Selecting the Right Gear Coupling for your ApplicationDesign World
This webinar will place the spotlight on gear couplings with a focus on factors to consider when making a coupling selection for your application. Topics covered will include basic sizing, application criteria, coupling design features and the variety of coupling types available.
Selecting the Right Gear Coupling for your ApplicationDesign World
This webinar will place the spotlight on gear couplings with a focus on factors to consider when making a coupling selection for your application. Topics covered will include basic sizing, application criteria, coupling design features and the variety of coupling types available.
Designing Engineers, Lmtd.A Pseudonym for ME 154 A divi.docxsimonithomas47935
Designing Engineers, Lmtd.
A Pseudonym for ME 154
A division of Mechanical Engineering Dept.
03 June 2016
To: Project Engineers
From: Michael Jenkins, Engineering Manager
Re: Design Project 5 (Design of a small speed reducer)
A large commercial customer from Mexico has approached us about submitting a bid for an order of 1000
small speed reducers. These speed reducers are to accept an input of 2.25 kW at a shaft speed of 2000 rpm
and will have a reduction ratio of 3.15:1 with the output shaft rotating in the same direction as the input. The
input and output shafts are to be on opposite sides of the casing and are to be parallel to each other. The
external parts of the shafts are solid, circular pieces of standard sizes and will have standard square key ways.
There will be no significant axial load placed on the shafts from external sources. The shafts will overhang
the face of the casing by 3 times the shaft diameter. The external loads will be applied by flexible couplings
which transmit only torque to the shaft. The power source is an electric motor and the driven load will be
smooth in nature. Reversal of the input rotation is anticipated on occasion. Any necessary lubrication should
be by grease packed into the casing (no liquid lubricants!). Minimal maintenance may be expected in use.
Your job is to design the internal workings of the speed reducer (e.g., gear set, chain and sprocket, etc) along
with associated shafts and bearings. Also design a suitable casing, being sure to allow for assembly, mounting
to convenient flat surfaces, and sealing of any grease. Provide a complete set of your final design calculations
and a set of component and assembly drawings. Describe your design process in your final FORMAL report.
Be sure to list and defend assumptions and major design decisions. Describe alternative designs which were
considered, giving reasons for their rejections. Include materials selection and manufacturer and part numbers
for any purchased parts (e.g. bearings).
Note, if an "off-the-shelf" speed reducer is selected, the above requirements are not obviated and your final
report shall include design calculations to confirm the vendor's design.
Provide a list of parts, approximate cost of each part, and method of fabrication (or procurement). Also
provide an estimate of the assembly time.
Your design teams should not exceed five, nor be less than two persons. One person shall be designated as the
lead. The lead, rather than the group collective, is responsible for communicating with me. I expect periodic
progress reports as follows:
Friday, 03 June 2016: Gant chart showing major tasks and anticipated completion dates (hard + soft copies)
Tuesday, 07 June 2016: Brief milestone report indicating a preliminary design compared to
alternative designs and selection rationale (hard + soft copies)
Thursday, 09 June 2016: Draft of final report including organization, l.
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, 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.
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.
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.
About
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
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Technical Specifications
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
Key Features
Indigenized remote control interface card suitable for MAFI system CCR equipment. Compatible for IDM8000 CCR. Backplane mounted serial and TCP/Ethernet communication module for CCR remote access. IDM 8000 CCR remote control on serial and TCP protocol.
• Remote control: Parallel or serial interface
• Compatible with MAFI CCR system
• Copatiable with IDM8000 CCR
• Compatible with Backplane mount serial communication.
• Compatible with commercial and Defence aviation CCR system.
• Remote control system for accessing CCR and allied system over serial or TCP.
• Indigenized local Support/presence in India.
Application
• Remote control: Parallel or serial interface.
• Compatible with MAFI CCR system.
• Compatible with IDM8000 CCR.
• Compatible with Backplane mount serial communication.
• Compatible with commercial and Defence aviation CCR system.
• Remote control system for accessing CCR and allied system over serial or TCP.
• Indigenized local Support/presence in India.
• Easy in configuration using DIP switches.
Hierarchical Digital Twin of a Naval Power SystemKerry Sado
A hierarchical digital twin of a Naval DC power system has been developed and experimentally verified. Similar to other state-of-the-art digital twins, this technology creates a digital replica of the physical system executed in real-time or faster, which can modify hardware controls. However, its advantage stems from distributing computational efforts by utilizing a hierarchical structure composed of lower-level digital twin blocks and a higher-level system digital twin. Each digital twin block is associated with a physical subsystem of the hardware and communicates with a singular system digital twin, which creates a system-level response. By extracting information from each level of the hierarchy, power system controls of the hardware were reconfigured autonomously. This hierarchical digital twin development offers several advantages over other digital twins, particularly in the field of naval power systems. The hierarchical structure allows for greater computational efficiency and scalability while the ability to autonomously reconfigure hardware controls offers increased flexibility and responsiveness. The hierarchical decomposition and models utilized were well aligned with the physical twin, as indicated by the maximum deviations between the developed digital twin hierarchy and the hardware.
