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EME 2056 Theory of Machines
EME 2056 Theory of Machines
Chapter 5:
Static Force Analysis
Lectured by: K.W. Liew
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Learning Outcome of Chapter 5Learning Outcome of Chapter 5
Analyse the static force of the linkage and slider-crank mechanism.
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ContentsContents
5.1. Introduction5.2. Forces5.3. Moment of a Force5.4. Free-Body Diagrams5.5. Static Equilibrium5.6. Two- and Three-Force Members5.7. Force Analysis5.8. Sliding Friction Force
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5.1 Introduction5.1 Introduction
The general function of any machine is to transmit motion and forces from an actuator to the components that perform the desired task.
Example:Escalator used in many commercial building –
Electrical power is fed into motors, which drive mechanisms that move and fold the stairs. The task is to safely and efficiently move people up and down at multilevel buildings.
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5.1 Introduction5.1 Introduction
A critical task in the design of machines is to ensure that the strength of the links and joints is sufficient to withstand the forces imposed on them. Therefore, a full understanding of the forces in the various components of a machine is vital.
This chapter deal with the force analysis in mechanisms without accelerations, or where the accelerations can neglected. This condition is termed static equilibrium.
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5.1 Introduction5.1 Introduction
Static equilibrium is applicable in many machines where movement is relatively slow.
Examples: clamps, latches, support linkages, and many hand-operated tools, such as pliers and cutters.
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5.2 Forces5.2 Forces
A force is a vector quantity that represents a pushing or pulling action on a part.
Being a vector, this force is defined by a magnitude and a direction of the pulling action.
Unit SI, the primary unit used is the Newton (N).
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Scalar Notation-
Since the x and y axes are designated positive
and negative directions.-
The magnitude and directional sense of the
rectangular components of a force can be expressed in terms of algebraic scalars.Eg: Sense of direction along positive x and y axes
yx FFF
5.2 Forces5.2 Forces
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Scalar NotationEg: Sense of direction along positive x and negative y axes
yx FFF '''
5.2 Forces5.2 Forces
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Scalar Notation-
Head of a vector arrow = sense of the
vector graphically (algebraic signs not used)-
Vectors are designated using boldface
notations-
Magnitudes (always a positive quantity)
are designated using italic symbols
5.2 Forces5.2 Forces
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Cartesian Vector Notation-
Cartesian unit vectors i
and j
are used to designate
the x and y directions
-
Unit vectors i
and j
have dimensionless magnitude of unity ( = 1 )
-
Their sense are indicated by a positive or negative sign (pointing in the positive or negative x or y axis)
-
Magnitude is always a positive quantity, represented by scalars Fx and Fy
5.2 Forces5.2 Forces
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Cartesian Vector Notation F
= Fx i
+ Fy j F’ = F’x i
+ F’y(-j)
F’ = F’x i
–
F’y j
5.2 Forces5.2 Forces
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Coplanar Force Resultants To determine resultant of several coplanar
forces:-
Resolve force into x and y components
-
Addition of the respective components using scalar algebra
5.2 Forces5.2 Forces
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Coplanar Force Resultants Example: Consider three coplanar
forces
Cartesian vector notationF1
= F1x i + F1y j
F2
= -
F2x i + F2y j
F3
= F3x i –
F3y j
5.2 Forces5.2 Forces
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Coplanar Force Resultants Vector resultant is therefore
FR
= F1
+ F2
+ F3
= F1x i
+ F1y j -
F2x i
+ F2y j + F3x i
–
F3y j= (F1x -
F2x + F3x )i
+ (F1y + F2y –
F3y )j
= (FRx )i
+ (FRy )j
5.2 Forces5.2 Forces
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Coplanar Force Resultants If scalar notation are used
FRx = (F1x -
F2x + F3x )FRy = (F1y + F2y –
F3y )
In all cases,FRx = ∑FxFRy = ∑Fy
*
Take note of sign conventions
5.2 Forces5.2 Forces
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Coplanar Force Resultants -
Positive scalars = sense of direction
along the positive coordinate axes-
Negative scalars = sense of direction
along the negative coordinate axes-
Magnitude of FR
can be found by Pythagorean Theorem
RyRxR FFF 22
5.2 Forces5.2 Forces
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Coplanar Force Resultants -
Direction angle θ
(orientation of the force)
can be found by trigonometry
Rx
Ry
FF1tan
5.2 Forces5.2 Forces
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Example 5.1The link is subjected to two forces F1
and F2
. Determine the magnitude and orientation of the resultant force.
