Mark Hawkins - General Formula for Beam Dimensions

In order to assist with the stress analysis and beam design, I have created this general formula to calculate the beam dimensions in relation to each other for different materials.

My calculations for current boom (corrected)

in my final page i forgot to intergrate the step function. however the value of the deflection is unaffected due to the fact that i copied these calculations from my original rough notes, and in those i did intergrate the step function correctly.

System Calculations

These are the calculations that have been worked out for the design we chose.

List of alloys that can be used for legs / boom is too thick!!! - Jarrett D

LEGS
we have estimated that the maximum amount of stress any part of the legs are exposed to is around 8mpa. Although our calculations need to be refined it is unlikely that this value will not be greatly affected. Therefore i have put together a list of aluminium alloys that can be used.

alloy....................... ...compression yield stregnth (mpa)
Aluminum 2014-O .................................................185
Aluminum 2014-T4; 2014-T451 ............................425

Aluminum 2014-T6; 2014-T651 ...........................470

Aluminum 2048-T851 Plate .................................420

Aluminum 2618-T61.............................................370

Aluminum 5086-H112 ..........................................270

Aluminum 5086-H116; 5086-H32 .......................290

Aluminum 5086-H34 ..........................................325

Aluminum 5086-O ..............................................160

Aluminum 7039-T61 ..........................................390

Aluminum 7039-T64 ..........................................410

Aluminum 7178-T6; 7178-T651 ........................530

Aluminum 7178-T76; 7178-T7651 ...................460

Aluminum 7475-T7351 ...................................380

Aluminum A206.0-T7 Casting Alloy ..............372

Aluminum 206.0-T7 Casting Alloy ................372

Aluminum 208.0-F, Sand Cast .....................105

Aluminum 242.0-T21, Sand Cast ..................125

Aluminum 242.0-T571, Permanent Mold Cast .235

Aluminum 242.0-T571, Sand Cast ....................235

Aluminum 242.0-T61, Permanent Mold Cast ....305

Aluminum 242.0-T77, Sand Cast .....................165

Aluminum 295.0-T4, Sand Cast ......................115

Aluminum 295.0-T6, Sand Cast .....................170

Aluminum 295.0-T62, Sand Cast ...................235

Aluminum 296.0-T4, Cast ...............................140

Aluminum 296.0-T6, Permanent Mold Cast .180

Aluminum 296.0-T7, Cast ..............................140

Aluminum 319.0-F, Permanent Mold Cast .....130

Aluminum 319.0-F, Sand Cast ........................130

Aluminum 319.0-T6, Sand Cast ......................170

Aluminum 336.0-T551, Permanent Mold Cast 193

Aluminum 336.0-T65, Permanent Mold Cast ...296

Aluminum 354.0-T61, Permanent Mold Cast ....250

Aluminum 355.0-T71, Permanent Mold Cast .....215

Aluminum 355.0-T71, Sand Cast ........................205

Aluminum 355.0-T51, Permanent Mold Cast ....165

Aluminum 355.0-T51, Sand Cast .......................165

Aluminum 355.0-T61, Cast ................................215

Aluminum 355.0-T62, Permanent Mold Cast .....275

Aluminum 355.0-T6, Permanent Mold Cast ........185

Aluminum 355.0-T6, Sand Cast ..........................180

STEEL WIRE
I have calculted that if we use steel wire with a thickness of 1cm to lift the objects, it will be exposed to a maximum tension of 124.9 mpa. Therefore a medium carbon steel should be used to create the wire as it typically has a tensile strength much higher than this.

mass estimation of the legs and boom
using the dimensions given on the cad drawings i calculated a rough estimate of the mass of the crane legs and boom.

legs
given that all of the aforementioned alloys have a density between 2800 - 2650 kg/m^3

mass of the crane foot extender= 3.69-3.50kg
'' '' crane foot = 1.76- 1.67kg
'' ''crane leg = 3.25-3.08kg
'' ''crane shoulder = 5.00 - 4.74kg

Boom
when estimating the boom i came across something very worrying. i will show my calculations so someone can spot a mistake if i have made one.

density of carbon steel = 7800kg/m^3

cross sectional area of boom = (0.05x0.06)+2(0.02x0.07)= 5.8x10^-3 m^2
volume of boom = 5.1 x 5.8x10^-3 = 0.02958 m^3
mass of boom = 7800 x 0.02958 = 230.724 kg

here you can see that the boom is very heavy, therefore i suggest we make it thinner or shorter unless my calculations are wrong.

all facts and figures were obtained from http://www.matweb.com/

Minutes of meeting 9 (25/03/2010)

All team members attended to discuss the situation for the following week.