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.
Saudi Arabia stands as a titan in the global energy landscape, renowned for its abundant oil and gas resources. It's the largest exporter of petroleum and holds some of the world's most significant reserves. Let's delve into the top 10 oil and gas projects shaping Saudi Arabia's energy future in 2024.
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.
Student information management system project report ii.pdf
Design of a Gear Reducer for a Tractor
1. Final Design Project:
Design of a Gear Reducer for a Tractor
MNE-381 Design for Machine Elements
Dr. Afsoon Amirzadeh
Adam York
Karoly Fodor
Thomas Napert
Diarny Fernandes
Fall Semester 2014
2. Introduction
Tractors require robust and reliable components due to the combination of a large engine
torque and the often jerky and uneven loading experienced by the drive train and gears. Such
conditions require careful and methodical design. For this project, teams were given design
requirements and dimensional constraints and expected to design a gear reducer for a tractor that
could feasibly be manufactured. Two gear-pinion pairs were required, and had to be designed in
such a way as to fit inside a 22” x 22” x 25” gearbox while adhering to US standard dimensional
constraints. The reducer has to transmit 22 horsepower and reduce an input velocity of 1800
RPM to a range between 330 and 335 RPM while having an input shaft that is in line with the
output shaft. The design of this gearbox was done to reinforce and prove the concepts learned in
class.
Gear Design
Note: Unless otherwise specified, all references to tables, figures, or appendices refer to the
textbook.
Adequate diameters and amounts of teeth were determined for each gear and pinion with
the use of the residual method. Hunting teeth were avoided by making non-integer velocity
ratios. Diametral pitches for the gears were chosen based on table 8-3 in the book. We ended up
with the first pinion and gear having 55 and 128 teeth, and the second pinion and gear having 44
and 102 teeth, respectively. In accordance with figure 9-24, the first pair was given a Pd of 8
because it receives an input speed of 1800 RPM at 22hp, and the second pair was given a Pd of
10 because it receives 773 RPM at 22hp. Both of these diametral pitches are US standard coarse
pitch values, according to table 8-3. Using table 9-12, a design life of 5000 hours was used,
which is suitable for both automobiles and agricultural equipment. An AGMA quality number of
A6 and a reliability of 99% were used to compliment that design life, according to table 9-3 and
9-11, respectively. We ended up with a minimum hardness of 214.77 HB for the first pair and
318.33 HB for the second. Because of this, we chose SAE 1015 SWQT 350 for the first pair and
SAE 5150 OQT 1000 for the second pair, which we found in Appendix 5. After selecting a
material for each gear, we checked out safety factor (Sf) values to make sure our design could
adequately handle loading. We also solved for the size factor (cs) and S’n values again to ensure
3. that they would be adequate. These calculations can be seen in the appendix of this report. We
also determined that the backlash for the first gear pair would be 0.0095”, and 0.01” for the
second pair, according to table 8-5. The calculations for the gears in this project are shown in
appendix A of this report. Parameters for the gears are shown on tables A, B, and C on the
following pages.
