This document describes the design of a vertical screw conveyor. It includes the selection of a JHS400 screw to transport cement vertically over 3.15 meters. A 1.4552 kW motor operating at 1425 rpm is chosen to power the conveyor. Three A-section V-belts running over pulleys with diameters of 125mm and 250mm are selected to transmit power from the motor to the screw. Gears and chains are also included in the drive mechanism with specified transmission ratios. The shaft, keys, bearings and clutch are designed. Material selections are made for the pulleys, V-belts and other components. Dimensions and specifications are provided for each designed part.
Design of material handling system belt conveyor system for crushed coal for ...Aditya Deshpande
This was a project under subject in graduation in Mechanical Engineering -DOMS- Material Handling System
Conveyor belts have been used for decades to transport bulk and unit loads. They have proved their worth everywhere because belt conveyor installations can be adapted to meet nearly all local conditions.
This project demonstrates how to design such Conveyor Belt for Coal Crushing in Thermal Power Plant application with mathematical and imperial ways
introduction, types of scissor lift, advantages and disadvantages design of different components and calculation based of selected material. generated 3d model in solidworks.
Design of material handling system belt conveyor system for crushed coal for ...Aditya Deshpande
This was a project under subject in graduation in Mechanical Engineering -DOMS- Material Handling System
Conveyor belts have been used for decades to transport bulk and unit loads. They have proved their worth everywhere because belt conveyor installations can be adapted to meet nearly all local conditions.
This project demonstrates how to design such Conveyor Belt for Coal Crushing in Thermal Power Plant application with mathematical and imperial ways
introduction, types of scissor lift, advantages and disadvantages design of different components and calculation based of selected material. generated 3d model in solidworks.
Design of Belt Drives With Pulley Theory By Prof. Sagar A. DhotareSagar Dhotare
It covers following points :-
Introduction flat and V Belt
Types of Belts
Calculations for Tensions
Maximum Torque Transmitted
pulley design
Advantage and disadvantages of V belt over flat belt
This document is about power transmission system. It's aimed those interested in learning about mechanical engineering and students who are studying various programmes in engineering. This document only deals with power transmission through flat and v-belts.
DESIGN OF CANE CARRIER ROLLER CONVEYOR CHAIN OF 150MM PITCH AND TESTING UNDER...ijiert bestjournal
Chain is the most important element of the industri al processes required for transmitting power and conveying of materials. Roller conveyor chain p erforms efficient and economical in wide range of applications in manufacturing and agricult ural industries. Chains are machine elements that are subjected to extreme service conditions,s uch as high tensile loads,compressive loads,friction,and sometimes aggressive operating enviro nment. The present work focuses on the design calculations of cane carrier roller conveyor chain for calculating breaking load . Finally,experimentation is carried out on Computerized Univ ersal testing Machine (UTM).
This paper describes the analysis of belt bucket elevator used in Myanmar C.P Livestock Co.Ltd Taunggyi feed mill . Material handling process is essential for the production. Bucket elevator has evolved as advanced material handling equipment in mechanized bulk material handling industry. The effective use of different types of bucket elevators completely depends on its design and types of bulk material. Yellow corn raw materials are transported by bucket elevator. In this journal, the use of conveyor systems and the design of bucket elevator with simultaneous buckets for lifting yellow corn at 28.8 m height are presented. And it is 70 tons per hour. The main aim is to share about conveyor systems and to know the calculation of belt design, shaft and pulley. Mg Than Zaw Oo | Ma Myat Win Khaing | Ma Yi Yi Khin "Analysis of Belt Bucket Elevator" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-3 | Issue-5 , August 2019, URL: https://www.ijtsrd.com/papers/ijtsrd26483.pdfPaper URL: https://www.ijtsrd.com/engineering/mechanical-engineering/26483/analysis-of-belt-bucket-elevator/mg-than-zaw-oo
hello folks;
In this documentation, A 2 stage bevel reduction gearbox is designed.
The example taken is of the gearbox requirement for the Box-shipping conveyor. All the necessary design calculations for gears and shafts are carried out in a proper and easy-to-understand sequence. The material selection, standardized components (keys, oil seals likewise)selection from the design databook is also discussed with reasoning. As and when needed concepts are explained with the help of suitable graphs, visuals, and drawings.
This report is authorized by the team member's name mentioned on Slide.
Thank you!!
If you find it helpful do like&l share it with your engineering friends
Design of Belt Drives With Pulley Theory By Prof. Sagar A. DhotareSagar Dhotare
It covers following points :-
Introduction flat and V Belt
Types of Belts
Calculations for Tensions
Maximum Torque Transmitted
pulley design
Advantage and disadvantages of V belt over flat belt
This document is about power transmission system. It's aimed those interested in learning about mechanical engineering and students who are studying various programmes in engineering. This document only deals with power transmission through flat and v-belts.
DESIGN OF CANE CARRIER ROLLER CONVEYOR CHAIN OF 150MM PITCH AND TESTING UNDER...ijiert bestjournal
Chain is the most important element of the industri al processes required for transmitting power and conveying of materials. Roller conveyor chain p erforms efficient and economical in wide range of applications in manufacturing and agricult ural industries. Chains are machine elements that are subjected to extreme service conditions,s uch as high tensile loads,compressive loads,friction,and sometimes aggressive operating enviro nment. The present work focuses on the design calculations of cane carrier roller conveyor chain for calculating breaking load . Finally,experimentation is carried out on Computerized Univ ersal testing Machine (UTM).
