads
Applied loads result in internal forces consistingof a shear force (from the shear stressdistribution) and a bending couple (from thenormal stress distribution)
Normal stress is often the critical design criteria
Requires determination of the location andmagnitude of largest bending moment
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Classification of Beam Supports
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Shear and Bending Moment Diagrams
Determination of maximum normal and
shearing stresses requires identification ofmaximum internal shear force and bendingcouple.
Shear force and bending couple at a point aredetermined by passing a section through the
beam and applying an equilibrium analysis onthe beam portions on either side of thesection.
Sign conventions for shear forces V and V
and bending couples M and M
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Quantifying Bending Stress
Compression
Tension
Sagging condition
Neutral Axis
y
A
B
A
B
Bending Stress :M : Bending MomentI : 2 nd Moment of area of the cross sectiony : Vertical distance from the neutral axis
: tensile ( +) or compressive( -) stress
y
L i di l B di S
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Quantifying Bending Stress
Hogging condition y
Compression
Tension
Neutral Axi s
AB
A
B
Neutral Axis : geometric centroid of the cross section ortransition between compression and tension
Logitudinal Bending Stress
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Torsion
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ContentsTorsional Loads on Circular
Shafts
Net Torque Due to InternalStresses
Axial Shear Components Shaft Deformations
Shearing Strain
Stresses in Elastic Range Normal Stresses
Torsional Failure Modes
Angle of Twist in Elastic Range
Design of Transmission Shafts
Stress Concentrations
Torsion of Noncircular Members
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Torsional Loads on Circular Shafts Stresses and strains of circular
shafts subjected to twisting couplesor torques
Generator creates an equal andopposite torque T
Shaft transmits the torque to thegenerator
Turbine exerts torque T on the shaft
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Net Torque Due to Internal Stresses Net of the internal shearing stresses is an
internal torque, equal and opposite to theapplied torque,
Although the net torque due to the shearingstresses is known, the distribution of the stressesis not
Unlike the normal stress due to axial loads, thedistribution of shearing stresses due to torsionalloads can not be assumed uniform.
Distribution of shearing stresses is staticallyindeterminate must consider shaft
deformations
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Axial Shear Components Torque applied to shaft produces shearing
stresses on the faces perpendicular to theaxis.
The existence of the axial shear components isdemonstrated by considering a shaft made upof axial slats.
The slats slide with respect to each other whenequal and opposite torques are applied to theends of the shaft.
Conditions of equilibrium require theexistence of equal stresses on the faces of the
two planes containing the axis of the shaft
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From observation, the angle of twist of theshaft is proportional to the applied torque andto the shaft length.
Shaft Deformations
When subjected to torsion, every cross-sectionof a circular shaft remains plane andundistorted.
Cross-sections of noncircular (non-axisymmetric) shafts are distorted whensubjected to torsion.
Cross-sections for hollow and solid circularshafts remain plain and undistorted because acircular shaft is axisymmetric.
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Shearing Strain Consider an interior section of the shaft. As a
torsional load is applied, an element on theinterior cylinder deforms into a rhombus.
Shear strain is proportional to twist and radius
It follows that
Since the ends of the element remain planar,the shear strain is equal to angle of twist.
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Stresses in Elastic Range
Recall that the sum of the moments fromthe internal stress distribution is equal tothe torque on the shaft at the section,
The results are known as the elastic torsionformulas,
Multiplying the previous equation by theshear modulus,
From Hookes Law, , so
The shearing stress varies linearly with theradial position in the section.
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Torsional Failure Modes
Ductile materials generally fail inshear. Brittle materials are weaker intension than shear.
When subjected to torsion, a ductilespecimen breaks along a plane ofmaximum shear, i.e., a plane
perpendicular to the shaft axis.
When subjected to torsion, a brittle
specimen breaks along planes perpendicular to the direction inwhich tension is a maximum, i.e.,along surfaces at 45 o to the shaftaxis.
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Design of Transmission Shafts Principal transmission shaft
performance specifications are:- power- speed
Determine torque applied to shaft at
specified power and speed,
Find shaft cross-section which will notexceed the maximum allowableshearing stress,
Designer must select shaft
material and cross-section tomeet performance specificationswithout exceeding allowableshearing stress.
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Stress Concentrations The derivation of the torsion formula,
assumed a circular shaft with uniformcross-section loaded through rigid end
plates.
