UNIVERSITY OF DAR ES SALAAM

COLLEGE OF ENGINEERING AND TECHNOLOGY

DEPARTMENT OF MECHANICAL AND INDUSTRIAL ENGINEERING

DESIGN PROJECT

STUDENT’S NAME: MARWA, BENSON SEBA

REGISTRATION NUMBER: 2022-04-06308
PROGRAMM: B.Sc. IN MECHANICAL ENGINEERING
TASK: DESIGN OF A WORKSHOP SLEWING SWIVEL PULLEY
MECHANISM
COURSE CODE: ME 309
COURSE: DESIGN PROJECT
NAME OF THE SUPERVISOR: DR. EZEKIEL NGESA
Table of Contents
ABSTRACT.......................................................................................................3
ACKNOWLEDGEMENT.....................................................................................4
LIST OF FIGURES.............................................................................................5
LIST OF TABLES...............................................................................................6
DESIGN BRIEF....................................................................................................7
INFORMATION COLLECTION PLAN.....................................................................7
PRODUCT DESIGN SPECIFICATION......................................................................8
CONCEPTUAL DESIGN........................................................................................9
Concept one......................................................................................................9
Working principle...........................................................................................9
Concept two......................................................................................................9
Working principle...........................................................................................9
Concept three..................................................................................................10
Working principle.........................................................................................10
Concept evaluation...........................................................................................10
Grading system.............................................................................................10
PRELIMINARY CALCULATIONS.........................................................................11
HAND DRAFT..................................................................................................12
DESIGN ANALYSIS...........................................................................................12
DESIGN CRITERIA.........................................................................................12
COMPONENTS DESIGN..................................................................................12
Wire rope design...........................................................................................12
Pulley design...............................................................................................13
Drum design................................................................................................14
Pawl and ratchet design..................................................................................17
Design of the drum lever.................................................................................21
Design of pulley rods.....................................................................................21
Design of thrust bearing..................................................................................22
Design of an I-beam......................................................................................23
Design of hook.............................................................................................24
 Design of drum shaft......................................................................................26
Design of bolted joints....................................................................................27
DESIGN DRAFT................................................................................................31
DETAIL DESIGN...............................................................................................31
DETAIL PART DRAWINGS..............................................................................31
ASSEMBLY DRAWING...................................................................................31
CONCLUSION..................................................................................................31
REFERENCES...................................................................................................31
 ABSTRACT
This is a design project exercise report of a workshop slewing swivel pulley mechanism which is
manually operated which required to lift object in workshop daily activities, The design is
required to satisfy workshop needs by both efficiency, safety and performance as well as
facilitating smooth operation.
 ACKNOWLEDGEMENT
Firstly, I would like to give my sincere gratitude to the Almighty God for my wellbeing and
guidance in tough times throughout the design exercise timelapse.
And may I take this opportunity to thank the lecture in charge in ME 309, Dr. Elias for the
giving necessary instructions, principles and knowledge required to perform the design exercise
i would also like to express my deepest thanks to Dr. Ezekiel Ngesa as my supervisor throughout
the design exercise, despite of being busy, he still took his time to guide me and keep me in the
correct path during the design period.
Lastly, I would like to thank my friends and family for their social and finacial support in the
design period.
LIST OF FIGURES
LIST OF TABLES
DESIGN BRIEF.
 The maximum load to be handled should be 5 kN .
 The load should be lifted and held in position mechanically through a system of ropes
and pulleys.
 The pulley holder is to be supported in the base support which is fixed into a slewing
support.
 The mechanism should be able to swivel the load/rotate about the vertical axis.
 The slewing support should be fixed on a concrete wall in the workshop.
 The pulley system together with the slewing support should form a complete unit that
will be mounted onto the wall.
 A thrust bearing should be provided to take up the downward thrust due to the load.
 A simple and cheap construction is required.

INFORMATION COLLECTION PLAN.

