 Open Access
 Total Downloads : 1165
 Authors : Dr. Suwarna Torgal, Kamlesh Gurjar
 Paper ID : IJERTV1IS3140
 Volume & Issue : Volume 01, Issue 03 (May 2012)
 Published (First Online): 30052012
 ISSN (Online) : 22780181
 Publisher Name : IJERT
 License: This work is licensed under a Creative Commons Attribution 4.0 International License
Optimization of Dynamics Parameters and the Effect of Sway Angles in Hydraulic Crane Hook
Dr. SUWARNA TORGAL1, KAMLESH GURJAR2*
1Department of Mechanical Engineering IET, DAVV, IndoreIndia 2*Department of Mechanical Engineering IET, DAVV, Indore India
ABSTRACT: – The present scenario focuses on crane hook suffers by sway angle due to the pendulum motion of payload, to put hold on the sway angle, to increase the efficiency and user friendly approach. Here the paper presents the design of antisway controller brake system for hydraulic floor crane by studying the parameters like mass & length and by the use of mathematical models & equation like Lagranges equation to achieve the equation of motion was optimized then automatically or self actuating antisway controller system was designed. Synchronized algorithm for the practical correct and excellent use of hydraulic floor crane for loading and unloading the goods. The result of this mathematical model shows the effect of mass and length if changed then sway angle is optimized.
KEY WORD:Crane System, Lagranges Equation, Crane hook, Weigh Sensor, Payload, Sway Angle and Mathematical Model.
INTRODUCTION:
Firstly in todays world the use of floor crane is going wide sprayed and this use is directly related with two parameters firstly the efficiency Secondly user friendly approach. The floor cranes use are many like domestic, industrial Construction site etc. While going through all this we observe major lacuna in the hook of the crane. This lacuna is the sway angle. We call this sway angle as lacuna because while lifting, transportation & placing the load, then hook of hydraulic floor crane play the major role that will put direct impact on the above said parameter i.e. user friendly approach and efficiency.
This sway in the hook of the crane will slow down the working of the crane & decrease the efficiency on the other hand the driver has to keep acute vision during the motion of the crane. To put all this problem on hold this antissway controller system for the hook of the crane is designed by learning the optimization of dynamic parameters of crane hook and the effect of sway angle in hydraulic floor crane. Recently designed cranes are larger and have higher lifting capacities and travel speeds. To achieve high productivit y and to comply with the safety requirements, these cranes require effective controllers such as anti swing controls. Inertia forces due to the mot ion of the crane can induce significant payload oscillations. If the oscillations of the payload can be constrained using an appropriate method, there will be a number of benefits such as having greater yield and safety margin, enabling higher operating speed, enhancing work quality and creating greater throughput for a given insta lled capacity. Besides, most actual systems are influenced by noise and external disturbances inc luding crane.
PROBLEM BACKGROUND: Among the several of types of cranes, hydraulic cranes are the mainly used.They are used for loading, unloading and transporting the load. One of the most essential problems in the cranes is wavering of the payload which is produced by various factors arising mostly from the crane maneuvers and motions of the cranes components forperforming the desired operations. Payload influence slows down the movement and transmission of the payload process because extra time is required to let the pendulum motion come to a stop.
HYDRAULIC FLOOR CRANE:
Figure (1) Computer Model for Hydraulic Floor Crane
METHODOLOGY:
SYTEM MODELLING FOR HYDRAULIC CRANE:
Figure 1 shows the schematic system of a crane. It is consist of two boom (Main boom and Auxiliary boom) two hydra ulic cylinder. The mathematical model for this hydraulic crane are shown figure 2. With their hook rotation and payload rotation various direction. Before analyzing the dynamic mot ion of hook parameter of the crane into a mathematical mode l, a number of assumpt ions are introduced, so that the crane mode l can be simplified.
Assumptions for Mathematical Model

The payload and crane hook (only) are supposed to have simultaneous motion in determining the equation of motion.

A hydraulic floor crane with two booms and two
hydraulic cylinders is considere d to create a
payload is considered for deriving the equation of motion.

The entire motion of hook and payload considered as general plane motion due to crane movement.

The mass of hook is considered as point mass and length of payload (Lp) considered weightless.

(Lp) has displacement in X, Y and Z direction but hook length (Lh) displace in X and Z direction only.