Experimental or numerically determined
concentration factors are applied as
The use of flange couplings, gears and pulleys attached to shafts by keys inkeyways, and cross-section discontinuitiescan cause stress concentrations
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Torsion of Noncircular Members
At large values of a/b , the maximumshear stress and angle of twist for otheropen sections are the same as arectangular bar.
For uniform rectangular cross-sections,
Previous torsion formulas are valid foraxisymmetric or circular shafts
Planar cross-sections of noncircularshafts do not remain planar and stressand strain distribution do not varylinearly
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Plastics
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Why Plastics?
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Why Plastics?
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Source: Automotive Plastics Report2000
Plastics Applications
2000 2010
Segment M Lb. M Lb. M Lb.
Interior 1,688 2,021 +333
Body 1,181 1,601 +420
Underhood 388 627 +239Chassis 961 1,195 +234
Total 4,217 5,444 1,226
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Specific Gravity
Steel 7.8
Aluminum 2.6
Magnesium 1.75
Plastics 0.9 - 1.6
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Automotive Plastics Basicsfor
Exteriors
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Selection Considerations
Physical Properties
Chemistry
Process Characteristics
Relative Part or System Cost
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Most Common of the Approx. 60Commercial Families of Plastic Matls
AcrylonitrileButadiene Styrene(ABS)
Acetal (POM) Acrylics (PMMA) Fluoropolymer
(PTFE)
Ionomer Nylon (PA)
Phenolic Polycarbonate (PC)
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Most Common of the Approx. 60Commercial Families of Plastic Matls
Polyester (PBT, PET) Polyester Thermoset
(SMC, BMC) Polyethylene (PE) Polyphenyleneoxide
(PPO) Polypropylene (PP)
Polystyrene (PS) Polyurethane (PUR)
Polyvinylchloride(PVC)
Styrene Acrylonitrile(SAN)
Vinyl Ester
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Source: Automotive Plastics Report2000
Plastics Applications
2000 2010
Segment M Lb. M Lb. M Lb.
Interior 1,688 2,021 +333
Body 1,181 1,601 +420
Underhood 388 627 +239Chassis 961 1,195 +234
Total 4,217 5,444 1,226
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Primary Processing Methods
Blow Molding Calendaring
Casting Compression Molding Extrusion
Reaction InjectionMolding Injection Molding
Powder or SlushMolding
Thermoforming Filament Winding Pultrusion Resin Transfer
Molding Rotational Molding
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Fatigue (Failure under fluctuating / cyclic stresses)
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Fatigue occurs when a material is subjected to alternatingstresses, over a long period of time.
Under fluctuating / cyclic stresses, failure can occur at loadsconsiderably lower than tensile or yield strengths of material under astatic load.
Estimated to causes 90% of all failures of metallic structures(bridges, aircraft, machine components, etc.)
Fatigue failure is brittle-like (relatively little plastic deformation) -even in normally ductile materials. Thus sudden and catastrophic!
Examples: springs, turbine blades, airplane wings, bridges and bones
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Fatigue does not always lead to failure
Failure can occur if the stress surpasses theendurance limit of the material[Endurance Limit (Sn): Is the stress value below which an infinite number
of cycles will not cause failure]
Steel will not fail if the endurance limit is not passed
Aluminum will eventually fail regardless of theendurance limit
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Cycl ic Stresses There are three common ways in which stresses may be applied:
axial (tension or compression), torsional (twisting),or flextural (bending)Examples of these are seen in Fig. 1.
Figure 1 Visual examples of axial stress, torsional stress, and flexural stress.
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TheS-NCurve :
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The S N Curve :A very useful way to visualize time to failure for a specific material is with the S-Ncurve.The " S-N " means str ess v/s cycles to f ailur e , which when plotted uses the stress
amplitude,s
a plotted on the vertical axis and the logarithm of the number of cycles tofailure.An important characteristic to this plot as seen in Fig. 2 is the fatigue limit
Figure 2 A S-N Plot for an aluminum alloy
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Other important terms are - fatigue strength and fatigue life .
The stress at which failure occurs for a given number of cyclesis the fatigue str ength .
The number of cycles required for a material to fail at a certainstress in fatigue li fe .
Signif icance of the fatigue l imit : If the material is loaded below this stress, then it will not fail,
regardless of the number of times it is loaded.
Material such as aluminum, copper and magnesium do notshow a fatigue limit, therefore they will fail at any stress and numberof cycles.
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S-N Cur ve for F er rous v/s non-fer rous metals
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Stages of creep
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1. Instantaneous deformation :mainly elastic.