S/ SOURCE OF PLACE EXPECTED MEANS OF
N INFORMATION INFORMATION INFORMATION
COLLECTION
1 Users and buyers.  Freight Recommended  Note
forwarders designs taking.
 MMI Steel Market analysis
mills
 SIDO, Dar
es salaam
workshops
2 Experts.  Roco rescue  Material used  Interview.
Inc.  Safety  Reading.
 Quora requirements  Note
website  Recommended taking.
designs
3 Literature review.  Machine  Design  Reading.
design specifications.  Note
textbook.  Analysis taking.
 Research information.
papers by  Mechanical
Kumar R & mechanisms.
Singh R on  Material
slewing selections.
systems
2021.
 Theory of
machines
 and
mechanisms
by Ulcker
& Pennock.
4 Manufacturer and  National  Production  Note
supplier. cranes cost. taking.
services  Market
Ltd. analysis.
 Rock
exotica.
Nformation collection plan for the design

PRODUCT DESIGN SPECIFICATION.

a) PERFORMANCE.
 It should be able to handle a maximum load of 5 kN .
 The load must be able to rotate at 360 ° while avoiding tangling of the rope

b) SAFETY.
 It should have color markings indicating the maximum load that can be handled.
 Construction should avoid sharp edges by applying chamfers, fillets and rounded
corners.

c) ENVIRONMENT.
 It should be designed to operate to both dusty and high humidity environments to
be suitable in all kinds of workshops.
 It should be designed to operate at room temperature.

d) MATERIALS.
 Pulleys should be of wear resistant materials due to friction between rope and
pulley.
 The slewing support should be made of materials with high stiffness and high
yield strength to prevent bending due to heavy loads.

e) MAINTENANCE.
 Components joining and fixing should be of temporary methods using bolts, nuts
and screws to allow easy replacement
 It should be made affordable and locally available materials.
 f) ERGONOMICS.
 The units should contain ergonomic grips for manual operations.
 Operation height should be of average human height between 150 cm and 175 cm.

g) TARGET PRODUCT COST.

 A single unit should be affordable at a maximum price of 4,000,000 Tsh.

h) INSTALLATION.
 All components are to be joined into a single unit.
 A single unit is to be mounted on a concrete wall by temporary mounting
methods.

i) QUANTITY.
 Production volume required should be about 50 units per year.

CONCEPTUAL DESIGN.
Concept one.
Working principle.
It’s a simple pulley arrangement whereby all of the moving pulleys are moving towards the
anchor at the same speed as the load, it provides a Mechanical advantage , M . A=2 n ,where n is
the number of movable pulleys in a system, Effort is applied by pulling the rope manually from
the pulley system, the load is fixed in place by tying the rope to a fixed hook attached to the
mounting wall.

Concept two.
Working principle.
It’s a compound pulley arrangement whereby several simple pulley systems are stacked
together, it provides a Mechanical advantage , M . A=2 n ,where n is the number of movable
pulleys in a system, Effort is applied by turning the lever which rotates the drum where the rope
is placed, the load is fixed in place by a pawl and ratchet mechanism which stops drum from
turning due to the weight of the load by engaging and disengaging the pawl manually, the drum
and pawl and ratchet mechanisms are also fixed to the mounting wall.
Concept three.
Working principle.
It’s also a simple pulley mechanism with a mechanical advantage of 4 due to two movable
pulleys, additional mechanical advantage is provided by integrating it with a gear system
attached to the drum to increase the effort in the pulley system, Effort is applied by turning the
wheel which start turning the pinion in the gear system for increasing the effort, which rotates the
gear and drum where the rope is placed , the load is fixed in place by a pawl and ratchet
mechanism which stops drum from turning due to the weight of the load by engaging and
disengaging the pawl manually, the drum, gear system and pawl and ratchet mechanisms are also
fixed to the mounting wall.

Concept evaluation.
Below is the matrix for the best concept selection.

Selection criteria Concept 1 Concept 2 Concept 3

Product Relative Weight Grade Weight Grade Weight Grace Weight
design importance. score. score score score score score score
specifications.
Performance. 5 0.11 3 0.66 5 0.55 4 0.60
Safety. 7 0.16 3 0.48 4 0.64 4 0.64
Environment. 3 0.07 3 0.21 4 0.28 4 0.28
Materials. 4 0.09 3 0.27 4 0.36 3 0.27
Maintenance. 8 0.18 3 0.54 4 0.72 4 0.72
Ergonomics. 2 0.04 3 0.12 5 0.20 5 0.20
Target product 9 0.20 2 0.4 4 0.80 3 0.60
cost.
Installation. 6 0.13 3 0.39 4 0.52 3 0.39
Quantity. 1 0.02 2 0.04 4 0.08 3 0.06
Total 45 3.11 4.15 3.31
Concept selection matrix
Grading system.
1. Poor.
2. Satisfaction.
3. Good.
4. Very good.
5. Excellent.
According to the matrix, concept 2 has highest weight score hence it is the best choice of the
design.
 PRELIMINARY CALCULATIONS
Given;

Maximum load, P=5 kN

Safety factor, f . s=1.5

Maximum design Load , Pd =7.5 kN

Effort Load=250 N

Required; Mechanical advantage (M.A)

From;

Maximum design Load

Mechanical advantage , M . A=
Effort Load

7500 N
M . A=
250 N

M . A=28.57 ≈ 30

∴ The pulley system must supply at least a mechanical advantage of 30.