Stress analysis is almost complete and based on the given values from the stress analyst, both the materials specialist and finance officer can begin selecting the most appropriate choices for the crane.

A meeting will be held on monday to put together the gathered data.

The following members have informed the group they will not be able to attend the meeting in person, but have provided alternative means of contact to recieve tasks and information of any made decisions:

Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst

Minutes of meeting 8 (23/03/2010)

Finalisation of the design idea and a group meeting to discuss the current state and carry on with the calculations of the stress analysis for the crane.
The latter was briefed and directed by the stress analyst for the general completion of this section.
Reviewes could be required at a later date to finalise all calculations in order to choose the materials and begin costing.

The following members attended:
Sandra Donohoe - Project Manager
Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst

Ideas for the crane design and safety - Sandra Donohoe

Source:
Strength of materials by Nicholas Willems, John T. Easley, Stanley T. Rolfe, New York ; London : McGraw-Hill, c1981.

Materials

The table from the listed source highlights typical properties of some materials commonly used in construction.

The materials which have the greatest probability in being used as part of the crane structure include: steels, high carbon steel, aluminium alloys.

Steels have the possibility to be used in areas where high strength is required (high Young’s Modulus and a high yield stress) e.g the glide beam (I beam design). However it can pose carrying issues for the workers over long and uneven ground, due to its high mass/weight density.

A design that could be looked into for the glide rail according to BS5950-1:2000 (structural use of steelwork in building - part 1: code of practice for design- rolled and welded sections), include the use of castellated beams of the following dimensions (stresses would need to be calculated however it can reduce the weight issues but would be more expensive than a standard I beam ):



On the other hand as the region is currently susceptible to aftershocks, collapse of infrastructures… rescuers will be working in potentially dangerous conditions, to avoid toppling over of the structure the extra weight (e.g. of the steel) could provide some stability if such events were to occur.

Aluminium alloys possess a low mass/weight density and a relatively high yield stress but also have noticeably lower E value (than steels) proving strength per weight and less brittleness than steel. Aluminium however has the disadvantage of being more costly than steels as it requires more specialised manufacturing and repair processes, however due to their chemical properties are generally more resistant to corrosion.

Once the rescues has been completed and most of the rubble removed, if there are no further uses for some of these cranes, having produced them using these types of materials would allow them to be recycled and be considered environmentally friendly.

Mark Hawkins - Second Design CAD Drawings

The following are the CAD drawings for the components of this second design. The first image is of this crane assembled, and the next ten are the individual components. The last sheet is an assembly sheet showing how the crane goes together.












The dimensions and angles described by these designs have been calculated by the stress analyst, though they are still awaiting materials analysis and corresponding approval from finance. Once these tasks have been completed, the materials information will be added to the drawings and any final alterations will be made.

Mark Hawkins - Second Design Revision

This revision of the design had two objectives, firstly was to simplify the joint on the leg design, and secondly to redesign the beam to the stress analyst's specifications.In all images the original design is to the left, and the revised design is to the right.

The ball joint in the leg was replaced with a much simpler structure in order that the manufacturing costs could be reduced. The image below depicts this change.



The next change was the beam. The stress analyst decided that the best beam design was an I beam as depicted below. The dimensions are no longer arbitrary for all designs, but as calculated by the stress analyst.



In order to fit this new beam to the structure, the shoulder and beam pins also required redesigning. The head of the shoulder was reshaped and the pins were lengthened as shown below.





The design is now complete, pending analysis by finance, and full engineering drawings will be posted here shortly.

Meeting 7 (22/03/2010)

All members were present for this meeting

In this meeting we discussed the current market prices and strengths/weaknesses of materials, and whether or not they should be used in the design. The stess analysist completed his analysis and handed the revised dimensions to the chief designer.

For the next meeting the designer will have completed the final CAD drawings and all materials will be priced.

We are on target to complete this project to date.

