Lecture Slides - Mechanical Engineeringme.utep.edu/cmstewart/documents/ME3334/Lecture 18 -...
Transcript of Lecture Slides - Mechanical Engineeringme.utep.edu/cmstewart/documents/ME3334/Lecture 18 -...
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Shigley’s Mechanical Engineering Design
Chapter 9
Welding, Bonding, and the
Design of Permanent Joints
Lecture Slides
© 2015 by McGraw-Hill Education. This is proprietary material solely for authorized instructor use. Not authorized for sale or distribution in any manner. This document may not be
copied, scanned, duplicated, forwarded, distributed, or posted on a website, in whole or part.
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Shigley’s Mechanical Engineering Design
Chapter Outline
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Shigley’s Mechanical Engineering Design
Welding Symbols
Welding symbol standardized by American Welding Society
Specifies details of weld on machine drawings
Fig. 9–4
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Shigley’s Mechanical Engineering Design
Welding Symbols
Fig. 9–1
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Shigley’s Mechanical Engineering Design
Welding Symbols
Arrow side of a joint is the line, side, area, or near member to
which the arrow points
The side opposite the arrow side is the other side
Shape of weld is shown with the symbols below
Fig. 9–2
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Shigley’s Mechanical Engineering Design
Welding Symbol Examples
Weld leg size of 5 mm
Fillet weld
Both sides
Intermittent and
staggered 60 mm along
on 200 mm centers
Leg size of 5 mm
On one side only
(outside)
Circle indicates all the
way around
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Shigley’s Mechanical Engineering Design
Welding Symbol Examples
Fig. 9–5
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Shigley’s Mechanical Engineering Design
Welding Symbol Examples
Fig. 9–6
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Shigley’s Mechanical Engineering Design
Tensile Butt Joint
Simple butt joint loaded in tension or compression
Stress is normal stress
Throat h does not include extra reinforcement
Reinforcement adds some strength for static loaded joints
Reinforcement adds stress concentration and should be ground
off for fatigue loaded joints
Fig. 9–7a
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Shigley’s Mechanical Engineering Design
Shear Butt Joint
Simple butt joint loaded in shear
Average shear stress
Fig. 9–7b
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Shigley’s Mechanical Engineering Design
Transverse Fillet Weld
Joint loaded in tension
Weld loading is complex
Fig. 9–8
Fig. 9–9
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Shigley’s Mechanical Engineering Design
Transverse Fillet Weld
Summation of forces
Law of sines
Solving for throat thickness t
Fig. 9–9
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Shigley’s Mechanical Engineering Design
Transverse Fillet Weld
Nominal stresses at angle q
Von Mises Stress at angle q
Fig. 9–9
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Shigley’s Mechanical Engineering Design
Transverse Fillet Weld
Largest von Mises stress occurs at q = 62.5º with value of
s' = 2.16F/(hl)
Maximum shear stress occurs at q = 67.5º with value of
tmax = 1.207F/(hl)
Fig. 9–9
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Shigley’s Mechanical Engineering Design
Experimental Stresses in Transverse Fillet Weld
Experimental results are more complex
Fig. 9–10
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Shigley’s Mechanical Engineering Design
Transverse Fillet Weld Simplified Model
No analytical approach accurately predicts the experimentally
measured stresses.
Standard practice is to use a simple and conservative model
Assume the external load is carried entirely by shear forces on
the minimum throat area.
By ignoring normal stress on throat, the shearing stresses are
inflated sufficiently to render the model conservative.
By comparison with previous maximum shear stress model, this
inflates estimated shear stress by factor of 1.414/1.207 = 1.17.