From the selected compound pulley system of a certain mechanical advantage

n
M . A C =2

Where ‘ n ’ is the number of movable pulleys

Thus;

5
M . A C =2

M . A C =32

Since, M . A C > M . A

Then the system is valid for use in the mechanism.

HAND DRAFT
A hand draft was prepared showing the working principle of the slewing swivel pulley
mechanism drawn roughly not according to scale, the hand draft is provided as attachment to the
design report.

DESIGN ANALYSIS
DESIGN CRITERIA.
Maximum Load , P=5 kN

Safety factor , S . F=1.5

Design Load , Pd =P × S . F =5 kN ×1.5=7.5 kN

Pd =7.5 kN

COMPONENTS DESIGN.
Wire rope design.
Classified as class 1 hoist mechanism for the rope design as it is manually operated.

Selecting a (6 X 7) Steel wire rope which is suitable for class 1 mechanisms

Wire rope cross section

Determination of diameter of wire rope.

Minimum wire factor of safety F . Sw =3.5 ( for class 1 )

From;

Minimum Breaking Load , MBL=Pd × F . S w

 MBL=7.5 kN × 3.5

MBL=26.25 kN

From the Databook (ISO 2408)

An 8 mm diameter 1570 MPa steel wire rope satisfies the mechanism

Pulley design.
Determination of the diameter of the pulley.
For class 1;
D
≥ 18
d

Where ‘D’ and ‘d’ are the pulley and rope diameters.
D ≥18 × d

But, d=8 mm
D ≥18 × 8 mm

D ≥144 mm

Pulley width, a (mm)

a=2.7 d

a=2.7 × 8 mm

a=21.6 mm

Pulley groove design.

 Pulley groove design

From the figure above,

Angle between slides of the pulley, ω (°) .

ω=30 ° ¿60 °

Taking, ω=45°( average)

Depth of the pulley groove, h (mm).

h=1.5 d

h=1.5 ×8 mm

h=12 mm

Radius of the groove in the pulley, r (mm).

r =0.55 d

r =0.55 ×8 mm

r =4.4 say 4.5 mm

Drum design.
Drum diameter determination
For class 1;
 D
≥ 18
d

Where ‘D’ and ‘d’ are the drum and rope diameters.
D ≥18 × d

But, d=8 mm
D ≥18 × 8 mm

D ≥144 mm

Take the length of the drum to be 300 mm.

Drum groove design.

Drum profile and groove design

From the figure above,

Depth of drum groove, h (mm);
h=0.375 d

h=0.375 ×8 mm

h=0.375 d

h=3 mm
Radius of groove in the drum, r (mm);
r =0.5375 d

r =0.5375 ×8 mm

r =4.3 mm say 4.5 mm

Pitch circle diameter of the rope drum, p (mm);

p=2.18r

p=2.18× 4.5 mm

p=9.81 mm say 10 mm

Thickness of the drum shell, t (mm);

t=0.02 D+10 mm

t=12.88 say 13 mm

Maximum drum diameter for one layer, Dm (mm)

Dm =D+ 2 h+ 2t

Dm =144 mm+(2× 3 mm)+(2 ×13 mm)

Dm =176 mm

Clearance between adjacent turns to be 1.5 mm for an 8 mm rope.

Fleet angle, θ=5° (for hoists)

 Fleet angle

Pawl and ratchet design.

Ratchet design.