Abdi Elmi - Finance

Since we were quite fond on the idea of Aluminium alloys ive been searching the net for their industrial prices. I came across a real good website :
http://www.metalprices.com/FreeSite/metals/al/al.asp

It shows how much the current Aluminium alloys are sold in the stock market in a range of different currencies. It's got this Aluminium alloys calculator which lets you choose an alloy, showing it's prices per Kg or lb.
The alloy calculator link is :

http://www.metalprices.com/freesite/alloycalculator/AlloyPlus.aspx

A problem I stumbled across is that the alloys were all named using unique identity numbers, so it's hard to tell which alloy has what metal inside it. It's crucial for our stress analysis to find the yield stress and it's young modulus so we have to distinguish one alloy from the other. Here's a list of the alloys:

226(GBD - AlSi9Cu3)
319 , 319.1
356.1
535.2
A356.2 ,
A380 , A380.1 (LME Al Alloy)
A431.1
B390.1
D12S (JIS H2118-1976)

We need to research each alloy and compare their advantages and disadvantages to make it suitable for our crane build.

Gantt Chart -Sandra Donohoe

The chart implies that at present the group is on target.

Having an initial design in place and calculations currently carried out to determine the stresses the crane would need to endure, along with materials and cost research taking place throughout in order to assess the design and improve where necessary.

Further work would however be required to ensure deadlines and milestones are met as it is important to ensure the team does not fall behind schedule.

An important aspect includes the marked milestones beginning the 29Th March (presentation and crane report tasks), as these could fall behind schedule should the crane concept not finish in the assigned week. An action plan would be immediately imposed to asses the situation and the appropriate course of action to be taken.

Minutes of meeting 6 (19/03/10)

The entire group attended and discussed the current situation and the next course of action in order to maintain on course as given by the gantt chart.
The stress analysis will be reviewed on Monday, including materials and cost research.
Further research required from all team members and any outstanding research material will need to be posted.

Aluminium Alloys - Jarrett D

During our last meeting we decided that an aluminium alloy could be used to create the legs of the crane. So I have done some research and found that there are two main categories of alloys, Wrought and cast. We will be using a cast alloy as it is stronger. However, as there are thousands of variations of cast aluminium alloys, I thought it best to find out the upper and lower strength limits of most cast aluminium alloys rather than to find these values for a specific alloy.

Facts on aluminium alloys
Tensile strength = 320-550 mpa
Yield strength = 250-450 Mpa
Density = 2626-2790 kg/m3
Young’s modulus = 70-74 Gpa

Advantages
· Aluminium alloys have a high strength to weight ratio so using them would make the crane easier to carry.
· Has a low fatigue limits which isn’t a problem as it fits the criteria of our crane perfectly.
· Excellent corrosion resistance

Disadvantages
· Has a lower tensile strength than steel so if a metal pipe (ie. The tripod legs) is to built out of an aluminium alloy. The diameter of the pipe would have to be larger then a pipe made out of steel to be able to deal with the same amount of stress.
· Cost is higher then that of steel.

Sources:
R.E. Sanders, Technology Innovation in aluminium Products, The Journal of The Minerals, 53(2):21–25, 2001.
Metals reference book(5th edn, Butterworths 1976)

Research on materials for the main frame of the crane - Jarrett D

I have found three materials that have the ideal properties to cope with the stresses and strains of a cranes function. the first of which is :

Carbon steel
Carbon steels are steels which contain only carbon as its main alloying ingredient. The amount of carbon ranges from 0.05% to 2% of the steels total wieght. This is a very important factor as generally the more carbon within the steel, the higher its stregnth (tensile and yield) and hardeness, the lower its ductility and harder it becomes to weld. For this reason we should consider using a medium steel containing around 0.5% to 0.6% carbon as this amount balances ductility with stregnth. some facts on general mediums steels are below:

medium steel facts
density = 7850 kg/m^3
tensile stregnth = 520 Mpa
yield stregnth = 350 Mpa
young's modulus = 208 Gpa

Advantages
Carbon steel can be used on parts of the crane where the stresses aren't particularly high (such as the crank arm or perhaps one of the tripod legs) and could even be used to create some of the rivets. doing this would save alot of money on cost.
Disadvantages
Although carbon steel is fairly strong, as far as steel goes it is relatively weak. its low tensile strength means that creating an entire crane out of the stuff would make the end product very heavy. Also as the steel includes no other alloyiong ingredients so its corrosion resistance isnt the best either, which means it may have to be painted to protect it.