2. Primary/transient creep :Slope of strain vs. time decreases with time: work-hardening
3. Secondary/steady-state creep :Rate of straining is constant: balance of work-hardening and recovery .
4. Tertiary:
Rapidly accelerating strain rate up to failure:formation of internal cracks, voids, grain boundary separation, necking, etc.
Parameters of creep behavior
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The stage secondary/steady-state creep is of longest duration and the steady-statecreep rate is the most important parameter of the creep behavior in long-life applications.Another parameter, especially important in short-life creep situations, is time to rupture, or the
rupture lifetime, tr. t / s . e . = e &
d ff
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Creep: stress and temperature effects With increasing stress or temperature:
The instantaneous strain increasesThe steady-state creep rate increasesThe time to rupture decreases
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All f hi h
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Alloys for high-temperature use (turbines in jet engines, hypersonic airplanes, nuclear reactors, etc.)
Creep is generally minimized in materials with: High melting temperature High elastic modulus Large grain sizes (inhibits grain boundary sliding)
Following materials are especially resilient to creep: Stainless steels
Refractory metals (containing elements of high melting point,like Nb, Mo, W, Ta) Superalloys (Co, Ni based: solid solution hardening and
secondary phases)
5.6 Design Philosophy
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Loading known and geometry specified Specifyfactor of safety, N, and determine material.
Loading known and material specified Specifyfactor of safety, N, and determine requiredgeometry.
Loading known and material and geometryspecified Determine factor of safety Is itsafe??
Design
AnalysisAlso check de f lec t ion ! !
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5.8 Failure Theories
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Uniaxial: Bi-axial:or
1. Maximum Normal Stress
2. Modified Mohr
3. Yield strength
4. Maximum shear stress
5. Distortion energy
6. Goodman
7. Gerber
8. Soderberg
Ductile or Brittle
Dynamic or Static
FatigueLoading
Theory to use depends on:
StaticLoading
FailureTheory:
When to Use? Failure When: Design Stress:
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1. MaximumNormal Stress
Brittle Material/ UniaxialStatic Stress
2. Yield Strength
(Basis for MCH T213)
Ductile Material/
Uniaxial Static NormalStress
3. Maximum ShearStress (Basis forMCH T 213)
Ductile Material/ Bi-axial Static Stress
4. Distortion Energy(von Mises)
Ductile Material/ Bi-axial Static Stress
5. GoodmanMethod
Ductile Material/Fluctuating NormalStress (Fatigue Loading)
Ductile Material/Fluctuating Shear Stress(Fatigue Loading)
Ductile Material/Fluctuating CombinedStress (Fatigue Loading)
Failure Theories for STATIC Loading
Uniaxial: Bi-axial:or
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FailureTheory:
When Use? Failure When: Design Stress:
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1. MaximumNormal Stress
Brittle Material/ UniaxialStatic Stress
2. Yield Strength
(Basis for MCH T213)
Ductile Material/
Uniaxial Static NormalStress
3. Maximum ShearStress (Basis forMCH T 213)
Ductile Material/ Bi-axial Static Stress
4. Distortion Energy(von Mises)
Ductile Material/ Bi-axial Static Stress
5. GoodmanMethod
a. Ductile Material/Fluctuating NormalStress (Fatigue Loading)
b. Ductile Material/Fluctuating Shear Stress(Fatigue Loading)
c. Ductile Material/Fluctuating CombinedStress (Fatigue Loading)
Comparison of Static Failure Theories:
Shows no failure zones
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Maximum Shear most conservative
Th G d Di diff b f il
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The Goodman Diagram - note difference between no failurezone and safe zone
s m
s a
General Comments:
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1. Failure theory to use depends on material (ductile vs. brittle) and type of loading (static ordynamic). Note, ductile if elongation > 5%.
2. Ductile material static loads ok to neglect Kt (stress concentrations)
3. Brittle material static loads must use Kt
4. Terminology:
Su (or Sut) = ultimate strength in tension
Suc = ultimate strength in compression
Sy = yield strength in tension
Sys = 0.5*Sy = yield strength in shear
Sus = 0.75*Su = ultimate strength in shear
Sn = endurance strength = 0.5*Su or get from Fig 5-8 or S-N curve
S n = estimated actual endurance strength = Sn(C m) (C st ) (C R) (C s)
Ssn = 0.577* Sn = estimated actual endurance strength in shear
5.9 What Failure Theory to Use:
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THANK YOU