Ratchet design

From the figure above,

D=outside diameter of ratchet (mm)

z=number ofteeth on ratchet

m=module of ratchet (mm)

b=width of pawl end face(mm)

Ψ =width¿ module ratio

P=tangential force
p=allowable pressure per unit length ( mmN )
σ b=allowable bending stress(MPa)

T =transmitted torque (N −mm)

Where;

b P
D=mz , Ψ = , b= , P=
m p
2T
D
and m=2
3 T
Z Ψ σb √
For independent ratchet type brakes, z=12
Ratchet material → Steel
Pawl material→ Steel

Hence, ψ=2 , f . s=3 ,Yield strength , σ yt =450 MPa

N
¿ , p=350 (for steel pawl∧steel ratchet )
mm
σ yt 450 MPa
Then, σ b= = =150 MPa
f .s 3
Taking, D=150 mm (Slightly larger thanthe drum diameter)

Then,
Module of the ratchet, m (mm)
D
m=
z
150
m=
12

m=12.5 mm say 14 ( Available standards)

Width of the pawl end face, b (mm)

b=ψm

b=2 ×14

b=28 mm
Tangential force, P (N)
P=bp
N
P=28 mm× 350
mm
P=9800 N

Transmitted torque, T (N-mm)

DP
T=
2
150 mm× 9800 N
T=
2
T =735000 N−mm

From,

m=2 3
√ T
Z Ψ σb

8T
σ b= 3
zΨ m
8 ×735000
σ b= 3
12× 2× 14
σ b=89.3 MPa

Since the calculated bending stress is less than the allowable 150 MPa then the design is valid.
Considering the figure below for the tooth profile selection for the ratchet.
 Ratchet tooth profile

From the Databook

Ratchet wheel Pawl

m z
t h a r h1 a1 r1
14 12 43.98 10.5 14 1.5 14 8 2

Pawl design.

Pawl design
Stresses due to eccentric load;
e 1=h=10.5 mm

M b=P e 1=9800 N ×10.5 mm=102900 N −mm

6 Mb P
σ= 2
+
bx bx
 σ yt 450 MPa
σ ≤ σ all and σ all= = =150 MPa
f .s 3
Assuming , x=15 mm
6 Mb P
σ= 2
+
bx bx

6 ×102900 9800
σ= + =121.33 MPa
28 ×15
2
28 × 15

σ < σ all

Thus, the design is valid.

Pawl-pin design.
Pawl-pin is treated as a cantilever beam subjected to bending.

d=2.71
√
3 P b
(
+a
2 σb 2 1 )
d=2.71
√
3 9800 28
2× 89.3 2
+8 ( )
d=28.85 mm say 30 mm

Design of the drum lever.

From,
EA
M . A Lever =
LA

Where,
M . A Lever =mechanical advantage of the lever

L A =Distance ¿ the fulcrum¿ drumattachment

E A =Distance ¿ fulcrum¿ the handle

Supposed the lever increases the effort from 150 N to 250 N

 250
Then, M . A Lever = =1.67
150

Assuming, E A =250 mm
EA 250 mm
LA= = =149.7 mm say 150 mm
L A M . A Lever 1.67

Handle is estimated to be 150 mm in length and rubberized for comfort.

Design of pulley rods.

Assuming length of the rod is 45 mm
Designing based from bending theory,
From,
16 M
σ b= 3
d π

d=
√(
3 16 M
σb π )
Each rod at each pulley experiences a 2n F load, Where F = 250 N, r = 22.5 mm

Then,

√( )
n
3 16 × 2 F ×r
d n=
σb π

d 0 =5.23 say 6 mm,

d 1=6.34 mm say 7 , d 2=7.9 mm say 8 mm , d3 =10.1 mm say 10.5 mm , d 4=12.67 mm say 13 mm , d 5=15.97 mm say 16

Design of thrust bearing.

Axial load; W A =7.5 kN + 100 N ( hook weight ) =7.6 kN

Radial load; W R=0 N

Based on application of the machine, the machine operates 250 days for 5 years with 4 working
hours a day
Then,
L H =5× 250 × 4=5000 hrs
Working hours, L H =5000 hours

Bearing life in revolutions, L=60 NLH

Possible maximum rotation speed by manual operation, N=30rpm

Thus,
L=60 × 30× 5000
6
L=9× 10 revolutions
From,
For ball bearings,

( )
1
L 3
C=W −6
10

W =Y .W A . K S

W =1× 7.6 kN ×1=7.6 kN

( )
6 1
9 × 10 3
C=7.6 −6
=15808.6 N
10

Dynamic load, C=15808.9 N

Standard available dynamic load, C=16600 N
From the data book, the selected bearing is of bearing number 305.