This paper describes the analysis of belt bucket elevator used in Myanmar C.P Livestock Co.Ltd Taunggyi feed mill . Material handling process is essential for the production. Bucket elevator has evolved as advanced material handling equipment in mechanized bulk material handling industry. The effective use of different types of bucket elevators completely depends on its design and types of bulk material. Yellow corn raw materials are transported by bucket elevator. In this journal, the use of conveyor systems and the design of bucket elevator with simultaneous buckets for lifting yellow corn at 28.8 m height are presented. And it is 70 tons per hour. The main aim is to share about conveyor systems and to know the calculation of belt design, shaft and pulley. Mg Than Zaw Oo | Ma Myat Win Khaing | Ma Yi Yi Khin "Analysis of Belt Bucket Elevator" Published in International Journal of Trend in Scientific Research and Development (ijtsrd), ISSN: 2456-6470, Volume-3 | Issue-5 , August 2019, URL: https://www.ijtsrd.com/papers/ijtsrd26483.pdfPaper URL: https://www.ijtsrd.com/engineering/mechanical-engineering/26483/analysis-of-belt-bucket-elevator/mg-than-zaw-oo
hello folks;
In this documentation, A 2 stage bevel reduction gearbox is designed.
The example taken is of the gearbox requirement for the Box-shipping conveyor. All the necessary design calculations for gears and shafts are carried out in a proper and easy-to-understand sequence. The material selection, standardized components (keys, oil seals likewise)selection from the design databook is also discussed with reasoning. As and when needed concepts are explained with the help of suitable graphs, visuals, and drawings.
This report is authorized by the team member's name mentioned on Slide.
Thank you!!
If you find it helpful do like&l share it with your engineering friends
Analytical Optimization of Chassis Frame for 40ft Dual-Axle Flatbed Trailer D...IOSR Journals
This article will review a design and analysis study that reduces trailer chassis mass while
minimizing the total cost impact. Design approaches, material selections and proposed section were reviewed.
The Trailer chassis main member were quantified and summarized to create an overall mass and weighted cost
estimate for a low mass Trailer.
Karakuri based dolly frames unstacking systemAnshumanRaj8
The project aims to design a Karakuri Kaizen model to stack and unstack dolly frames efficiently and ergonimically. The design havve been proposed and assembled using standard components from Minitec using Solidworks version 2020. The required inclination angle for the conveyor and the deadwight of the protoype is calculated for the designed assembly. Frame count validation electronic unit is designed to check if the frames per minutes worked in a given set of time is maintained. The electronic unit designed in Kicad , required electronic components and 3d printed, housing for the electronicunit is designed and assembled.
Design, Analysis and Manufacturing of Hydro-pneumatic Press Machineijceronline
A Hydro-pneumatic press is a press machine utilizing both air and oil in its operation and gives higher outlet hydraulic pressure with lower inlet pneumatic pressure. In this project the press is design and manufacture for pressing sleeve bearing into the circular casting part. Casting part is thick cylinder and sleeve bearing is kind of cylindrical bearing. Two actuators are used in the press one is for vertical pressing and other is for horizontal pressing. This paper includes the concept development, design, analysis and manufacturing of press machine. Various parts of the press are modelled by using Pro-E modelling software. Structural analysis has been applied on the parts of press machine by using analyzing software ANSYS.
In India, industries usually have quality range of gantry girders for industrial sheds. Assisted by skilled workers in India, companies have been able to successfully grow towards the zenith, but there is still minor margin remaining which can be achieved by optimally designing the gantry girder in an economic as well as efficient manner. For this purpose, it is essential to implement the procedure for model, design, analyze and validate the girder efficiently.
design of Material handling final year project ppt Ganesh Yande
This paper includes the design of belt conveyor system where the moving roller of the conveyor is powered by a pneumatic cylinder. Pneumatic cylinder will starts reciprocating and by using rack and pinion mechanism the reciprocating motion converts into the rotary motion. These rotary motions further transmit using freewheel-sprocket chain drive to the drive pulley of conveyor. Due to power given by cylinder piston, rack -pinion and freewheel-sprocket chain drives the shaft of pulley starts rotating unidirectional. Hence our belt conveyor is also starts rolling.
Keywords: pneumatic Conveyor, Packing, Material Handling, Rack and Pinion
TECHNICAL TRAINING MANUAL GENERAL FAMILIARIZATION COURSEDuvanRamosGarzon1
AIRCRAFT GENERAL
The Single Aisle is the most advanced family aircraft in service today, with fly-by-wire flight controls.
The A318, A319, A320 and A321 are twin-engine subsonic medium range aircraft.
The family offers a choice of engines
Event Management System Vb Net Project Report.pdfKamal Acharya
In present era, the scopes of information technology growing with a very fast .We do not see any are untouched from this industry. The scope of information technology has become wider includes: Business and industry. Household Business, Communication, Education, Entertainment, Science, Medicine, Engineering, Distance Learning, Weather Forecasting. Carrier Searching and so on.
My project named “Event Management System” is software that store and maintained all events coordinated in college. It also helpful to print related reports. My project will help to record the events coordinated by faculties with their Name, Event subject, date & details in an efficient & effective ways.
In my system we have to make a system by which a user can record all events coordinated by a particular faculty. In our proposed system some more featured are added which differs it from the existing system such as security.
Welcome to WIPAC Monthly the magazine brought to you by the LinkedIn Group Water Industry Process Automation & Control.
In this month's edition, along with this month's industry news to celebrate the 13 years since the group was created we have articles including
A case study of the used of Advanced Process Control at the Wastewater Treatment works at Lleida in Spain
A look back on an article on smart wastewater networks in order to see how the industry has measured up in the interim around the adoption of Digital Transformation in the Water Industry.
