dynamic-force-analysis-of-mechanisms ppt.pdf

Prepared by:
Asst.Prof.Chirag Mevada
(Mechanical Department,ACET)
Dynamic force analysis of
mechanisms
Subject:- DOM
Code:- 3151911

 Introduction
 Dynamic forces are associated with accelerating masses.
 As all machines have some accelerating parts, dynamic forces are always present when the machines
operate.
 In situations where dynamic forces are dominant or comparable with magnitudes of external forces and
operating speeds are high, dynamic analysis has to be carried out.
 For example, in case of rotors which rotate at speeds more than 80,000 rpm, even the slightest
eccentricity of the centre of mass from the axis of rotation produces very high dynamic forces.
 This may lead to vibrations, wear, noise or even machine failure.
•S.S. Ratan, Theory of Machines, 3rd

 D' ALEMBERT'S PRINCIPLE
 D' Alembert's principle states that the inertia forces and couples, and the external forces and torques on a
body together give statical equilibrium.
 Inertia is a property of matter by virtue of which a body resists any change in velocity.
 The negative sign indicates that the force acts in the opposite direction to that of the acceleration. The
force acts through the centre of mass of the body.
 Similarly, an inertia couple resists any change in the angular velocity.

 D' ALEMBERT'S PRINCIPLE
 According to D' Alembert's principle, the vector sum of forces and torques (or couples) has to be zero,
i.e.,
 and
 This suggests that first the magnitudes and the directions of inertia forces and couples can be determined,
after which they can be treated just like static loads on the mechanism. Thus, a dynamic analysis problem
is reduced to one requiring static analysis.

 EQUIVALENT OFFSET INERTIA FORCE
 In plane motions involving accelerations, the inertia force acts on a body through its centre of mass.
 However, if the body is acted upon by forces such that their resultant does not pass through the centre of
mass, a couple also acts on the body.
 In graphical solutions, it is possible to replace inertia force and inertia couple by an equivalent offset
inertia force which can account for both. This is done by displacing the line of action of the inertia force
from the centre of mass.
 The perpendicular displacement h of the force from the centre of mass is such that the torque so produced
is equal to the inertia couple acting on the body,

 DYNAMIC ANALYSIS OF FOUR-LINK MECHANISMS

 Example:-
The dimensions of a four-link mechanism are AB = 500 mm, BC = 660 mm, CD= 560 mm
and AD= 1000 mm. The link AB has an angular velocity of 10. 5 rad/s counter-clockwise and an angular
retardation of 26 rad/s2 at the instant when it makes an angle of 60° with AD, the fixed link. The mass of the
links BC and CD is 4.2 kg/ m length. The link AB has a mass of 3.54 kg, the centre of which lies at 200 mm
from A and a moment of inertia of 88,500 kg.mm2. Neglecting gravity and friction effects, determine the
instantaneous value of the drive torque required to be applied on AB to overcome the inertia forces.
Solution:- The required input torque 23.5 N.m (counterclockwise)
Configuration Diagram Velocity Diagram Acceleration Diagram

 DYNAMIC ANALYSIS OF SLIDER-CRANK MECHANISMS
 The steps outlined for dynamic analysis of a four-link mechanism also hold good for a slider-crank
mechanism and the analysis can be carried out in exactly the same manner.
 However, an analytical approach is also being described in detail in the following sections.
 VELOCITY AND ACCELERATION OF A PISTON
 Figure shows a slidercrank mechanism in which the crank OA rotates in the clockwise direction. l and r
are the lengths of the connecting rod and the crank respectively.
 Let x = displacement of piston from inner-dead centre
 At the moment when the crank has turned through angle θ from the inner-dead centre,

