Xianwei Xia Portfolio

Mechanical Engineering Design Portfolio

Xianwei Xia

(Master’s Degree in Mechanical Engineering)

Mechanical Projects:-

Human Power Water Cleaner

Waste Heat powered CHP System

Cold Food Storage

Internship:-

GSMA Project Management Intern

Welcome, and thank you for taking the time to visit my

portfolio.

The Goal of this portfolio is to give you a deeper insight

into my experiences and skills I have gained over my

study.

Hopefully this will allow you to understand better how my skills can be applied to your

company.

I would be happy to talk in more detail.

About MeI am a Master Student in Mechanical Engineering specializing in 3D CAD modeling, FEA, Engineering Analysis, Concentrate on strong heat transfer skills on thermal system design, HVAC system design, internal combustion engine and heat exchanger design.

Objective: Seeking an entry-level position working as Mechanical Engineer within an organization that progresses dynamically and provides me an opportunity to enhance my skills and update my knowledge

Skills

• Solidworks, ProE, Arena, AutoCAD, MATLAB/Simulink, ANSYS

• specializing in 3D CAD modeling, FEA, Engineering Analysis,

• Concentrate on strong heat transfer skills on thermal system design, HVAC system design, internal combustion engine and heat exchanger design

Education and Qualifications

• August, 2014-May, 2016 Stevens Institute of Technology, Hoboken, NJ (Master of Engineering in Mechanical, GPA: 3.74)

• August, 2012-May, 2014Florida Institute of Technology, Melbourne, FL ( Bachelor of Science in Mechanical Engineering, GPA: 3.15)

Human Powered Water Disinfector

Project Title:-Human Powered Water Disinfector

Aim:-• To invent an easy-to-use and cost effective portable human powered water disinfector which can save millions people lived in third-

world country by offering them clean water, funded by New Life International.• 12 Watts is required for running the water purification cell.

Solution:-The Panther Purifying System has three main sub sections;

Mini Elliptical Custom Axial Generator Controller

Analysis:-The five most important parts of the elliptical were analyzed in ANSYS

Base

Max Deformation (mm) .01

Max Stress (MPa) 4.34

Safety Factor 15

Fatigue Life Cycle Max

Fatigue Safety Factor Max

Max Deformation (mm) .01


Safety Factor 15


Fatigue Safety Factor Max

Pedal Support

Beam

Roller Support

Max Deformation (mm) 0.01


Safety Factor Max


Fatigue Safety Factor 10.22

Pedal Crank Connection


Max Stress (MPa) 74

Safety Factor 3.77

Fatigue Life Cycle 10e6



Max Stress (MPa) 132

Safety Factor 2.1



Crank

Justification and Theoretical Calculations of custom axial generator:-

• Faraday’s Law

Controller:-In order to rectify the 3 phase AC output of the generator and to provide feedback to the user a custom controller was designed and constructed. Also, when the user operates the elliptical it would be very beneficial to know when he is done pedaling. To provide this, the team also developed a control box with user feedback.

The feedback box has four LEDs and four switches. The switches on the box are labeled 1 ppm, 2 ppm, 3 ppm, and 4 ppm. When starting to treat a water source, the user tests the water with the standard chlorine tester provided by New Life International and determines a starting ppm between 0 and 4. He then flips the corresponding switch letting the microcontroller inside the box know what the starting ppm is. The four LEDs are what the user uses to tell when he is done. The first LED will flash until the water supply has enough chlorine generated. The second LED will flash when the purifier has generated enough chlorine. The blue LED will flash when the resistance of the cell becomes too low and therefore makes it difficult for the user to pedal, so the user can change the resistance by adding water to NaOH cell. The yellow LED will flash when no switches are flipped. It is meant to act as a warning light to the user so he can flip a switch and the code can operate correctly.

NaOH Tube of Purifier

Test & Result

By taking into account all the different variables the team was able to find an ideal combination. The team concluded upon;

• Gear ratio of 8.625

• Air gap of 5 mm

• Purifier resistance of between 4 to 9 ohms.

It can be seen that our system hits the necessary 12 watts to power the purifier and to have it start working

With gear ratio of 8.625, the 300 RPM translates to 34.8 cycles per minute which is easily sustainable and outputs 30 watts.

Waste Heat powered CHP System

Project Title:-Waste Heat powered CHP System

Aim:-Designed a solar energy combined co-generation system for a factory with utilization of waste heat from the furnace to offset the

electrical load, HVAC cooling and heating load.

Solution:-• The cogeneration thermal system using

steam boiler and steam turbine and a

compound renewable energy source which

is solar energy.

• However the whole design concept was

simplified in order to make feasible

calculation.

Comparison:-

• A cogeneration system with gas turbine is preferred to use in large industrial factory because its large capacity, and the larger capacity the more efficient the system is, and as well as more expensive than steam turbine. Consider this case in every aspect, the steam turbine with solar energy is the optimum plan.