Hybrid optimization of pumped hydro system and solar- Engr. Abdul-Azeez.pdffxintegritypublishin
Advancements in technology unveil a myriad of electrical and electronic breakthroughs geared towards efficiently harnessing limited resources to meet human energy demands. The optimization of hybrid solar PV panels and pumped hydro energy supply systems plays a pivotal role in utilizing natural resources effectively. This initiative not only benefits humanity but also fosters environmental sustainability. The study investigated the design optimization of these hybrid systems, focusing on understanding solar radiation patterns, identifying geographical influences on solar radiation, formulating a mathematical model for system optimization, and determining the optimal configuration of PV panels and pumped hydro storage. Through a comparative analysis approach and eight weeks of data collection, the study addressed key research questions related to solar radiation patterns and optimal system design. The findings highlighted regions with heightened solar radiation levels, showcasing substantial potential for power generation and emphasizing the system's efficiency. Optimizing system design significantly boosted power generation, promoted renewable energy utilization, and enhanced energy storage capacity. The study underscored the benefits of optimizing hybrid solar PV panels and pumped hydro energy supply systems for sustainable energy usage. Optimizing the design of solar PV panels and pumped hydro energy supply systems as examined across diverse climatic conditions in a developing country, not only enhances power generation but also improves the integration of renewable energy sources and boosts energy storage capacities, particularly beneficial for less economically prosperous regions. Additionally, the study provides valuable insights for advancing energy research in economically viable areas. Recommendations included conducting site-specific assessments, utilizing advanced modeling tools, implementing regular maintenance protocols, and enhancing communication among system components.
Immunizing Image Classifiers Against Localized Adversary Attacksgerogepatton
This paper addresses the vulnerability of deep learning models, particularly convolutional neural networks
(CNN)s, to adversarial attacks and presents a proactive training technique designed to counter them. We
introduce a novel volumization algorithm, which transforms 2D images into 3D volumetric representations.
When combined with 3D convolution and deep curriculum learning optimization (CLO), itsignificantly improves
the immunity of models against localized universal attacks by up to 40%. We evaluate our proposed approach
using contemporary CNN architectures and the modified Canadian Institute for Advanced Research (CIFAR-10
and CIFAR-100) and ImageNet Large Scale Visual Recognition Challenge (ILSVRC12) datasets, showcasing
accuracy improvements over previous techniques. The results indicate that the combination of the volumetric
input and curriculum learning holds significant promise for mitigating adversarial attacks without necessitating
adversary training.
Sachpazis:Terzaghi Bearing Capacity Estimation in simple terms with Calculati...Dr.Costas Sachpazis
Terzaghi's soil bearing capacity theory, developed by Karl Terzaghi, is a fundamental principle in geotechnical engineering used to determine the bearing capacity of shallow foundations. This theory provides a method to calculate the ultimate bearing capacity of soil, which is the maximum load per unit area that the soil can support without undergoing shear failure. The Calculation HTML Code included.
Vaccine management system project report documentation..pdfKamal Acharya
The Division of Vaccine and Immunization is facing increasing difficulty monitoring vaccines and other commodities distribution once they have been distributed from the national stores. With the introduction of new vaccines, more challenges have been anticipated with this additions posing serious threat to the already over strained vaccine supply chain system in Kenya.
CFD Simulation of By-pass Flow in a HRSG module by R&R Consult.pptxR&R Consult
CFD analysis is incredibly effective at solving mysteries and improving the performance of complex systems!
Here's a great example: At a large natural gas-fired power plant, where they use waste heat to generate steam and energy, they were puzzled that their boiler wasn't producing as much steam as expected.
R&R and Tetra Engineering Group Inc. were asked to solve the issue with reduced steam production.
An inspection had shown that a significant amount of hot flue gas was bypassing the boiler tubes, where the heat was supposed to be transferred.
R&R Consult conducted a CFD analysis, which revealed that 6.3% of the flue gas was bypassing the boiler tubes without transferring heat. The analysis also showed that the flue gas was instead being directed along the sides of the boiler and between the modules that were supposed to capture the heat. This was the cause of the reduced performance.
Based on our results, Tetra Engineering installed covering plates to reduce the bypass flow. This improved the boiler's performance and increased electricity production.
It is always satisfying when we can help solve complex challenges like this. Do your systems also need a check-up or optimization? Give us a call!
Work done in cooperation with James Malloy and David Moelling from Tetra Engineering.
More examples of our work https://www.r-r-consult.dk/en/cases-en/
Student information management system project report ii.pdfKamal Acharya
Our project explains about the student management. This project mainly explains the various actions related to student details. This project shows some ease in adding, editing and deleting the student details. It also provides a less time consuming process for viewing, adding, editing and deleting the marks of the students.
Water scarcity is the lack of fresh water resources to meet the standard water demand. There are two type of water scarcity. One is physical. The other is economic water scarcity.