5.2 Forces5.2 Forces
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SolutionScalar Notation
N
NNF
FFN
NNF
FF
Ry
yRy
Rx
xRx
8.582
45cos40030sin600
:8.236
45sin40030cos600
:
5.2 Forces5.2 Forces
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SolutionResultant Force
From vector addition,Direction angle θ
is
N
NNFR
6298.5828.236 22
9.678.2368.582tan 1
NN
5.2 Forces5.2 Forces
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SolutionCartesian Vector NotationF1
= { 600cos30°i
+ 600sin30°j
} NF2
= { -400sin45°i
+ 400cos45°j
} N
Thus, FR
= F1
+ F2
= (600cos30°N -
400sin45°N)i
+ (600sin30°N + 400cos45°N)j
= {236.8i
+ 582.8j}N
5.2 Forces5.2 Forces
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Moment of a force about a point or axis provides a measure of the tendency of the force to cause a body to rotate about the point or axis.
Case 1Consider horizontal force Fx
, which acts perpendicular to the handle of the wrench and is located a distance dy from the point O
5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
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Fx
tends to turn the pipe about the z axis
The larger the force or the distance dy , the greater the turning effect
Torque
–
tendency of rotation caused by Fx
or simple moment (Mo
) z
5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
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Moment axis (z) is perpendicular to shaded plane (x-y)
Fx
and dy lies on the shaded plane (x-y)
Moment axis (z) intersects the plane at point O
5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
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Case 2Apply force Fz
to the wrench
Pipe does not rotate about z axis
Tendency to rotate about x axis
The pipe may not actually rotate Fz
creates tendency for rotation so moment (Mo
) x
is produced
5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
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Case 2
Moment axis (x) is perpendicular to shaded plane (y-z)
Fz
and dy lies on the shaded plane (y-z)
5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Case 3Apply force Fy
to the wrench
No moment is produced about point O
Lack of tendency to rotate as line of action passes through O
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
In General
Consider the force F
and the point O which lies in the
shaded plane
The moment MO
about point O, or about an axis passingthrough O and perpendicularto the plane, is a vector quantity
Moment MO
has its specified magnitude and direction
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Magnitude
For magnitude of MO
,MO
= Fdwhere d = moment arm
or perpendicular
distance
from the axis at point O to its line of action of the force
Units for moment is N.m
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Direction
The direction of MO
is specified by using “right hand rule”
The thumb points along the moment axis to give the direction and sense of the moment vector
Moment vector is upwards and perpendicular to the shaded plane
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Direction
MO
is shown by a vector arrow with a curl to distinguish it from force vectorExample (Fig b)
MO
is represented by the counterclockwise curl, which indicates the action of F. The arrowhead of the curl shows the sense of rotation caused by F.
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Direction
Moment always acts about an axis perpendicular to the plane containing F and d
Moment axis intersects the plane at point O
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Resultant Moment of a System of Coplanar Forces
Resultant moment, MRo = addition of the moments of all the forces algebraically since all moment forces are collinear
MRo = ∑Fdtaking counterclockwise to be positive
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Resultant Moment of a System of Coplanar Forces
A counterclockwise curl is written along the equation to indicate that a positive moment if directed along the + z axis and negative along the – z axis
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Example 5.2For each case, determine the moment of the force about point O
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Solution
Line of action is extended as a dashed line to establish moment arm d
Tendency to rotate is indicated and the orbit is shown as a colored curl
)(.5.37)75.0)(50()()(.200)2)(100()(
CWmNmNMbCWmNmNMa
o
o
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Solution
)(.4.42)45sin1)(60()(
)(.229)30cos24)(40()(
CCWmNmNMd
CWmNmmNMc
o
o
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
Example 5.3Determine the moments of the 800N force acting on the frame about points A, B, C and D.