T1 (AKA A514)/ High speed steel
High speed steels are steels that contain other alloying elements apart from carbon. they typically contain between 0.05% to 0.025% carbon along with other elements depending on the properties the material is required to have. Carbon steels that are required to be highly weather resistant will include elements such as nickel, silicon and phosphurus. Carbon steels reqiuered to be strong will include elements such as copper, titanium anad vanadium. However one high speed steel in particular is ABSOLUTLY ESSENTIAL to the construction of cranes, which is known as T1.

properties of T1
density = 7800 kg/M^3
tensile stregnth = 700 - 895 Mpa
yield stregnth = 620 - 690 Mpa
young's modulus = 205 Gpa

Advantages

• T1 has a high tensile stregnth therefore less material would have to be used as aposed to carbon steel, which would save weight. because of this fact T1 should be used on high stress components such as the boom, rivets and steel wire
• very good corrosion resistance when compared with carbon steels
• easliy welded and fairly ductile

Disadvantages

• Generally costs more than carbon steel

Titanium Alloys (grade 5)
Titanium alloys are split into 39 grades the most commonly used grade being grade 5, generally the higher the grade the better the alloy. Typically titanium alloys are used because of there extremely high strength to weight ratio however, they are also very hard which makes them great for creating cogs and gears with.

Grade 5 properties
Density = 4500kg/m^3
Tensile strength = 1000 Mpa
Yield strength = 880 Mpa
Young’s Modulus = 110 Gpa

Advantages

• 
  As the titanium alloys have a low density and high tensile and yield strength using this material would save a lot of weight.
• 
  High hardness which makes it ideal for moving parts where metal on metal friction occurs (pulley).
• 
  Alloys tend to include elements such as silicon, phosphorus etc which make the very corrosion resistant

Disadvantages
· Poor shear strength means this material cannot be used to make the rivets or screws
· Very expensive

sources:
metals references book 5th edn Butterworths, 1976
A.M. Howatson, P.G. Lund and J.D. Todd, "Engineering Tables and Data" p41
http://www.matbase.com/material/ferrous-metals/low-temperature-steel/a514-a/properties
http://asm.matweb.com/search/SpecificMaterial.asp?bassnum=MTP641http://www.efunda.com/materials/alloys/carbon_steels/show_carbon.cfm?ID=AISI_1040&prop=uts&Page_Title=Carbon%20Steel%20AISI%2010xx

Mark Hawkins - Revision of Crane Feet Design

Whilst in discussion with other group members, improvements to the design of the feet of the crane were purposed. The original design, featured to the left of the image below, required the area of ground immediately beneath them to be level. It is highly unlikely that level ground could be located in an earthquake disaster zone and thus the feet were redesigned, as featured to the right of the image below, and were fitted with rounded rubber (or similar) stoppers at their base.

This new design allows the crane to be placed in a greater variety of locations and increases the ease at which the crane may be assembled, as the symmetry of the new feet mean that they do not require orientating. The image below shows a close up of the new design integrated into the crane structure.

Finally, below is the revised crane structure in its entirety. This design will require farther design alterations, and the next purposed change will be to replace the main solid square beam with an "I" beam. This will increase strength whilst decreasing overal weight. The altered design incorporating this change will be produced, along with any other recomended changes, once the stress analysis has been completed.

Mark Hawkins - First CAD Engineering Drawings

Here are copies of the CAD engineering drawings produced for analysis by the stress analysist. All angles and dimensions are approximate, and subject to change upon the findings of the analysis.

Minutes of meeting 5 (17th March 2010)

The following group members attended:

Sandra Donohoe - Project Manager
Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst
Abdi Elmi - Finance Officer

Calculations where discussed and some required changes to the design would be required (e.g. main glide rail would possibly need to take an I beam shape in order to support the stresses imposed and further research on finance and materials)

Minutes of meeting 4 (15th March 2010)

The following group members came to the meeting on the given day to discuss the design status and allocate tasks for the next stage of the project, the stress analysis:

Sandra Donohoe - Project Manager
Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst
Abdi Elmi - Finance Officer

Mark Hawkins - Initial Design

The original design was created on CAD software (Solidworks 2010) as depicted to the left. This initial design, which was based on group discussion, unfortunately has a major flaw. The tripod legs cross at its base; which could only be fixed by either lowering the height of the feet in relation to the leg length, or by changing the angle of the tripod. Neither of these options would be practical as they would both comprise the structure of the crane.

Another problem with this design was size. This crane would be both heavy and complicated to assemble in a hurry. Therefore the design was revised, as shown to the left, to a simpler form.