2. i
Table of contents
List of Illustration ii
Introduction iii
Aim and Objective iv
Specifications iv
1. Design Layout 1
2. Motor Selection 3
3. Belt and Pully Design 6
4. Gear design 13
5. Bevel gear design 19
6. Shaft design 22
7. Keyway design 29
8. Bearing selection 31
9. Clutch 33
References 35
3. ii
List of Illustrations
Figure 1.1 – design view of the Vertical screw conveyor 1
Figure 1.2 a – Rendered View of the Gear Box 1
Figure 1.2 b – Top view and side view 1
Figure 1.3 – Rendered View of the Screw conveyor and Section View 2
Figure 2.1 – JHS400 screw specifications 3
Figure 3.1 – Selection of V-belt cross section 6
Figure 3.2 – Service factor for drives 7
Figure 3.3 – Pully arrangement 7
Figure 3.4 – A section V-belts 8
Figure 3.5 – Power correction factors for belt pitch length 8
Figure 3.6 – Power correction factor for Arc contact 9
Figure 3.7 – Pulley belt arrangement 10
Figure 4.1 – Gear arrangement 13
Figure 4.2 – No: of teeth vs. Involute factor Y 14
Figure 4.3 – Values of Deformation Factor C (kN/m) for Dynamic load 16
Figure 4.4 – terms used in a gear 18
Figure 6.1 – Shaft design 22
figure 6.2 – WD components 22
Figure 6.3 – Bending moment diagram 23
Figure 6.4 – Shaft design 24
Figure 6.5 – Forces acting on gear 26
Figure 6.6 – Bending moment diagram 27
Figure 7.1 – terms in key 29
4. iii
INTRODUCTION
Generally, conveying is accomplished by a combination of mechanical, inertial,
pneumatic, and gravity forces. Application of screw conveyors can be seen almost in every industry
nowadays. Conveyors utilizing primarily mechanical forces are screw, belt, and mass conveyors.
Screw conveyors are widely used for transporting and elevating particulates at controlled and
steady rates. They are used in many bulk materials applications in industries ranging from
industrial minerals, agriculture (grains), pharmaceuticals, chemicals, pigments, plastics, cement,
sand, salt and food processing.
The main reason why the screw conveyors are popular because they can be used for uniform
and continuous supply of various materials in manufacturing machinery and transport devices in
many industries as stated above. So it is a very effective way of elevating bulk materials.
Some advantages of Vertical Screw Conveyors are,
• Ideal for handling dry to semi-fluid materials
• Capacities up to 6,000 cubic feet per hour.
• Ability to elevate bulk materials up to 30-feet without use of internal bearings.
• Totally enclosed design for dust and vapor-tight requirements.
Since they operate over a wide range of speeds and angles of elevation up to the vertical. In
this mini project, we have focused on and designed a Vertical screw conveyor which is fully
enclosed.
5. iv
AIM
To design a Vertical screw conveyor to transport material to a higher elevation from ground
level.
OBJECTIVE
• Selecting the necessary material to be transported vertically.
• Designing the vertical screw conveyor.
• Obtaining the power required for the design and selection of an appropriate motor.
• Design the drive mechanism.
• Design the gear box.
• Design the shaft and selection of keys.
• Selection of bearings.
• Design a suitable clutch.
SPECIFICATIONS
Transport material : Cement
For a higher transfer rate of the selected material (Cement),
Selected Screw : JHS400
∴ pitch of the screw : 350 mm
∴ Vertical screw conveyor height : 3.15 m
Speed of the screw : 60 rpm
6. 1
1. DESIGN LAYOUT
Figure 1.1 – design view of the Vertical screw conveyor
Figure 1.2 a – Rendered View of the Gear Box Figure 1.2 b – Top view and side view
7. 2
Figure 1.3 – Rendered View of the Screw conveyor and Section View
8. 3
2. MOTOR SELECTION
Figure 2.1 – JHS400 screw specifications
Screw blade diameter = 400 mm
Drive shaft diameter = 60 mm
Pitch = 350 mm
Screw blade thickness = 4 mm
Capacity (Q) =
𝜋 (𝐷−𝑑)2× 𝑠 × 𝑛 × 𝑠𝑔 × 𝑖 × 60
4
Where, D = screw diameter (in dm)
d = drive shaft diameter (in dm)
s = pitch (in dm)
n = revolutions per minute
sg = specific weight of the material
i = degree of through filling
𝜆 = Progress resistance coefficient
for Cement, sg = 1600 g
𝜆 = 6.0
i = 0.1
Maximum Capacity (Q) =
𝜋 (4−0.6)2× 3.5 ×60 ×1600 ×0.1 ×60
4
= 18,303,672.78 kgh-1
2.1
9. 4
Im = mass flow rate (ton per hour)
𝜆 = Progress resistance coefficient
L = length (m)
H = height of the Vertical screw driver
(L sin90o
)
The driving power of the loaded screw conveyor is given by,
P = PV + PN + Pst
Where, PV = required power to move the material
PN = required power to operate unloaded screw
Pst = required power for the vertical position of screw conveyor
Material travelling (PV) =
𝐼 𝑚 ×𝐿 × 𝜆 × 𝑔
3600
=
18303.672 ×3.15 × 6.0
3600 ×102
= 0.9421 kW
Unloaded Operated Screw (PN) =
𝐷 × 𝐿
20
=
400 × 3
1000 × 20
= 0.06 kW
Position of the screw (Pst) =
𝐼 𝑚 ×𝐻 × 𝑔
3600
=
18303.672 ×(3.15+0.5)
3600 ×102
= 0.1819 kW
∴ using eqn 2.2,
Screw Conveyor Power = PV + PN + Pst
= 0.9421 + 0.06 + 0.1819
= 1.1840 kW
Losses within the mechanical elements,
Losses due to Gear train = 2% Losses due to belt = 2%
Losses due to drive pully = 3% Losses due to Bearing = 1%
Losses due to pinion pully = 3% Losses due to chain = 5%
Uncountable losses = 5%
2.2
10. 5
Total uncountable losses of = 1184 × (
102
100
×
103
100
×
103
100
×
105
100
×
102
100
×
101
100
×
105
100
) − 1184
the machine
= 271 W
∴ Total Power required = 1455.2126 W
= 1.4552 kW
Motor selection from the Handbook (page No: 04)
Table 2.1 – “4 POLES”, Synchronous motor at 50Hz,
Output (kW) Efficiency (%)
1.5 75.5 ×
2.2 81.5 √
Motor output power = 2.2 ×
81.5
100
= 1.793 kW
1.793 kW > 1.4552 kW (∴ Motor can supply the necessary power required)
∴ selected motor = D100L at 1425 rpm
Transmission ratio =
𝑚𝑜𝑡𝑜𝑟 𝑟𝑝𝑚
𝑠ℎ𝑎𝑓𝑡 𝑟𝑝𝑚
=
1425
60
≈ 24
∴ Transmission ratio = 1: 24
Transmission ratio of the Belt drive = 2: 1
Transmission ratio of the Gear drive = 4: 1
Transmission ratio of the Chain drive = 3: 1
2 | 24 _
4 | 12 _
3 | 3 _
1
11. 6
3. BELT AND PULLY DESIGN
Data:
Transmission ratio of the Belt drive = 2: 1
Power consumption of the Motor = 2.2 kW
Motor rpm = 1425 rpm
From the V-Belt drive handbook,
Selection of V-belt cross section, (page No: 3/79)
Figure 3.1 – Selection of V-belt cross section
According to the design power and rpm of motor,
Type of belt = Type A
Service factor for drives, (page No: 3/80)
Operation hours per day = over 16 hrs.