 VELOCITY AND ACCELERATION OF A PISTON

 VELOCITY OF PISTON

 ACCELERATION OF PISTON

 ANGULAR VELOCITY AND ANGULAR ACCELERATION OF CONNECTING ROD

 ENGINE FORCE ANALYSIS
 An engine is acted upon by various forces such as weight of reciprocating masses and connecting rod, gas
forces, forces due to friction and inertia forces due to acceleration and retardation of engine elements, the
last being dynamic in nature.
 In this section, the analysis is made of the forces neglecting the effect of the weight and the inertia effect
of the connecting rod.
(i) Piston Effort (Effective Driving Force)
 The piston effort is termed as the net or effective force applied on the piston.
 In reciprocating engines, the reciprocating masses accelerate during the first half of the stroke and the
inertia force tends to resist the same.
 Thus, the net force on the piston is decreased.
 During the later half of the stroke, the reciprocating masses decelerate and the inertia force opposes this
deceleration or acts in the direction of the applied gas pressure and thus, increases the effective force on
the piston.
 In a vertical engine, the weight of the reciprocating masses assists the piston during the outstroke (down
stroke), thus, increasing the piston effort by an amount equal to the weight of the piston.
 During the instroke (upstroke), the piston effort is decreased by the same amount.

(i) Piston Effort (Effective Driving Force)

(ii) Force (thrust) along the Connecting Rod
(iii) Thrust on the Sides of Cylinder

(iv) Crank Effort
(v) Thrust on the Bearings

 TURNING MOMENT ON CRANKSHAFT

 DYNAMICALLY EQUIVALENT SYSTEM
 In the previous section, the expression for the turning moment of the crankshaft has been obtained for the
net force F on the piston.
 This force F may be the gas force with or without the consideration of inertia force acting on the piston.
 As the mass of the connecting rod is also significant, the inertia due to the same should also be taken into
account.
 As neither the mass of the connecting rod is uniformly distributed nor the motion is linear, its inertia
cannot be found as such.
 Usually, the inertia of the connecting rod is taken into account by considering a dynamically-equivalent
system.
 A dynamically equivalent system means that the rigid link is replaced by a link with two point masses in
such a way that it has the same motion as the rigid link when subjected to the same force, i.e., the centre
of mass of the equivalent link has the same linear acceleration and the link has the same angular
acceleration.

 Figure(a) shows a rigid body of mass m with the
centre of mass at G. Let it be acted upon by a force F
which produces linear acceleration f of the centre of
mass as well as the angular acceleration of the body
as the force F does not pass through G.
 Now to have the dynamically equivalent system, let the replaced massless link [Fig. (b)] has two point
masses m1 (at B and m2 at D) at distances b and d respectively from the centre of mass G as shown in
Fig. (b).

1. To satisfy the first condition, as the force F is to be same, the sum of the equivalent masses m1 and m2
has to be equal to m to have the same acceleration. Thus,
m = m1 + m2
2. To satisfy the second condition, the numerator F*e and the denominator I must remain the same. F is
already taken same, Thus, e has to be same which means that the perpendicular distance of F from G
should remain same or the combined centre of mass of the equivalent system remains at G. This is
possible if
m1b = m2d
 To have the same moment of inertia of the equivalent system about perpendicular axis through their
combined centre of mass G, we must have
I= m1b2 + m2d2
 Thus, any distributed mass can be replaced by two point masses to have the same dynamical properties if
the following conditions are fulfilled:
(i) The sum of the two masses is equal to the total mass.
(ii) The combined centre of mass coincides with that of the rod.
(iii) The moment of inertia of two point masses about the perpendicular axis through their combined
centre of mass is equal to that of the rod.

 INERTIA OF THE CONNECTING ROD
 Let the connecting rod be replaced by an equivalent massless link with two point masses as shown in Fig.
 Let m be the total mass of the connecting rod and one of the masses be located at the small end B.
 Let the second mass be placed at D and

 Let k = radius of gyration of the
connecting rod about an axis
through the centre of mass G
perpendicular to the plane of
motion.
 Then
 or
 This result can be compared
with that of an equivalent length
of a simple pendulum in the
following manner:
 The equivalent length of a
simple pendulum is given by
 where b is the distance of the
point of suspension from the
centre of mass of the body and k
is the radius of gyration.
 Thus, in the present case, d + b
(= L) is the equivalent length if
the rod is suspended from the
point B, and D is the centre of
oscillation or percussion.
 However, in the analysis of the
connecting rod, it is much more
convenient if the two point
masses are considered to be
located at the centre of the two
end bearings, i.e., at A and B.

 INERTIA FORCE IN RECIPROCATING ENGINES (GRAPHICAL METHOD)

dynamic-force-analysis-of-mechanisms ppt.pdf

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