This design would be much easier to assemble and transport, due to the much simpler design. The each leg structure may be disassembled into short component pieces, but once assembled may be carried across rough terrain as a single piece. The main difference in these designs is shown below, changes to the shoulder section and central leg section mean that this crane is supported by a single tripod on either side.

These changes greatly improve the design and at this stage, rough CAD drawings were created and handed to the stress analyst. All of the dimensions and angles depicted in these drawings are approximate, until the stress analyst has completed his task. The design is likely to be changed considerably to accommodated his recommendations.

Meeting 3 (10/03/2010)

Once more the following group members are consistently present at these group meetings:
Sandra Donohoe - Project Manager
Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst
Abdi Elmi - Finance Officer
The design status was assessed as a result of the new information and an initial sketch was made:


Further research and analysis will be carried out to evaluate its potential

Specifications for the design- Sandra Donohoe

The following brief is based on information provided by Mr Thomson and will be brought up in the following meeting to decide on any new requirements to the design:

• Designed to have a minimum lifting load of 1000kg, the final value will depend on the tasks the crane is going to perform.

• The load material has no specific dimension/size limitations, therefore loads will be concrete blocks and structure beams of a selected range.

• Transport the load a minimum of 4m from the point of lift i.e. from 1 “end” of the beam to the other. As a result the glide rail would require a minimum range of 5.50 m to 6.00 m to compensate for support beam positioning and load dimensions.

• Needs to be rapidly disassembled and reassembled on site

• Some problems caused by uneven terrain can be tackled in two ways: with height varying support frames (which would have an impact on cost) or have “packing material” transported in a trailer (such as wood) to be placed under the frames and balance the structure (time would be impacted).

• The individual parts of the crane are to be carried manually over 100m of rough ground by 4 people and require as few trips back to the vehicle for the components

• Transported using a standard Land Rover size 4x4 or small helicopters

• Powered by either a hand-cranked or powered winch

• The crane is to have an expected lifespan which lasts the duration of the catastrophe and may be put out of service once this task has been completed. Consequently the material selected would need to be strong, resistant to forms of weathering/corrosion…, affordable price, can consider recycling of frames material.

Abdi Elmi - Initial Crane and Finance research

Crane Research

Through net research ive found quite a few portable cranes that are manufactured and mass produced by companies such as : Abus Cranes , Spanco Inc, Contrx Cranes etc.
The most ideal crane most of these companies supply is the Jib crane:From our first few meetings we've identified flaws to this design in out particular situation (such as the platform and the mobility) and we're planning to go for quite a different design.

Finance

Ive done some research on manufacturing finance (via previous lecture notes). Some equations essential to finding the manufacturing cost of the crane parts is shown below :
Manufacturing Cost(Mi) = Material Cost(Mc) +( Processing Cost(Pc) * Cost Coefficient(Rc))
[Mi=Mc+(Pc.Rc)]

Material Cost(Mc) = Total volume of material to produced part(v) * Cost of material per unit volume (cmt)
[Mc=V.Cmt]

The material we discussed so far in using is an Aluminium alloy, but that ofcourse is subject to change.
Manufacturing costs will alter depending on the method of manufacturing and the individual shape complexity, but that will be something we will discuss in the near future.

Mark Hawkins - Design Inspiration

The main focus of this initial research phase was to consider preexisting portable crane designs, and assess their pro and con. This should allow better understanding of crane design for future design phases.

The first style of crane that I considered was a gantry style crane. The example to the left shows a "Hasemer and Feltes Aluminium Gantry Crane" which seems to meet most of the project brief criteria.

The main issues with this particular style of crane is firstly that on the loose and uneven post earthquake ground, the struts may not be adjustable enough to keep the winch guide stable and horizontal.

Also, in order for this crane to move debris a minimum of 4 metres from any point of lift, the winch guide beam would have to be 8 metres long. This would cause the whole structure to become very unstable in the likely event of aftershocks. For more information on this preexisting design please visit http://www.ghequipment.com.au/products/cranes/portcranes.htmcranes/portcranes.htm

The next type of crane considered were overhead cranes, as depicted to the right. This type of crane has several advantages over the gantry style crane as its much wider base would make it far more resilient to aftershocks. This design could also be fitted with adjustable legs to allow it to be positioned on uneven surfaces.