Type of driven mechanism = Extra heavy duty
Service factor = 1.8
12. 7
Figure 3.2 – Service factor for drives
From the belt ratio,
Let Pitch diameter of smaller pully (d) = 125 mm
Pitch diameter of larger pully (D) = 250 mm
Pitch length of the belt (L) calculations, (page No: 3/78)
Pitch length of the belt (L) = 2𝐶 + 1.57(𝐷 + 𝑑) +
(𝐷−𝑑)2
4𝐶
Where, C = center distance of drive
Figure 3.3 – Pully arrangement
3.1
13. 8
Recommended range for the center distance,
2(𝑑 + 𝐷) ≥ 𝐶 ≥ 0.7(𝑑 + 𝐷)
2(125 + 250) ≥ 𝐶 ≥ 0.7(125 + 250)
750 mm ≥ 𝐶 ≥ 262.5 𝑚𝑚
∴ Taking minimum C value for calculations,
C = 262.5 mm
Substituting for the eqn 3.1,
L = (2 × 262.5) + 1.57(125 + 250) +
(250−125)2
4𝐶
= 1128.6 mm
According to the standard pitch lengths, From Table3C, (page No: 3/69)
Figure 3.4 – A section V-belts
L = 1250 mm
∴ Power correction factor for belt pitch length (type A) = 0.93 (page No: 3/84)
Figure 3.5 – Power correction factors for belt pitch length
14. 9
Center distance calculations, (page No: 3/78)
Center distance (C) = 𝐴 + √(𝐴2 − 𝐵)
Where, A =
𝐿
4
− 𝜋
(𝐷+𝑑)
8
B =
(𝐷−𝑑)2
8
=
1250
4
− 𝜋
(250+125)
8
=
(250−125)2
8
= 165.2378 mm = 1953.1250 mm
Substituting for the eqn 3.2,
C = 165.2378 + √(165.23782 − 1953.1250)
= 324.4400 mm
Number of belts calculation,
No: of belts (X) =
𝐷𝑒𝑠𝑖𝑔𝑛 𝑝𝑜𝑤𝑒𝑟
𝐹𝑖𝑛𝑎𝑙 𝑏𝑒𝑙𝑡 𝑝𝑜𝑤𝑒𝑟
=
𝑁𝑡 𝐾𝑠
𝑁 𝑜 𝐾 𝑒 𝐾1
Where, Nt = Required Power in watts
Ks – Service Factor for Belt Drive
No – Power Rating
Ke – Power Correction Factor for Arc Contact
Kl – Power Correction Factor for Belt Pitch Length
Nt = 2.2 kW Ks = 1.8
Ke = 0.94 Kl = 0.93 (page No: 3/83, page No: 3/84)
Figure 3.6 – Power correction factor for Arc contact
No - Power rating calculations,
From Table9C, (page No: 3/87)
D (mm) Additional Power Ratio
Speed of faster shaft (rpm) 125 2.00 and over
960 1.61 0.12
1425 X Y
1440 2.24 0.17
3.2
3.3
15. 10
Using interpolating method,
X = 2.2
Y = 0.16
∴ No = X + Y
= 2.2 + 0.16
= 2.38
Substituting for the eqn 2.3,
X =
2.2 ×1.8
0.94 ×0.93 ×2.36
= 1.8794
≈ 2 𝑏𝑒𝑙𝑡𝑠
∴ two V-belts are required to transmit the power.
Assessing the required no: of belts using standard equation
Figure 3.7 – Pulley belt arrangement
2.3 log |
𝑇1
𝑇2
| = 𝜇𝜗𝐶𝑜𝑠𝑒𝑐(𝛽) where, T1, T2 = tensions of the belt
𝜗 = angle of contact
𝜇 = coefficient of friction
𝛽 = Nominal include angle
Assuming 𝜇 = 0.3
From the V-Belt drive handbook,
Table 2A, (page No: 3/66)
T1 + T2 = 200
Table 1, (page No: 3/65)
2𝛽 = 40
◦
3.4
17. 12
Material selection,
Pulley material - Cast Iron
Due to reduced weight and their low cost.
V- Belt material - Thermoplastic polyester elastomer, with a shore hardness 92A,
Since this is a heavy-duty mechanism, the V-belt temperature should have a vast range.