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5.3 Moment of a Force – Scalar Formulation
5.3 Moment of a Force – Scalar Formulation
SolutionScalar Analysis
Line of action of F passes through C)(.400)5.0)(800(
.0)0)(800()(.1200)5.1)(800()(.2000)5.2)(800(
CCWmNmNM
mkNmNMCWmNmNMCWmNmNM
D
C
B
A
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Moment of force F about point O can be expressed using cross product
MO = r X Fwhere r represents position vector from O to any pointlying on the line of action of F
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Magnitude
For magnitude of cross product,
MO = r F sinθwhere θ
is the angle measured between
tails of r and F
Treat r as a sliding vector. Since d =r sinθ, MO = r F sinθ
= F (r sinθ) = Fd
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Direction
Direction and sense of MO are determined by right-hand rule - Extend r to the dashed position - Curl fingers from r towards F- Direction of MO is the same as the direction of the thumb
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Direction*Note:
- “curl” of the fingers indicates the sense of rotation- Maintain proper order of rand F since cross product is not commutative
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Cartesian Vector Formulation
For force expressed in Cartesianform,
where rx , ry , rz represent the x, y, zcomponents of the position vectorand Fx , Fy , Fz represent that of the force vector
zyx
zyxO
FFFrrrkji
FXrM
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Cartesian Vector Formulation
With the determinant expended, MO = (ryFz – rzFy )i – (rxFz - rzFx )j + (rxFy – yFx )k
MO is always perpendicular to the plane containing r and F
Computation of moment by cross product is better than scalar for 3D problems
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5.3 Moment of a Force - Vector Formulation
5.3 Moment of a Force - Vector Formulation
Cartesian Vector Formulation
Resultant moment of forces about point O can be determined by vector addition
MRo = ∑(r x F)
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
FBD is the best method to represent all the known and unknown forces in a system.
FBD is a sketch of the outlined shape of the body, which represents it being isolated or free from its surroundings.
Necessary to show all the forces and couple moments that the surroundings exert on the body so that these effects can be accounted for when equations of equilibrium are applied.
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Support ReactionsEx: Pin
The pin passes through a hold in the beam and two leaves that are fixed to the ground
Prevents translation of the beam in any direction Φ
The pin exerts a force F on the beam in this direction
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Weight and Center of Gravity
When a body is subjected to gravity, each particle has a specified weight
For entire body, consider gravitational forces as a system of parallel forces acting on all particles within the boundary
The system can be represented by a single resultant force, known as weight W of the body
Location of the force application is known as the center of gravity
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Weight and Center of Gravity
Center of gravity occurs at the geometric center or centroid for uniform body of homogenous material
For non-homogenous bodies and usual shapes, the center of gravity will be given
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Idealized Models
When an engineer perform a force analysis of any object, he or she considers a corresponding analytical or idealized model that gives results that approximate as closely as possible the actual situation.
To do this, careful selection of supports, material behavior and object’s dimensions are needed for trusty results.
In complex cases may require developing several different models for analysis.
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Procedure for Drawing a FBD1. Draw Outlined Shape
Imagine body to be isolated or cut free from its constraints
Draw outline shape
2. Show All Forces and Couple Moments
Identify all external forces and couple moments that act on the body
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Procedure for Drawing a FBD
Usually due to - applied loadings- reactions occurring at the supports or at points of contact with other body- weight of the body
To account for all the effects, trace over the boundary, noting each force and couple moment acting on it
3. Identify Each Loading and Give Dimensions
Indicate dimensions for calculation of forces
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Procedure for Drawing a FBD
Known forces and couple moments should be properly labeled with their magnitudes and directions
Letters used to represent the magnitudes and direction angles of unknown forces and couple moments
Establish x, y and coordinate system to identify unknowns
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Example 5.4Draw the free-body diagram of the foot lever. The operator applies a vertical force to the pedal so that the spring is stretched 40mm and the force in the short link at B is 100N.
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Lever loosely bolted to frame at A
Rod at B pinned at its ends and acts as a short link
For idealized model of the lever,
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Free-Body Diagram
Pin support at A exerts components Ax and Ay on the lever, each force with a known line of action but unknown magnitude
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Link at B exerts a force 100N acting in the direction of the link
Spring exerts a horizontal force on the leverFs = ks = 5N/mm(40mm) = 200N
Operator’s shoe exert vertical force F on the pedal
Compute the moments using the dimensions on the FBD
Compute the sense by the equilibrium equations
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Example 5.5Draw the free-body diagram of the unloaded platform that is suspended off the edge of the oil rig. The platform has a mass of 200kg.
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Idealized model considered in 2D because by observation, loading and the dimensions are all symmetrical about a vertical plane passing through the center
Connection at A assumed to be a pin and the cable supports the platform at B
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Direction of the cable and average dimensions of the platform are listed and center of gravity has been determined
Free-Body Diagram
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
Platform’s weight = 200(9.81) = 1962N
Force components Ax and Ay along with the cable force T represent the reactions that both pins and cables exert on the platform
Half of the cables magnitudes is developed at A and half developed at B
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Example 5.6The free-body diagram of each object is drawn. Carefully study each solution and identify what each loading represents.