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Shigley’s Mechanical Engineering Design
Parallel Fillet Welds
Same equation also applies for simpler case of simple shear
loading in fillet weld
Fig. 9–11
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Shigley’s Mechanical Engineering Design
Fillet Welds Loaded in Torsion
Fillet welds carrying both direct shear V and moment M
Primary shear
Secondary shear
A is the throat area of all welds
r is distance from centroid of weld group to point of interest
J is second polar moment of area of weld group about centroid of group
Fig. 9–12
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Shigley’s Mechanical Engineering Design
Example of Finding A and J
Rectangles represent
throat areas. t = 0.707 h
Fig. 9–13
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Shigley’s Mechanical Engineering Design
Example of Finding A and J
Note that t3 terms will be
very small compared to
b3 and d3
Usually neglected
Leaves JG1 and JG2 linear
in weld width
Can normalize by
treating each weld as a
line with unit thickness t
Results in unit second
polar moment of area, Ju
Since t = 0.707h,
J = 0.707hJuFig. 9–13
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Shigley’s Mechanical Engineering Design
Common Torsional Properties of Fillet Welds (Table 9–1)
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Shigley’s Mechanical Engineering Design
Common Torsional Properties of Fillet Welds (Table 9–1)
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–14
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–15
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–15
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–15
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Shigley’s Mechanical Engineering Design
Example 9–1
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–16
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Shigley’s Mechanical Engineering Design
Example 9–1
Fig. 9–16
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Shigley’s Mechanical Engineering Design
Fillet Welds Loaded in Bending
Fillet welds carry both shear V and moment M
Fig. 9–17
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Shigley’s Mechanical Engineering Design
Bending Properties of Fillet Welds (Table 9–2)
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Shigley’s Mechanical Engineering Design
Bending Properties of Fillet Welds (Table 9–2)
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Shigley’s Mechanical Engineering Design
Strength of Welded Joints
Must check for failure in parent material and in weld
Weld strength is dependent on choice of electrode material
Weld material is often stronger than parent material
Parent material experiences heat treatment near weld
Cold drawn parent material may become more like hot rolled in
vicinity of weld
Often welded joints are designed by following codes rather than
designing by the conventional factor of safety method
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Shigley’s Mechanical Engineering Design
Minimum Weld-Metal Properties (Table 9–3)
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Shigley’s Mechanical Engineering Design
Stresses Permitted by the AISC Code for Weld Metal
Table 9–4
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Shigley’s Mechanical Engineering Design
Fatigue Stress-Concentration Factors
Kfs appropriate for application to shear stresses
Use for parent metal and for weld metal
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Shigley’s Mechanical Engineering Design
Allowable Load or Various Sizes of Fillet Welds (Table 9–6)
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Shigley’s Mechanical Engineering Design
Minimum Fillet Weld Size, h (Table 9–6)
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Shigley’s Mechanical Engineering Design
Example 9–2
Fig. 9–18
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Shigley’s Mechanical Engineering Design
Example 9–2
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Shigley’s Mechanical Engineering Design
Example 9–2
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Shigley’s Mechanical Engineering Design
Example 9–3
Fig. 9–19
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Shigley’s Mechanical Engineering Design
Example 9–3
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Shigley’s Mechanical Engineering Design
Example 9–3
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Shigley’s Mechanical Engineering Design
Example 9–3
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Shigley’s Mechanical Engineering Design
Example 9–3
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Shigley’s Mechanical Engineering Design
Example 9–3
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Shigley’s Mechanical Engineering Design
Example 9–4
Fig. 9–20
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Shigley’s Mechanical Engineering Design
Example 9–4
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Shigley’s Mechanical Engineering Design
Example 9–4
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Shigley’s Mechanical Engineering Design
Example 9–4
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Shigley’s Mechanical Engineering Design
Example 9–5
Fig. 9–21
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Shigley’s Mechanical Engineering Design
Example 9–5
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Shigley’s Mechanical Engineering Design
Example 9–5
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Shigley’s Mechanical Engineering Design
Example 9–6
Fig. 9–22
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Shigley’s Mechanical Engineering Design
Example 9–6
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Shigley’s Mechanical Engineering Design
Example 9–6
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Shigley’s Mechanical Engineering Design
Resistance Welding
Welding by passing an electric current through parts that are
pressed together
Common forms are spot welding and seam welding
Failure by shear of weld or tearing of member
Avoid loading joint in tension to avoid tearing
Fig. 9–23
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Shigley’s Mechanical Engineering Design