Therefore, the selected material has a temperature range of -5° to 70° C
Table 3.1 - Pully characteristics
Characteristics Smaller Pully Larger Pully
Material Cast Iron Cast Iron
Pitch Diameter (mm) 125 250
Outside Diameter (mm) 133 258
Torque (Nm) 10.4044 20.8088
18. 13
4. GEAR DESIGN
Data:
Transmission ratio = 1:4
Tn = no: of teeth
Nn = gear speed (rpm)
Dn = diameter of the gear (mm)
𝑁1
𝑁2
=
𝐷1
𝐷2
4
1
=
𝐷1
𝐷2
∴ assuming that, D1 = 100 mm
D2 = 400 mm Figure 4.1 – Gear arrangement
Module (m) =
𝐷
𝑇
From the Gears and Shaft handbook, (page No: 10)
standard module series, m = 4
∴ No: of teeth for each Gear,
T1 =
100
4
T2 =
400
4
= 25 = 100
From the reduction of pulleys,
Speed of Gear 1 = 712.5 rpm
Table 4.1 – Gear characteristics
Gear 1 Gear 2
N (rpm) 712.5 178.125
D (mm) 100 400
T 25 100
For the design, 20◦ stub involute system (y) (page
y 0.133 0.161
19. 14
Figure 4.2 – No: of teeth vs. Involute factor Y
Material selection,
Material selected = Alloy Steel (SNCM439) [4.1]
Tensile strength ( 𝜎ut) = 980 N/mm2
Allowable Static Stress ( 𝜎o) =
σ 𝑢𝑡
3
=
980
3
= 326.6667 N/mm2
Strength Factor,
Gear 1, Gear 2,
𝜎o1 = 𝜎o x 0.133 𝜎o2 = 𝜎o x 0.161
= 43.4467 N/mm2 = 52.5933 N/mm2
Here the Strength factor for G1 is less than that of G2
𝜎o1 < 𝜎o2
∴ the rest of the calculations are done to the G1.
20. 15
Torque in Gear 1 = 20.8088 Nm (∵ torque is not changed throughout the shaft)
Circular pitch (Pc) = π x m
= π x 4
= 12.5663 mm
Tangential Load (WT1) =
2𝑇
𝐷
=
2×20.8088
100×10−3
= 416.176 N
Normal load (WN1) =
𝑊𝑇
cos(𝜃)
=
416.176
𝐷 cos(20)
= 442.8852 N
Let normal pressure between tooth is 45 N/mm-1
Face Width (b) =
442.8852
45
= 9.8419 mm
Pitch line Velocity of the Gear wheel 1
V = rω
=
100×10−3
2
×
2𝜋
60
× 712.5
= 3.7306 ms-1
Value of Deformation Factor C, (page No: 30)
Assuming both pinion and gear material is Steel
Taking the maximum tooth error = 0.08 mm
C = 952 x 103 Nm-1
21. 16
Figure 4.3 – Values of Deformation Factor C (kN/m) for Dynamic load
W1 =
21×𝑉×(𝑏.𝐶+ 𝑊𝑇1)
21×𝑉+ √𝑏.𝐶+ 𝑊𝑇1
=
21×3.7306×(9.8419×952+ 416.176)
21×𝑉+ √9.8419×952+ 416.176
= 4344.35 N
∴ Dynamic Tooth load (WD) = WT + W1
= 416.176 + 4344.35
= 4760.5247 N
For Alloy steel, Hardness = 300 BHN (using Hardness Table)
[4.2]
∴ Static Tooth load (Ws) = 𝜎e x b x π x m x y where, 𝜎e = 17.5 x Hardness
= (17.5 x 300) x 9.8419 x π x 4 x 0.133
= 85989.7891 N
For Safety,
Ws ≥ WD
∴ the condition satisfies for the obtained values
22. 17
Wear Tooth Load (Ww) = Dp x b x Q x k
Where, DP = Pitch circle diameter of the pinion
b = Face width of the pinion
Q = Ratio factor
K = Load-stress factor
Q =
2 ×(𝑉.𝑅)
(𝑉.𝑅)+1
Where, (V.R) =
𝑇1
𝑇2
=
100
25
= 4
=
2 × 4
4+1
= 1.6
K =
(𝜎 𝑒𝑠)2 𝑆𝑖𝑛 𝜃
1.4
{
1
𝐸 𝑝
+
1
𝐸 𝑔
} Where, 𝜎 𝑒𝑠 = Surface endurance limit
𝜃 = Pressure angle
EP = Young's modulus for the material of the pinion
EG = Young's modulus for the material of the gear in
=
(28×300−70)2 𝑆𝑖𝑛(20)
1.4
{
1
189×103
+
1
189×103
}
= 179.3832 N/mm2
Substituting values to eqn 4.1,
Ww = 100 x 9.8419 x 1.6 x 179.3832
= 282420.9101 N
For Safety,
Ww ≥ WD
∴ the condition satisfies for the obtained values
Table 4.2 - Gear Characteristics
Characteristics Gear 1 Gear 2
Material Alloy Steel (SNCM439) Alloy Steel (SNCM439)
Diameter (mm) 100 400
N (rpm) 712.5 178.125
T 25 100
4.1
23. 18
Two gear wheels are designed, which are spur gears and the module for all the gears are same.