Neglect the effect of air resistance on the movement of hook and payload.
Figure (2) Mathematical Model for Hydraulic Floor Crane
FORMULATION FOR DYNAMIC PARAMETERS AND SWAY ANGLE:
Firstly we are derived the equation of motion for the payload and crane hook by using Lagrangian equation. It is a scalar procedure which is starting from the scalar quantities of kinetic energy, potential energy and express in generalized coordinates. It is given as:
d L L F
dt q q i
mathematical model.
3) In this model the effect of crane motion in straight rotation of hook steering and movement of
i i
Where, L = T U
T = Total Kinetic Energy, U = Total Potential Energy Fi = Non potential Forces,
[1]qi = Generalized Coordinates
q = Velocity Coordinates
So
1 m [L
cos
. .
L cos 2
.
cos ]2
. .
[ L sin.
L sin ]2
i 2 p p 2 1 h 1
T
1 x] [Lp 3 3
p 2 2
Lh 1 sin 1 p 3 3
So,
d T T U
1 . 1
. 2 1 1 .
1 . 1 . 2
.
dt qi
qi qi
Qi
[2]2 I p 2
2 I p 3
2 mh
[2 Lh1 cos ]2
[ 2 Lh1 sin ]2
2 Ih
1 …………[11]
1
1
Here,
q1 1, q2 2 , q3 3 , q4 x
EQUATION OF MOTION FOR PAYLOAD
Total Potential Energy (P.E.) is
AND HOOK:Displacement of payload in X, Y and Z direction
U u p uh
[12]x L sin
L sin x
Where, P.E. for payload
p p 2
Yp Lp sin
h 1
3 [4] [3]
up mp g[Lp cos 3 Lp cos 2
P.E. for hook
Lh Lh
cos 1]
Z p Lp cos 2
Lh cos 1
Lp cos 3
[5]uh mh g[Lh
So
Lh cos 1 ]
Displacement of hook in X and Z direction
U mp g[Lp cos 3
Lp cos 2 Lh
Lh cos 1]
mhg[Lh
Lh cos
1]..[13]
X h Lh sin 1
x [6]
Putting the value of derivative of K.E. and P.E. from
equation [11] and [13] in Lagranges equation. So linear equation in term of angular acceleration (as
Zh Lh cos
1 [7]
variable) of hook and payload are given blow:
So the resultant velocity vector for payload and hook is given as
Let
A Sin , A Sin , A Sin
1 1 2 2 3 3
V 2 x 2 y 2 z 2
B1 Cos 1, B2 Cos 2 , B3
Cos 3
p p p p
[8]C1 Sin2 1, C2 Sin2 2
V 2 x 2
y 2
z 2 [9]
d T T U
dt
h h h h 0
Total kinetic energy (K.E.) is
.
3 3 3
T Tp Th
[10][L B L2 A2
I ] m [L2 A A ]
m L L A A
x[0] V
Where, K.E. for payload
3 p 3 p 3 p
2 p p 2 3 1
p h p 1 3 3
[14]
1 
m v21 I 
1 
2 
2 
p p 2 p 
2 2 p 
3 [10.a] 
T 2 I
Where,
V m [C L2
L A ]
2m L2 A B
2L L m A A m gL A
p 3 p 3 3
p p 3 2
p p 3 2 1
h p p 1 3
p p 3
And K.E. for hook
Similarly,
dt
d T T U 0
Th T2
1 2 1 2
m v
I
h h h 1
.
2 2 2
2 2 [10.b] [m L2 A A ] [m L2 B2 m L2 A2 I ] [m L L ][B B A A ]
x[m L B ] V
3
p p 2 3 2
p p 2
p p 2
p
1
p p h
1 2 1 2
p p
2 2
[15]
Where
V 2 A B m
[m L L B A m L L A B ]
B m
m (B A L2 A B )
length of the hook. Now the matrices are form for the
2 3 2 3 p
1 p p h 1 2
p p h 1 2 1 2 1 p
3 2 r 2 3
p 3 2
2
p p 2 2
p p 2 2 2 p p 1 1 p h p 1
p p 1
x m L A m L2 A B L2 m B2 L L m B2 xL m B
Similarly
0
d T T U
dt
.
1 1 1
mass and length of the hook at the angle of rotation of crane and boom of 300 by using the specification of crane. This equation represents the value of angular acceleration related to sway angles ( 1 , 2 and 3 ).
[m L L A A ]
[ A A B B ]m L L
L [m A2
mh B2
mh A2 I ]
Mass Matrices for angular acceleration at
300
3 p h p
1 3 2 1 2 1 2
p p h
1 h p 1 4 1 4 1 h
xmp Lh ( A1 B1 )
Here
V 2 ( A B m )
V1…………………………………………………………………[16]
126.84 
507.3 
231.35 0.1125m 
1260 
848.04 107 m 