Design of an I-beam

I beam cantilever design

Taking the material for the beam to be

Yield strength , σ yt =450 MPa

Assuming one pulley has weight of 120 N

Then the total load, ( F )acting at 2.5 m of the cantilever beam is 7500 N + 5(120) N = 8100 N
L 3000 mm
Allowable deflecting for a wall mounted cantilever I-beam, δ all = = =15 mm
200 200

Mode of failure ⟶ Beam is under bending

From
My M
σ b= =
I Zy

Where, Z y =Sectional modulus

M
Zy≥
σb

σ y 450
σ b=σ all= = =150 MPa
f .s 3
And, Bending moment , M =8100 N × 2500 mm=20.25 kN−m
Then,
20250 N −m −4 3 3
Zy≥ =1.35 ×10 m =135 cm
N
150 × 106 2
m
Standard beam suitable sectional modulus based on hot rolled medium-wide I-beam DIN 1025 is
3
146 cm .

I beam cross section

From the data book and the figure above,

Dimension in mm Cross Mass Section

sectio properties
n about axis
 Y −Y
m
A kg I Zy
h b s t r 2 ( ) 4
(cm ) m (cm ) (cm¿¿ 3)¿

400 180 8.6 13.5 21 84.5 66.3 1320 146

Selected beam dimensions

Checking for maximum deflection, δ max (mm)

2
F .a
δ max = (3 L−a)
6 EI
2
8100 ×2.5
δ max = 9 −8
( (3 × 3 )−2.5)
6 × 200 ×10 ×1320 ×10
δ max =13.78 mm

As δ max ≤ δ all , then the design is valid.

Design of hook.
As it operates as a middle duty hoist, it is in A5-A6 crane group, of 0.764 tons
Standard available is 2 tons

Grade
Crane group
level
M - - - - A3 A4 A5 A6 A7 A8
P - - - A3 A4 A5 A6 A7 A8 -
S - - A3 A4 A5 A6 A7 A8 - -
T - A3 A4 A5 A6 A7 - - - -
V A3 A4 A5 A6 A7 - - - - -
Hook
type Crane/hoist capacity (metric tons)
no.
1.6 8 6.3 5 4 3.2 2.5 2 1.6 1.25 1
2.5 12.5 10 8 6.3 5 4 3.2 2.5 2 1.6
4 20 16 12.5 10 8 6.3 5 4 3.2 2.5
5 25 20 16 12.5 10 8 6.3 5 4 3.2
Hook type determination table
From the table above hook no 1.6 is selected.
 Hook profile

Hook a1 a2 a3 b1 b2 d1 e3 h1 h2 L
type
no.
1.6 56 45 64 45 38 36 118 56 48 224
2.5 63 50 72 53 45 42 132 67 58 253
4 71 56 80 63 53 48 148 80 67 285
5 80 63 90 71 60 53 165 90 75 318
Hook type dimensions
Considering the above diagram and the table, the hook’s dimensions are as follows,

Feature a1 a2 a3 b1 b2 d1 e3 h1 h2 L
Dimensio
56 45 64 45 38 36 118 56 48 224
n (mm)
Selected hook dimensions

Diameter of the swivel hook, α 1 (mm)

As the hook is fastened by a nut then its throat is treated as a bolt,

Size of the throat,

From,

√
Pd
α 1 c=
π
σ
4 all

√
7500
α 1 c= =6.91 mm
π
×200
4
From the data book the standard core diameter is 8.16 mm and the corresponding size of the bolt
is M 12

Therefore, α 1=12 mm

Design of drum shaft.

Drum diameter, D=144 mm

Rope tension, T r=250 N

Crank force, F c =150 mm

Crank radius, Lc =250 mm

Drum length Ld =300 mm

Torque from the crank, T

T =F c × Lc =150 N ×250 mm=37500 N−mm

Bending moment from rope tension, M

Ld
M =T r × =250 N ×150 mm=37500 N −mm
2

Diameter of the shaft,d s

Equivalent twisting moment, T e

T e =√ M 2 +T 2

T e =√ 37500 2+ 375002=53033 N−mm

From,

d s=
√
3 16 T e
τ max × π

√
d s= 3
16 ×53033
τ max × π
=16.6 mm
Using a standard shaft of diameter 20 mm.

Design of bolted joints.

Mounting design.