Module (m) = 4
Figure 4.4 – terms used in a gear
From the Machine Design – R. S. Khurmi -Table 28.1 (page No: 1032)
Table 4.3 – Particulars for 20degree stub involute system
Table 4.4- Gear Particulars
Particulars Gear 1 Gear 2
Addendum (mm) 3.2 3.2
Dedendum (mm) 4 4
Working Depth (mm) 6.4 6.4
Minimum tool depth (mm) 7.2 7.2
Total Thickness (mm) 6.6283 6.6283
Minimum clearance (mm) 0.8 0.8
Fillet radius at root (mm) 1.6 1.6
25. 20
Assuming tooth form factor, Y = 0.154 −
0.912
𝑇 𝐸
YP = 0.154 −
0.912
21.08
YG = 0.154 −
0.912
189.8
= 0.111 = 0.149
(𝜎 𝑂𝑃 × 𝑌𝑃) = 100 x 0.111 (𝜎 𝑂𝐺 × 𝑌𝐺) = 70 x 0.149
= 11.1 = 10.43
∴ (𝜎 𝑂𝑃 × 𝑌𝑃) > (𝜎 𝑂𝐺 × 𝑌𝐺)
i.e. the gear is weaker
thus, the design should be based upon the gear.
Torque on gear = 83.2352 Nm (from previous calculations)
Tangential load on gear (WT) =
2𝑇
𝐷 𝐺
=
2𝑇
𝑚.𝑇 𝐺
=
2 ×83.2352 × 103
𝑚 ×60
=
2.7745 × 103
𝑚
N
Pitch line Velocity (V) =
𝜋𝐷 𝐺×𝑁 𝐺
60
=
𝜋𝑚.𝑇 𝐺×(
𝑁 𝑃
3
)
60
=
𝜋𝑚×60×(
178.125
3
)
60
= 0.1865(m) ms-1
Velocity factor (Cv) =
3
3+𝑉
=
3
3+0.1865𝑚
Length of pitch cone element (L) =
𝐷 𝐺
2𝑆𝑖𝑛(𝜃 𝐺)
=
𝑚𝑇 𝐺
2𝑆𝑖𝑛(𝜃 𝐺)
=
𝑚60
2𝑆𝑖𝑛(71.57)
= 31.62(m) mm
5.1
5.2
26. 21
Assuming that face width is half of L,
Face Width (b) =
𝐿
2
=
31.62𝑚
2
= 15.81(m) mm
From 5.1, 5.2, and 5.3,
WT = (𝜎 𝑂𝐺 × C 𝑉) 𝑏𝜋𝑚𝑌𝐺(
𝐿−𝑏
𝐿
)
2.7745 × 103
𝑚
= 70 × (
3
3+0.1865𝑚
) (15.81𝑚)𝜋𝑚(0.149) (
31.62−15.81
31.62
)
2.7745 × 103
𝑚
=
24570.7931𝑚2
𝑚31.62(3+0.1865𝑚)
3.5705 =
𝑚2
(3+0.1865𝑚)
0 = m3 – 0.6659m-10.7115
m = 2.3049 mm and m = -1/1525±1.8218i mm
∴ m = 3
∴ b = 15.85(m)
= 15.81 x 3
= 47.43 mm
Pitch diameters
DG = mTG DG = mTG
= 3 x 20 = 3 x 60
= 60 mm = 180 mm
5.3
27. 22
6. SHAFT DESIGN
Figure 6.1 – Shaft design
For Gear 1,
TD = 20.8088 Nm (from previous calculations, Section 3)
FD =
𝑇 𝐷
𝑅 𝐷
= 416.176 N
WD = 442.8852 N (from previous calculations, Section 4)
Vertical component of WD = WD Cos (20)
= 416.1759 N
Horizontal component of WD = WD Sin (20) figure 6.2 – WD components
= 151.4757 N
For Pulley,
WP = Tension T1 + Tension T2
= 183.46 + 16.5339
= 199.9999
≈ 200 𝑁
28. 23
Using Beam Calculations
[6.1]
RAV = 386.971 N
RBV = 229.029 N
RAH = 39.086 N
RBH = 112.914 N
The Resulting Bending Moment for pt
A and D,
Resultant Bending Moment at A
= √ 𝑀𝐴𝑉
2
+ 𝑀𝐴𝐻
2
= 14000 N.mm
Resultant Bending Moment at D
= √ 𝑀 𝐷𝑉
2
+ 𝑀 𝐷𝐻
2
= 11490.7253 N.mm
Maximum bending moment is at D,
Bending Moment at D= 14000 N.mm
Assuming same torque = 20.8088 Nm
Figure 6.3 – Bending moment diagram
29. 24
Material selection
Alloy steel
Km = 2 Shear stress (𝜏) = 0.3 x (Yield stress)
Kt = 1.5 = 147 MNm-2
Yield stress = 490 MNm-2 stress (𝜎) = 0.6 x (Yield stress)
= 294 MNm-2
Diameter Calculations
Equivalent Twisting moment (Te) = √(𝐾 𝑚 × 𝑀)2 + (𝐾𝑡 × 𝑇)2
= √(2 × 14000 × 10−3)2 + (1.5 × 20.8088)2
= 41.9317 Nm
Te =
𝜋
16
× 𝜏 × 𝑑3
41.9317 = 𝜋
16
× 147 × 106
× 𝑑3
d = 11.3257 mm
Equivalent Bending moment (Me) =
1
2
[(𝐾 𝑚 × 𝑀) + 𝑇𝑒]
= 14020.9659
Me =
𝜋
16
× 𝜎 × 𝑑3
14020.9659 = 𝜋
16
× 294 × 106
× 𝑑3
d = 7.8608 mm
taking the larger of the two values,
d = 11.32 mm
≈12 mm
30. 25
Figure 6.4 – Shaft design
For Bevel gear (D),
T = 83.2352 Nm
L = 31.62 m
Mean Radius of Gear (Rm) = (𝐿 −
𝑏
2
)
𝐷 𝐺
2𝐿
= (31.62 −
15.81
2
)
60 ×10−3
2×31.62
= 2.25 mm
∴ tangential force acting at mean radius (WT) =
𝑇
𝑅 𝑚
=
83.2352
0.0225
= 3699.3422 N
Axial force acting on the bevel gear shaft (WRH) = (WT)tan(ø)Sin(𝜃 𝑃)
= 3699.3422 x tan(20) x Sin(18.43)
= 425.6744 N
31. 26
Radial force acting on bevel gear shaft (WRV) = (WT)tan(ø)Cos(𝜃 𝑃)
= 3699.3422 x tan(20) x Cos(18.43)
= 1277.3911 N
For Gear (B),
TB = 83.2352 Nm
WD = 442.8852 N (from previous calculations)
WDV = 416.1759 N
WDH = 151.4157 N
Figure 6.5 – Forces acting on gear
Please Turn Over for the Bending Moment calculations.