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
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5.4 Free-Body Diagrams5.4 Free-Body Diagrams
Solution
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Example 5.7Draw the free-body diagrams of each part of the smooth piston and link mechanism used to crush recycled cans.
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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Solution
Member AB is a two force member
FBD of the parts
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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Solution
Since the pins at B and D connect only two parts together, the forces are equal but opposite on the separate FBD of their connected members
Four components of the force act on the piston: Dx and Dy represent the effects of the pin and Nw is the resultant force of the floor and P is the resultant compressive force caused by can C
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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Example 5.8Draw the free-body diagrams of the bucket and the vertical boom of the back hoe. The bucket and its content has a weight W. Neglect the weight of the members.
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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Solution
Idealized model of the assembly
Members AB, BC, BE and HI are two force members
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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Solution
FBD of the bucket and boom
Pin C subjected to 2 forces, force of the link BC and force of the boom
Pin at B subjected to three forces, force by the hydraulic cylinder and the forces caused by the link
These forces are related by equation of force equilibrium
5.4 Free-Body Diagrams5.4 Free-Body Diagrams
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5.5 Static Equilibrium5.5 Static Equilibrium
Static Equilibrium – all links that are at rest or moving at constant velocity.
Conditions for an object to be in static equilibrium:
1. The resultant, of all external forces acting on the object is equivalent to zero and does not cause it to translate.
2. The moment due to any external force is cancelled by the moments of the other forces acting on the object and do not cause it to rotate about any point.
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5.5 Static Equilibrium5.5 Static Equilibrium
For equilibrium of an object in 2D, ∑Fx
= 0; ∑Fy
= 0; ∑MO
= 0
∑Fx
and ∑Fy
represent the algebraic sums of the x and y components of all the forces acting on the object.
∑MO
represents the algebraic sum of the couple moments and moments of the force components about an axis perpendicular to x-y
plane and
passing through arbitrary point O, which may lie on or off the object.
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Simplify some equilibrium problems by recognizing members that are subjected top only 2 or 3 forces
Two-Force Members
When a member is subject to no couple moments and forces are applied at only two points on a member, the member is called a two-force member
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Two-Force MembersExample
Forces at A and B are summed to obtain their respective resultants FAand FB
These two forces will maintain translational and force equilibrium provided FA is of equal magnitude and opposite direction to FB
Line of action of both forces is known and passes through A and B
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Two-Force Members
Hence, only the force magnitude must be determined or stated
Other examples of the two- force members held in equilibrium are shown in the figures to the right
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Three-Force Members
If a member is subjected to only three forces, it is necessary that the forces be either concurrent or parallel for the member to be in equilibrium
To show the concurrency requirement, consider a body with any two of the three forces acting on it, to have line of actions that intersect at point O
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Three-Force Members
To satisfy moment equilibrium about O, the third force must also pass through O, which then makes the force concurrent
If two of the three forces parallel, the point of currency O, is considered at “infinity”
Third force must parallel to the other two forces to insect at this “point”
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
Bucket link AB on the back hoe is a typical example of a two-force member since it is pin connected at its end provided its weight is neglected, no other force acts on this member
The hydraulic cylinder BC is pin connected at its ends, being a two-force member.
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5.6 Two- and Three-Force Members
5.6 Two- and Three-Force Members
The boom ABD is subjected to the weight of the suspended motor at D, the forces of the hydraulic cylinder at B, and the force of the pin at A. If the boom’s weight is neglected, it is a three-force member
The dump bed of the truck operates by extending the hydraulic cylinder AB. If the weight of AB is neglected, it is a two-force member since it is pin-connected at its end points
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5.7 Force Analysis5.7 Force Analysis
Example 5.9The link is pin-connected at a and rest a smooth support at B. Compute the horizontal and vertical components of reactions at pin A
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5.7 Force Analysis5.7 Force Analysis
SolutionFBD
Reaction NB is perpendicular to the link at B
Horizontal and vertical components of reaction are represented at A
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5.7 Force Analysis5.7 Force Analysis
SolutionEquations of Equilibrium
NAxNA
FNN
mNmNmNM
x
x
B
B
A
100030sin200
;0200
0)75.0()1(60.90;0
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5.7 Force Analysis5.7 Force Analysis
Solution
NA
NNA
F
y
y
y
233
030cos20060
;0
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Example 5.10Placement of concrete from the truck is accomplished using the chute. Determine the force that the hydraulic cylinder and the truck frame exert on the chute to hold it in position. The chute and the wet concrete contained along its length have a uniform weight of 560N/m.