Mounting design

Maximum load=designload + total pulley weight+ beamweight

Maximum load , P=7500 N + ( 100 N × 6 ) + ( 66.3 ×3 × 9.81 )=10051.21 N

P 10051.21 N
Direct shear load on each bOlt , P s= = =2512. 8 N say 2513 N
n 4

Assuming l 1=450 mm∧l 2=50 mm∧e=3000 mm

Pe l1 10051.21× 3000 ×450
Maximum tensile load , Pt = = =33.1 kN
2 ( ( l1 ) +( l2 ) ) 2 ( ( 375 ) + ( 50 ) )
2 2 2 2

1 1
P t + ( Pt ) + 4 ( P s ) = [ 33.1+ √ ( 33.1 ) + 4 ( 2.513 ) ]
[ √ ]
2 2 2 2
Equivalent tensile load , Pte=
2 2
Pte =33.3 kN

Size of the bolt,

From,

√
Pte
d c=
π
σ
4 all
 √
33300
d c= =14.56 mm
π
× 200
4
From the data book the standard core diameter is 14.9 mm and the corresponding size of the bolt
is M 18
Taking thickness of the plates to be 15 mm.

Hinge bolt design.

Direct shear load on the bolt , Ps =10051.21 N

Assuming the distance of the bolt from the mounting plate is l=250 mm∧e=3000 mm
Pel 10051.21 ×3000 ×250
Secondary tensileload , Pt = = =60.31 kN
2 ( l2 ) 2 ( (250 )2 )

Maximum tensile load , P M =Pt + Ps=60.31+10.05=70.36 kN

P M =70.36 kN

Size of the bolt,

From,

√
PM
d c=
π
σ
4 all

√
70360
d c= =21.16 mm
π
× 200
4
From the data book the standard core diameter is 23.32 mm and the corresponding size of the
bolt is M 27

Beam bolted joint design.

Supposed the vertical and horizontal distance between bolts is 200 mm and e=2350 mm
 Beam bolted joint design

r 1=r 2=r 3=r 4= √1002 +1002=141.4 mm

Finding maximum shearing force

P 10051.21 N
Primary shearing load on each bolt , P s1= = =2512.8 N
n 4
Pe r 1
Secondary shearing load on each bolt , Ps 2=
( r 12+r 22 +r 32 +r 42 )
10051.21 ×2350 ×141.4
Ps 2= =41761.57 N
( 141.4 2+ 141.42 +141.4 2+141.4 2 )
As bolt 2 and 4 experience more force, then

Maximum shearing force on bolt 2∧4 , Pm =√ P s 12 + P s 22 +2 Ps 1 × Ps 2 ×cos 45 °

Pm= √ 2512.8 2+ 41761.572 + ( 2 ×2512.8 × 41761.57 ×cos 45 ° )

Pm=43574.63 N

Size of the bolt,

From,

√
Pm
d c=
π
σ
4 all
 √
43574.63
d c= =16.66 mm
π
×200
4
From the data book the standard core diameter is 16.933 mm and the corresponding size of the
bolt is M 20

Pulley system to beam joint design.

Single bolt design

8100 N
Maximum tensile load on each bolt , P b= =2025 N
4

Size of the bolt,

From,

√
Pb
d c=
π
σ
4 all

√
2025
d c= =3.6 mm
π
× 200
4
From the data book the standard core diameter is 4.019 mm and the corresponding size of the
bolt is M 5
DESIGN DRAFT
According to the analysis made and the hand draft drawn, aa design draft was drawn true to scale
for all parts, indicated with surface roughness and tolerances necessary.
The design draft is provided as attachment to the design report.

DETAIL DESIGN
DETAIL PART DRAWINGS
Detail drawings of all parts were prepared with reference to the design draft prepared, the drawn
detail drawings are provided as attachments to the design report.

ASSEMBLY DRAWING
An assembly drawing was prepared true to scale showing how parts are connected together, the
drawn assembly drawing is provided as attachment to the design report.

CONCLUSION
The design was based in considering structural optimization, good load handling, safety during
operation and high operational efficiency, it demonstrates the successful applications of
engineering principles and innovative design strategies to create a workshop slewing swivel
pulley system that is safe to use, powerful and dependable.

REFERENCES
1. KHURMI, R.S and GUPTA (2005). ‘A textbook of Machine Design’ (14th ed). Eurasia
publishing house.
2. ISO 4301-1:2016 Crane classification.
3. Bhandari, V.B (2014). ‘Machine Design Data Book’, McGraw Hill
4. Materego, M (2024). ‘Machine elements and design lecture notes’, University of Dar es
salaam. PowerPoint presentation.
5. Elias, E (2023). ‘Design methodology lecture notes’, University of Dar es salaam.
PowerPoint presentation