32. 27
Using Beam Calculations
[6.1]
RAV = 165.29 N
RCV = 1858.286 N
RAH = 45.314 N
RCH = 623.314 N
The Resulting Bending
Moment for pt
B and C,
Resultant Bending Moment at
B = √ 𝑀 𝐵𝑉
2
+ 𝑀 𝐵𝐻
2
= 7712.4428 N.mm
Resultant Bending Moment at
C = √ 𝑀 𝐶𝑉
2
+ 𝑀 𝐶𝐻
2
= 87502.7551 N.mm
Figure 6.6 – Bending moment diagram
33. 28
Maximum bending moment is at C,
Bending Moment at C = 87502.7551 N.mm
Torque = 83.2352 Nm
Diameter Calculations
Equivalent Twisting moment (Te) = √(𝑀)2 + (𝑇)2
= √(87502 × 10−3)2 + (83.2352)2
= 120.7635 x 103 N.mm
Te =
𝜋
16
× 𝜏 × 𝑑3
120.7635 x 103 = 𝜋
16
× 147 × 106
× 𝑑3
d = 16.1135 mm
≈ 𝟏𝟖 𝒎𝒎
34. 29
7. KEYWAY DESIGN
Data:
Shaft material = Alloy Steel
Shear stress = 147 MNm-2
Crushing stress = 294 MNm-2
Diameter of the shaft (d) = 18 mm
Figure 7.1 – terms in key
From the Machine Design – R. S. Khurmi -Table 13.1 (page No: 472)
Table 7.1 – Key cross section value for Shaft diameter
For 18 mm shaft,
Width (w) = 8 mm
Thickness (t) = 7 mm
35. 30
Considering shearing of the key,
T = 𝑙 × 𝜏 × 𝑤 (
𝑑
2
)
T = 𝑙 × 147 × 8 (
18
2
)
T = 10584 (𝑙)
Torque transmitted from shaft (T) =
𝜋
16
× 𝜏 × 𝑑3
=
𝜋
16
× 147 × 183
= 16331.2468 N.mm
∴ 16331.2468 = 10584 (𝑙)
(𝑙) = 15.9043 mm
Considering crushing of the key,
T = 𝑙 × 𝜎 ×
𝑡
2
(
𝑑
2
)
16331.2468 = 𝑙 × 294 ×
7
2
(
18
2
)
16331.2468 = 9261 (𝑙)
(𝑙) = 18.1764 mm
∴ shearing (𝑙) < crushing (𝑙)
Length of ley (𝑙) = 18.1764 mm
36. 31
8. BEARING SELECTION
Data:
Shaft diameter = 18 mm
Shaft speed = 178.9 rpm
Extra heavy Duty = over 16 hrs
Bearing type = Deep Groove Ball bearing
Maximum load (Fr) = 416 + 1277
= 1693 N
From bearing Handbook, (page No: 31)
Equivalent Fr for 1693 N = 2000 N
Equivalent Shaft rpm for 178.9 rpm = 200 rpm
∴ (C/P) = 2.88
L10h = (hours per day) x (weekdays) x (Weeks per year) x (No: of years)
= 16 x 6 x 25 x 2
= 4800 h
C = 4800 x 2.88
= 13824
From bearing Handbook, (page No: 119)
Equivalent Diameter for 18 mm = 20 mm
Equivalent C for 13824 = 15900
∴ D = 52 mm
B = 15 mm
∴ Shaft diameter is altered to 20 mm
38. 33
9. CLUTCH
Data:
Torque = 20.8088 Nm
outer diameter of friction surface = d2
inner diameter of friction surface = d1
For uniform wear conditions,
P x r = c (constant)
At inner radius. Intensity of pressure is at maximum.
Pmax x r = c c = 0.3
𝑑2
2
Nmm-1
Material selection,
Inner
From Machine Design – R. S. Khurmi – Table 24.1 (page No: 887)
Table 9.1 – Material selection table
Material = Powder metal on cast iron
Assuming that,
Both sides are effective, n = 2
Ratio of the diameter = 1.25 i.e. (r1/r2 = 1.25)
39. 34
Normal load acting on the friction surface (W) = 2𝜋𝑐(𝑟1 − 𝑟2)
= 2𝜋 × 0.3𝑟2(1.25𝑟2 − 𝑟2)
= 0.47𝑟2
2
Mean radius of the friction surface (R) =
𝑟1+𝑟2
2
=
1.25𝑟2+𝑟2
2
= 1.125 𝑟2
Torque transmitted ( T) = 𝑛 × 𝜇 × 𝑊 × 𝑅
20.8088 = 2 x 0.4 x 0.47 𝑟2
2
x 1.125 𝑟2
0.423 𝑟2
3
= 20.8088
𝑟2 = 3.66 mm
𝑟1 = 1.25 𝑟2
= 4.575 mm