5.7 Force Analysis5.7 Force Analysis
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5.7 Force Analysis5.7 Force Analysis
Solution
Idealized model of the chute
Assume chute is pin connected to the frame at A and the hydraulic cylinder BC acts as a short link
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5.7 Force Analysis5.7 Force Analysis
SolutionFBD
Since chute has a length of 4m, total supported weight is (560N/m)(4m) = 2240N, which is assumed to act at its midpoint, G
The hydraulic cylinder exerts a horizontal force FBC on the chute
Equations of Equilibrium
A direct solution of FBC is obtained by the summation about the pin at A
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5.7 Force Analysis5.7 Force Analysis
Solution
NAxNA
FNF
mN
mNmF
M
x
x
BC
BC
A
790007900
;07900
0)0625.0(30sin2240
)2(30cos2240)5.0(
;0
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5.7 Force Analysis5.7 Force Analysis
Solution
Checking,
0)0625.0(30sin2240)1(30cos2240
)30cos1(2240)5.0(7900
;0
2240
02240
;0
mNmN
mNmN
M
NA
NA
F
B
y
y
y
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5.7 Force Analysis5.7 Force Analysis
Example 5.11The uniform truck ramp has a weight of 1600N ( ≈
160kg ) and is pinned to the body
of the truck at each end and held in position by two side cables. Determine the tension in the cables.
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5.7 Force Analysis5.7 Force Analysis
Solution
Idealized model of the ramp
Center of gravity located at the midpoint since the ramp is approximately uniform
FBD of the Ramp
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5.7 Force Analysis5.7 Force Analysis
SolutionEquations of Equilibrium
By the principle of transmissibility, locate T at C
md
md
NTN
TmT
M A
0154.120sin
210sin
59850)30cos5.1(1600
)30cos2(20sin)30sin2(20cos
;0
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5.7 Force Analysis5.7 Force Analysis
SolutionSince there are two cables supporting the ramp,
T’ = T/2 = 2992.5N
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5.7 Force Analysis5.7 Force Analysis
Example 5.12The lever ABC is pin-supported at A and connected to a short link BD. If the weight of the members are negligible, determine the force of the pin on the lever at A.
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(99)
5.7 Force Analysis5.7 Force Analysis
Solution FBD
Short link BD is a two-force member, so the resultant forces at pins D and B must be equal, opposite and collinear
Magnitude of the force is unknown but line of action known as it passes through B and D
Lever ABC is a three-force member
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(100)
5.7 Force Analysis5.7 Force Analysis
Solution FBD
For moment equilibrium, three non-parallel forces acting on it must be concurrent at O
Force F on the lever at B is equal but opposite to the force F acting at B on the link
Distance CO must be 0.5m since lines of action of F and the 400N force are known
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(101)
5.7 Force Analysis5.7 Force Analysis
Solution Equations of
Equilibrium
Solving,
kNFkNF
FF
FNFF
F
A
A
y
A
x
32.107.1
045sin3.60sin
;0040045cos3.60cos
;0
3.604.07.0tan 1
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(102)
5.7 Force Analysis5.7 Force Analysis
Example 5.13The hand exerts a force of 35N on the grip of the spring compressor. Determine the force in the spring needed to maintain equilibrium of the mechanism.
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5.7 Force Analysis5.7 Force Analysis
Solution
FBD for parts DC and ABG
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SolutionLever ABG
Pin E
NFNFF
FFF
FFF
NFmmNmmFM
x
EFED
EFEAy
EA
EAB
140014060cos2;0
060sin60sin;0
1400)100(35)25(;0
5.7 Force Analysis5.7 Force Analysis
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SolutionArm DC
NFmmmmF
M
s
s
C
62.600)75(30cos140)150(
;0
5.7 Force Analysis5.7 Force Analysis
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5.8 Sliding Friction Force5.8 Sliding Friction Force
When friction force cannot be neglected in a machine analysis, an additional force, friction force, Ff , is observed.
Friction always acts to impede motion. So, a friction force acts on a sliding link (perpendicular to the normal force, N) and in a direction opposite to the motion.
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5.8 Sliding Friction Force5.8 Sliding Friction Force
For a stationary object, friction works to prevent motion until the maximum attainable friction has been reached.
This maximum value is a function of a coefficient of friction, .
The friction force value that acts on sliding components is calculated as
Ff = N