Adhesive Bonding
Adhesive bonding has unique advantages
Reduced weight, sealing capabilities, reduced part count, reduced
assembly time, improved fatigue and corrosion resistance, reduced
stress concentration associated with bolt holes
Fig. 9–24
From A. V. Pocius, Adhesion and
Adhesives Technology, 2nd edition,
Hanser Publishers, Munich,
2002. Reprinted by permission.
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Shigley’s Mechanical Engineering Design
Types of Adhesives
May be classified by
◦ Chemistry
Epoxies, polyurethanes, polyimides
◦ Form
Paste, liquid, film, pellets, tape
◦ Type
Hot melt, reactive hot melt, thermosetting, pressure sensitive,
contact
◦ Load-carrying capability
Structural, semi-structural, non-structural
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Shigley’s Mechanical Engineering Design
Mechanical Performance of Various Types of Adhesives
Table 9–7Source: From A. V. Pocius,
Adhesion and Adhesives
Technology, 2nd ed., Hanser
Gardner Publishers, Ohio,
2002. Reprinted by
permission.
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Shigley’s Mechanical Engineering Design
Stress Distributions
Adhesive joints are much stronger
in shear loading than tensile loading
Lap-shear joints are important for
test specimens and for practical
designs
Simplest analysis assumes uniform
stress distribution over bonded area
Most joints actually experience
significant peaks of stress
Fig. 9–25
Adapted from R. D. Adams,
J. Comyn, and W. C. Wake,
Structural Adhesive Joints
in Engineering, 2nd ed.,
Chapman and Hall,
New York, 1997.
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Shigley’s Mechanical Engineering Design
Double-lap Joint
Classic analysis of double-lap joint known as shear-lag model
Double joint eliminates complication of bending from
eccentricity
Fig. 9–26
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Shigley’s Mechanical Engineering Design
Double-lap Joint
Shear-stress distribution is given by
Fig. 9–26b
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Shigley’s Mechanical Engineering Design
Example 9–7
Fig. 9–26
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Shigley’s Mechanical Engineering Design
Example 9–7
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Shigley’s Mechanical Engineering Design
Example 9–7
Fig. 9–27
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Shigley’s Mechanical Engineering Design
Example 9-7
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Shigley’s Mechanical Engineering Design
Example 9-7
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Shigley’s Mechanical Engineering Design
Single-lap Joint
Eccentricity introduces bending
Bending can as much as double the resulting shear stresses
Near ends of joint peel stresses can be large, causing joint failure
Fig. 9–28
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Shigley’s Mechanical Engineering Design
Single-lap Joint
Shear and peal stresses in single-lap joint, as calculated by Goland
and Reissner
Volkersen curve is for double-lap joint
Fig. 9–28 J. Appl. Mech.,
vol. 77, 1944
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Shigley’s Mechanical Engineering Design
Adhesive Joint Design Guidelines
Design to place bondline in shear, not peel.
Use adhesives with adequate ductility to reduce stress
concentrations and increase toughness to resist debond
propagation.
Recognize environmental limitations of adhesives and surface
preparation.
Design to facilitate inspection.
Allow sufficient bond area to tolerate some debonding before
becoming critical.
Attempt to bond to multiple surfaces to support loads in any
direction.
Consider using adhesives in conjunction with spot welds, rivets, or
bolts.
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Shigley’s Mechanical Engineering Design
Design Ideas for Improved Bonding
Fig. 9–29
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Shigley’s Mechanical Engineering Design
Design Ideas for Improved Bonding
Fig. 9–29
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Shigley’s Mechanical Engineering Design
Design Ideas for Improved Bonding
Fig. 9–29