The main disadvantage of this crane is that it would have to be 8 metres square to meet the required design criteria. This would make such a crane very difficult to transport by hand over rough terrain, and would not fit inside the back of a standard 4x4 vehicle. For more information on this crane, please see

http://www.low-cost-cranes.com/jib-cranes-350.html

The final style crane that I researched was the portable jib crane as shown to the left and right. The main advantage of this style of crane is that it is rotary and thus may move an object through 180 degrees. This means that the length of the crane arm is minimised, as is the overall size of the crane. However, the main disadvantages of this crane are that in order to remain stable; the base either needs to be significantly counterbalanced with a heavy weight, or the legs need to spread across the ground meaning it can only be placed on a flat surface. Details of the particular crane depicted here can be found at http://apexlifting.tradeindia.com/Exporters_Suppliers/Exporter18134.292868/PORTABLE-JIB-CRANE.html

This research has shown the three main types of crane that I believe would be appropriate to meet the design brief. Each of these preexisting designs has advantages and disadvantages, so the next step is to use the basic principles discovered here in crane design; and create a new, unique, and innovative alternative to be used in earthquake disaster relief operations.

Sandra Donohoe - Initial concept

The main objective for this section was to draw inspiration for a new design by studying the current market.



If these models were to be considered as the foundation for the principal design, certain factors would need further investigation, including:

• Non-collapsible side frames.

• Design a product where the glide rail has a minimum internal width of 4m.

• Weight and height of each part/piece (dependent on material) as they would need to be carried quickly over 100m to the site.

• Aluminium alloy could be used for certain sections due to its high strength to weight ratio (one of the examples given contained a combined total weight of 100kg).

• Material used for cables and ropes (i.e. stainless steel).

• Each piece needs to have restricted dimension sizes in order to be transported by a 4x4 vehicle (some models can quickly fold into 7 pieces).

• Assembly needs to support a minimum load of 1000kg.

• Powered winch can be used to rapidly lift the load.

• Pin type connections could be used as they require no spanners or wrenches or other hand tools, this reduces weight and may increase speed of assembly.

• No need for a counter balance/ anchoring as required by models such as the jib crane.

• Wheels would not be considered due to the type of terrain the crane would be required to operate on (often not plane or rubble).

• Adjustable leg stands could allow the height of the gantry crane to be altered depending on how uneven the terrain is found to be (fitting a spirit level into the model can assist in assuring balance of the glide rail is achieved before the load is lifted).

www.ghequipment.com.au/products/cranes/portcranes.htm
www.aluminiumcraneco.com/portable-gantries-gantry-crane.htm

Jason Harries - Initial Design

My train of thought was based on the idea of simplicity and for that reason I researched into the history of cranes and got some ideas from the Ancient Romans.

Pentospastos

This was a simple crane design that used a simple triangular frame and a block containing three pulleys which is attached to a manual winch. With this formation it could could lift over 1000kg.

The general design is simple and depending on the material used it could withstand the forces required of it.

However the design will not allow it move the load too far, so the design must be altered if it is to fullfill the required result.

Also places to peg the support cables may be hard to find in a disaster scenario.

Polyspastos

This is a crane of simlair design to the Pentospastos but on a larger scale. This one has multiple lines coming from the winch to pulley block which gives it the ability to lift more weight.

This design has the same flaws as the first one, and to lift the larger force either a large human force would be needed or a mechanical force would be needed to turn the winch.

The designs do not completely full fill the required specification but the idea can be modified so that it can perform as needed.

Meeting 2 (08/03/2010)

The register was taken and the same people from Meeting 1 were present.

Firstly discussed researched ideas that each group member looked at over the weekend.

Some ideas had some obvious flaws which may need to be remedied.

The group debated on the interpretation of the design brief and will take this up with Mr Thomson.

Meeting 1 (05/03/2010)

Meeting was had on recorded date and what was discussed was:
- Contact details between group members
- Setting up of blog
- Job allocations
- Minutes

The contact details were distributed between the members that attended, Jarrett Doherty was not present. As you can see the blog has been created so all of the members can access and contribute to it.

The Jobs were allocated as listed:

Sandra Donohoe - Project Manager
Mark Hawkins - Chief Designer
Jason Harries - Stress Analyst
Abdirahman Elmi - Finance Officer

The materials specialist has not been allocated due to the fact that Jarrett Doherty was not here, so therefore the job will be split between the current four unless a new member arises.

Chief Designer presented 5 sketches with initial ideas.

Project Manager has created a timetable so a record of meetings can be kept.

For the next meeting each member needs to research the current market.