Calculation & Result

Description Symbol Value Unit

Expected indoor temperature Ti 18℃

Outdoor temperature(summer,max,cooling) To,s 38℃

Outdoor temperature(winter,min,heating) To,w -20℃

Air density when air temperature is 38℃ in summer ρa(t=38) 1.173 kg/m³

Air density when air temperature is -20℃ in winter ρa(t=-20) 1.298 kg/m³

Buildings' floor area A 3000㎡

Buildings' height h 6 m

Buildings' volume V 18000 m³

Ventilation time period t 0.5 hour per air change

Air volume flow rate Va' 36000 m³/hr

Mass flow rate(summer)(ventilation) ma's 42228 kg/hr

Mass flow rate(winter) ma'w 46728 kg/hr

Air specific heat capacity constant pressure Cp,a 1.004 kJ/kgK

Temperature range(summer) ΔTs 38℃

Temperature range(winter) ΔTw 20℃

Thermal energy flow rate q 1611082.66 kJ/hr

Refrigerator output power p 447.52 kW

Coefficiency of performance(summer,cooling) COP 1.5 -

Input work flow rate of refrigerator wi' 298.346667 kW

Facility peak cooling load Lc 317 kW

Facility peak heating load Lh 103 kW

Combined equipment load W 135 kW

Efficiency of waste heat(boiler) to heat exchanger(Q) ηhx 0.53333333 -

Efficiency of waste heat(boiler) to turbine(W) ηst 0.44444444 -

Efficiency of waste heat to boiler ηwb 0.9 -

Facility maximum usage Wmax 452 kW

Corresponding boiler input(electricity primary) Wop,1 1017 kW

HVAC maximum usage Qmax 298.346667 kW

Corresponding boiler input(HVAC primary) Wop,2 559.4 kW

Natrual gas lower heating value Hgas 35588 kJ/m³

Hgas 10 kWh/m³

Natrual gas volume per hour Vgas 101.7 m³/hr

Natrual gas complete combustion total energy(ideal) Qgas 1017 kW

Furnace outlet temperature tw 530℃

Furnace inlet temperature(preheated) tco 230℃

Efficiency of heat exchanger c ε 0.4 -

Combined flow rate mf 3 kg/s

Incoming furnace air temperature tci 30℃

Item Symbol Value Unit

Steam turbine power plant capacity 1000 kW

Heat rate hr 8500 Btu-th/kW-hr

Load factor LF 75%

Interest ie 8%

Inflation rate j 4%

Cost for constant Cc 600 $/kW

Operation period T 300 day/yr

4800 hr/yr

Construction time 4 yr

Plant life time 40 yr

Personnel to operate 30

Construction cost R 600000 $/qtr

Plant value at the end of const period A 11183571.2 $

40 years life value At 484218283 $

Quaterly cost S 1237199.2 $/qtr

Natrual gas price 0.00002335 $/Btu

Fuel cost FC 5.8153E-05 $/kW

Annual fuel cost AFC 209.349546 $/yr

Energy output Eq 900000 kWh/qtr

Capital cost 1.37466578 $/kW

Laber costs 2250000 $/yr

0.625 kWh

Total cost 1.99966578 $/kW

Electricity unit price 0.17 $/qtr

Income Inc 153000 $/qtr

Expenditure Exp 2399.59893 $/qtr

Return on investment ROI 150600.401 $/qtr

Cold Food Storage

Project Title:-

Cold Food Storage Design

Aim:-

Designed a 500 tons capacity direct expansion cold food storage to maintain or extend product life of meat and fruit at New Jersey.

• Reduce respiratory activity and degradation by enzymes;

• Reduce internal water loss and wilting;

• Slow or inhibit the growth of decay-producing microorganisms;

• Reduce the production of the natural ripening agent, ethylene.

Solution:-

• Selected the wall and roof with 2.75 overall thermal resistant by using PUR insulation, and the centerline mounted air supply duct with uniformly distributed 17 degrees upward outlet.

• Distributed the air supply uniformly in the storage room, and abled to preserve products months longer.

Storage Layout & Pipe Distribution

Calculation & Compressor Selection

Where:

𝑄1 = 𝑊𝑎𝑙𝑙 ℎ𝑒𝑎𝑡 𝑔𝑎𝑖𝑛 𝑙𝑜𝑎𝑑𝑄2 = 𝐻𝑒𝑎𝑡 𝑜𝑓 𝑡ℎ𝑒 𝑓𝑜𝑜𝑑, 𝑝𝑎𝑐𝑘𝑎𝑔𝑒, 𝑣𝑒ℎ𝑖𝑐𝑒𝑙, 𝑟𝑒𝑠𝑝𝑟𝑖𝑎𝑡𝑖𝑜𝑛𝑄3 = 𝑉𝑒𝑛𝑡𝑖𝑙𝑎𝑡𝑖𝑜𝑛 𝐿𝑜𝑎𝑑𝑄4 = 𝑀𝑜𝑡𝑜 𝑙𝑜𝑎𝑑𝑄5 = 𝑀𝑖𝑠𝑐𝑒𝑙𝑙𝑎𝑛𝑒𝑜𝑢𝑠 𝑙𝑜𝑎𝑑𝑛1 = 𝑠𝑒𝑎𝑠𝑜𝑛𝑎𝑙 𝑐𝑜𝑟𝑟𝑒𝑐𝑡𝑖𝑜𝑛 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡𝑛2 = 𝑇ℎ𝑒𝑟𝑚𝑎𝑙 𝑟𝑒𝑑𝑢𝑐𝑡𝑖𝑜𝑛 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡𝑛3 = 𝑉𝑒𝑛𝑡𝑖𝑙𝑎𝑡𝑖𝑜𝑛 𝑐𝑜𝑒𝑓𝑓𝑖𝑐𝑖𝑒𝑛𝑡

cool storage room cold storage room Freezing storage room

Documents

Xianwei Xia Portfolio