Table A: Geometry Parameters
Parameter Symbol Pinion 1 Gear 1 Pinion 2 Gear 2
Pitch diameter D 5.5" 12.8" 5.5" 12.75"
Outside diameter Do 5.7" 13" 5.75" 13"
Root diameter Dr 5.25" 12.55" 5.188" 12.438"
Base circle diameter Db 5.168" 12.028" 5.168" 11.981"
Addendum a 0.1" 0.1" 0.125" 0.125"
Dedendum b 0.125" 0.125" 0.156" 0.156"
Clearance c 0.025" 0.025" 0.031" 0.031"
Circular Pitch p 0.314" 0.314" 0.393" 0.393"
Whole Depth ht 0.225" 0.225" 0.281" 0.281"
Working Depth hk 0.2" 0.2" 0.25" 0.25"
Tooth Thickness t 0.157" 0.157" 0.196" 0.196"
Center Distance C 9.15" 9.13" 9.15" 9.15"
Fillet radius in basic rack rf 0.03" 0.03" 0.037" 0.037"
Bending Geometry Factor J 0.459 0.479 0.43 0.465
Pitting Geometry Factor I 0.114 0.114 0.112 0.112
Table B: Force and Speed Factors
Parameter Symbol Pair 1 Pair 2
Input Speed np - ng 1800 rpm 773.438 rpm
Output speed ng - np 773.438 rpm 333.64 rpm
Gear ratio mg 2.327 2.318
Quality number Av 6 8
Face Width F 1.2 1.5
Pitch Line Speed vt 2591.814 ft/s 1113.67 ft/s
Tangential Force Wt 280 lbf 651.636 lbf
Normal Force Wn 297.97 lbf 693.457 lbf
Radial Force Wr 101.912 lbf 237.176 lbf
Size Factor Ks 1 1
Load Distribution Factor Km 1.145 1.159
Dynamic Factor Kv 1.116 1.206
4. Table C: Additional Force and Speed Factors
Force/Speed Factor Symbol Pinion 1 Gear 1 Pinion 2 Gear 2
Rim Thickness Factor Kb 1.292 1.292 1.649 1.649
Number of Load Cycles Nc 6.48E+08 2.78E+08 2.78E+08 1.20E+08
Bending Stress Cycle Factor Yn 0.945 0.959 0.959 0.974
Pitting Stress Cycle Factor Zn 0.909 0.926 0.926 0.944
Expected Bending Stress St 16775.995 psi 16089.089 37251.553 psi 34444.64 psi
Expected Contact Stress Sc 70924.55 psi 70924.55 psi 102272.472 psi 102272.472 psi
Allowable Bending Stress # Sat 15092.376 psi 14258.403 psi 33012.912 psi 30071.942 psi
Allowable Contact Stress # Sac 66354.946 psi 65078.242 psi 93842.157 psi 92044.87 psi
Shaft Design
Note: Unless otherwise specified, all references to tables, figures, or appendices refer to the
textbook.
Shaft 1 and 3 were modeled hypothetically in for a range between 6” and 11” long. The
6” shaft was determined to be the best choice because its short length minimized bending and
deflection while maintaining a large enough clearance between shaft ends to account for the
bearing mounts. Shaft 2 was made to be 15” long to match the length of shafts 1 and 3. After
some analysis and several checks, these shaft lengths turned out to be satisfactory. All of the
shaft diameters were set to US standard sizes as shown in appendix A2-1, except for the shaft
ends. The shaft ends were given diameters equal to standard bearing sizes according to table 14-
3. The material selected for all three of the shafts was SAE 4140 OQT 1300 steel because of its
high tensile strength and ductility. The material properties in question were found in appendix 3.
The bulk of each shaft had a constant diameter, with the exception of the shaft ends. The
reasoning behind this was two-fold: keeping a constant diameter on either side of the gear saves
material while making manufacturing easier, since the gear can be slid onto the shaft from either
end. This meant that each gear would have to be held in place by two retaining rings. Because of
the loading requirements, a pair of appropriately sized CR heavy duty spiral rings would be used
to hold each gear in place. A design factor (N) of 4 was used for the shafts, which we checked
5. after selecting standard sizes. The calculations for the dimensions, loading and safety factors of
each shaft are described in appendix B of this report. Parameters for shaft 1, 2 and 3 are shown
on tables D, E and F, respectively, on the following pages. Diagrams (not to scale) of each shaft
are provided in figures A, B and C to clarify the information on the tables.
Figure A: Shaft 1
Table D-1:
Tangential Force (lb) Radial Force (lb) Torque (lb -in) Reaction-y (lb) Reaction-x (lb)
280.00 101.91 770.00 50.96 140.00
Table D-2:
Section (D) Stress Factor (Kt) Moment [M] (lb-in) Torque [T] (lb-in)
1 2.50 0.00 770.00
2 3.00 446.95 770.00
3 2.00 446.95 770.00
4 3.00 446.95 0.00
5 2.50 0.00 0.00
Table D-3:
Section
(D)
Minimum Diameter
[Dmin] (in)
Min. Dia. with
Ring Groove
Standard
Diameter
Cs Check New S'n
1 0.65 - 1.1811 0.860 30652.75
2 1.25 1.32 1.4 0.844 30084.79
3 1.09 - 1.4 0.844 30084.79
4 1.24 1.32 1.4 0.844 30084.79
5 0.00 - 1.1811 0.860 30652.75
8. Table F-3
Section [D] Min. Dia. with Ring Groove Standard Diameter Cs Check New S'n
1 - 1.57 0.83 29697.93
2 1.77 1.80 0.82 29264.50
3 - 1.80 0.82 29264.50
4 1.74 1.80 0.82 29264.50
5 - 1.57 0.83 29697.93
Table F-4
SAE 4140 OQT 1300
S'n 28512
Sn 44000
Cm 1
Cst 1
CR 0.81
Cs 0.8
Because of the compact nature of the shafts, bending moments and shaft deflections were
minimized. This is important since large deflections could possibly result in improper gear
meshing or even shaft failure. Deflection information is shown on table G below, where
negatives denote downward deflections. Since shaft 2 would be subjected to moments and
deflection at two different locations, worst case loading was used in our calculations. All
pertinent formulas are from A14-1 in the textbook.