0 
976.44 
461.25 
mh 
x 
1025 
2m [L2 A B L L (B A )A B ] 2m L2 L xm L A
620 0.130 0.0618 0
0.0756 620.30 0.2475 0.476
3
2 =
2.877
0.789
1 3 1 3 p
2 p p 1 1
p h 1 2 1 2 1
p h 1
p h 1
1 2
p p h
2 1 2 1 1 3 h p 1 3
M L L (2A B B A )
L L B A (m m )
x m L (B A )
x m L A
h 1 h
h p
1
p h
1 1 2
p p 1
d T T U
[18]F
dt x x x
Length Matrices for angular acceleration at
300
[0]3Where
2[mp Lp B2 ]
1[mp Lh A1 ]
x[mp
m1 ]
Vx [17]
620.55 0.130 0.1375Lh
h h h h
0.0756 620.30 0.55Lh
0
0.476
3
2
2.815 0.1375Lh
0.604 0.185Lh
1
1775.3L 2
102 3726L
V m L L A
2m L A
281.87L
1127.5L
518.12L
2800L h
x 2 p p p 2 1
p h 1
0 976.44 1025Lh
8 x
h
563.75 0.275Lh
Non potential force Fx
(mcr
mp )x
RESULTS AND DISCUSSION:
SPECIFICATION: – Assumed parameters for
The mass and length matrices show the relation
hydraulic floor crane
between angular acceleration (sway angle
1 , 2 and 3
Table 1:
) mass and length of the hook. These matrices were solved by using the MATLAB software for different value of mass and length of hook and angle of rotation of boom and crane. The results were shown by drawing the graphs between the angular acceleration and mass and length of the hook at different angle of rotation of crane and boom like 300, 450 and 600. By
20 40 60 80 100 120 140
100000
80000
60000
40000
20000
0
20000 0
40000
60000
Angular Acceleration(1)
(rad/sec2)
Length (In meters) 
Mass (In Kilograms) 
Moment of Inertia (I)=(mass*lengtp) (In Kg. (meters)2 ) 

Payload 
0.55 
2050 
620 
Crane hook 
0.45 
8 
1.62 
increasing the mass of the hook then
1
began to
30 degree
FORMATION OF MATRICES:
Mass of the hook (Kg)
The equations of motion are constructed by using Lagranges equation for angular acceleration (
1 , 2 and 3 ), which gives the relation between the
mass of and length of the hook which given by equation [15], [16] and [17]. There are four variable so the matrices of 4X4 were constructed for the mass and
increases but at 15 kg to 18kg it is decreasing shown in graph (3).
0
0 20 40 60 80100120140160
50
100 30 degree
150
Length of the hook (metres)
Angular Acceleration(1) (rad/ec^2)
Anguar Acceleration(1) (rad/sec^2)
200
0
200
400
0 50 100 150
Mass of the hook (Kg)
60 degree
Figure (3) Effect of mass of hook on
0.08
0.06
0.04
0.02
0
Angular
Acceleration(2)
(rad/sec^2)
1
Angular Acceleration(1)
(rad/sec^2)
500
400
300
200
100
0
100
0 50 100 150
Mass of the hook (Kg)
200
0 10 20 30 40 50 60 70 80 90 100110120130
Length of the hook (metres)
30 degree
60 degree
30
25
20
15
10
5
0
Angular Acceleration(2)
(rad/sec^2)
Figure (3) Effect of Length of hook on
1
60 degree
0 20 40 60 80 100 120
80
60
40
20
0
30 degree
Mass of the hook (Kg)
0 10 20 30 40 50 60 70 80 90100110120
Length of the hook (metres)
Figure (4) Effect of mass of hook on
2
Angular Acceleration(3) (rad/sec^2)
Angular Acceleration(2)
(rad/sec^2)
4
2
0
2 0 20 40 60 80 100 120 140
4
6
8
Mass of the hook (Kg)
20 40 60 80 100 120 140
60 degree
600
400
200
0
200 0
400
600
Angular Acceleration(2) (rad/sec^2)
30 degree
Length of the hook (metres)
0.1
0.08
0.06
0.04
0.02
0
Angular Acceleration(3)
(rad/sec^2)
Angular Acc. (3)
rad/sec^2
Figure (3) Effect of Length of hook on
2
0 50 100 150
Mass of the hook (Kg)
60 degree
10
5
0
30 degree
0 0.5 1 1.5
Length of hook (metres)
Figure (4) Effect of mass of hook on
3
Length of the hook (metres)
0.1
0.15
20
0.05 0
0.05
0
Angular Acceleration(3) (rad/sec^2)
Figure (3) Effect of Length of hook on 3
CONCLUSION:
In this paper the concept shows that the hook of the crane experiences pendulum motion when payload is attached. This motion is optimized by changing the hook parameters like mass and length of hook by framing the equation of motion for the hook and payload of crane using Lagranges equation for controlling the sway angle of hook and payload. A hydraulic floor crane with 4 degree of freedom to increase the efficiency of floor crane, Straight motion of the crane and rotation of hook and payload was considered, such condition gives the complicated non linear equations. This equation was convertd into mass metrics and length metrics and was solved in MATLAB software accordingly. The assumed mathematical model is used for hydraulic floor crane with two booms and two hydraulic cylinders. The result obtained as shown in attached chart and graph, which shows that while increasing the mass and length of hook, would reduce and optimize the pendulum motion and sway angle of the hook and payload.
NOMENCLATURE:
Xp , YP and ZP = Displacement of Payload in X,Y and Z direction.
Xh , Yh and Zh = Displacement of Payload in X,Y and Z direction
1 = Angle of rotation of hook in a vertical plain in X direction.
2 = Angle of payload rotation in vertical plain in X direction.
3 = Angle of rotation of hook in an in X direction.
Lp, Lh, mp and mh = Length and mass of payload and hook of a crane
Ip and Ih = Mass moment of inertia for payload and hook
40 60 80 100 120 6
T and U = Total Kinetic and Potential Energy
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