9. Table G-1: Shaft Deflections
Shaft Diameter
[D] (in)
Area Moment of Inertia
[I] (in4
)
Load [P]
(lb)
Modulus of Elasticity [E] (psi)
1 1.40 0.19 101.91 30458000
2 2.20 1.15 237.18 30458000
3 1.80 0.52 237.18 30458000
Table G-2: Shaft Deflections (cont.)
Shaft Total Length [L]
(in)
Length from Edge to Load [a]
(in)
Max Deflection [ymax] (in)
1 6.00 3.00 -7.98E-05
2 15.00 3.00 -5.41E-04
3 6.00 3.00 -6.80E-05
Keys
Note: Unless otherwise specified, all references to tables, figures, or appendices refer to the
textbook.
All of the keys were designed to be made out of SAE 1018 steel, according to table 11-4.
The height and width of the keys were set according to the US standard sizes found in table 11-1,
while the proper lengths of the keys were found in appendix A2-1. Standard fillet radii were
found in table 11-2. Because the keys are composed of a weaker material, they will fail before
the gears or shafts are damaged in an overload situation. This is desirable, since the keys are
significantly less expensive to produce or replace, and their failure would serve to preserve the
gears and shafts. Selected information about the keys is provided in table H on the following
page.
10. Table H: Key Parameters
Parameter Key 1 (shaft 1) Key 2 (shaft 2) Key 3 (shaft 2) Key 4 (shaft 3)
Diameter of Shaft [D] (in) 1.4 2.2 2.2 1.8
Height [H] (in) 0.375 0.625 0.625 0.375
Width [W] (in) 0.375 0.625 0.625 0.375
Yield Strength [Sy] (psi) 54000 54000 54000 54000
Torque [T] (lb-in) 770 1792 1792 4154
Length [Torque] (in) 0.326 0.29 0.29 1.368
Length [Normal Stress] (in) 0.326 0.29 0.29 1.368
Minimum Length [L] (in) 0.326 0.29 0.29 1.368
Closest Standard [L] (in) 0.375 0.3125 0.3125 1.5
Chordal Height [Y] 0.03 0.05 0.05 0.02
Depth of Key seat [S] 1.19 1.84 1.84 1.59
T-Value [T] 1.56 2.47 2.47 1.97
Standard Fillet Radii 0.031 0.063 0.063 0.031
Bearings
Note: Unless otherwise specified, all references to tables, figures, or appendices refer to the
textbook.
With the exception of the bearing pair on which shaft 3 rotates, all of the bearings in this gearbox
are US standard 6006 bearings. The bearings holding shaft 3 are US standard 6008 bearings. All
of the standard bearing sizes and parameters were found in table 14-3 in the textbook. The
process was simplified by designing the shaft ends to have a diameter equal to the inner diameter
of a standard bearing. The bearings we selected are very strong and far exceed the design
requirements, but this was unavoidable since their size had to be taken into consideration as well.
However, this also ensures that the bearings will not have to be replaced throughout the useful
life of the gearbox. The parameters for each bearing assembly are shown on table I on the
following page.
11. Table I: Bearing Parameters
Parameter
Bearing Pair
(shaft 1)
Bearing 3
(shaft 2)
Bearing 4
(shaft 2)
Bearing Pair
(shaft 3)
Design Load [Pd] (lb) 50.96 128.96 210.12 118.59
Design Load [Ld] (h) 5000 5000 5000 5000
Bearing Coefficient [k] 3 3 3 3
Rotation Speed [ω] (RPM) 1800 773.6 773.6 332.48
Basic Dynamic Load [C] (lb) 414.95 792.53 1291.28 549.48
Standard Bearing 6006 6006 6006 6008
Conclusion
Through the surprisingly complex design process of a mechanically simple gear reducer,
we came to appreciate the considerable amount of thought that goes into engineering mechanical
systems. The design process took numerous hours and multiple failed attempts, but successfully
enlightened our group on what it is like to design machine elements, however simple they may
be. We learned about the importance of precise calculation, the integration calculations and
mechanical drawings through CAD software, and about the convenience of industry standard
dimensions and factors. But perhaps the most important takeaway of this project was an
appreciation for the engineering techniques we used. There are people in the world who use the
very methods we used in this project to design things of astounding complexity, such as
automatic transmissions or large scale manufacturing equipment. Even though we are at a novice
level when it comes to engineering, the knowledge that the material we are learning today could
someday help us design the machines that enable our modern society to flourish made the
relative tedium of this project well worth it.