Further development and evaluation

Further development and brief tender evaluation

The product I believe is a good prototype design. Obviously rigorous testing and a thorough evaluation have to be done if the product was actually manufactured.

During the presentation the product was under heavy scrutiny, one of the main problems identified was the lack of structural support in the legs. The crane would be unstable without these two extra bars for support. Below is a diagram and an interesting common fixing mechanism for the bar to leg connection.

The estimated total cost of the initial model in production to cost £1000 (labour included).

I encourage more constructive criticism from our competitors.

Thankyou, Good work Group. : )

Godbless All

Final Conclusions:

Following discussion and observation of the other presentations, the following points were brought forth for future consideration when conducting a similar project.

- Much of the research, analysis and development of our design provided a sound basis for our tender proposal.
- However, following our presentation of the proposal it was evident that certain elements had not been fully developed.

• Our costings did not take labour, production and profit margins into account, and as a  result were incomplete leading to a misleading quote for the price of our crane.
•  In retrospect the crane, although fulfilling the brief, could have been more ingenious in solution, unfortunatly the analysis of some of the more complex designs initially left us confused, and contained many mistakes, so the simplest option was seen as the most logical choice as it could be pursued to its full potential. 

-  On a positive note, the group did work well together, the group members worked to their strengths with romi and andy focussing on the basic design and stress analysis elements of the process, allowing the other group members to complete separate tasks such as further research to assist the analyses and solve problems encountered as we went along.
- The schedule was kept on top of with regular meetings, and individual taskings, ensuring that the project at no point fell behind its originally planned timescale.

A. Compton.
J. Collins.

Conclusion

The actual crane design was good but the beams that were going to be used did not have standard dimensions. This made it difficult to get an accurate costing of the beams and would have meant a factory would not have been needed to manufacture the customised beam designs. The use of actuators for the sidebars would help the crossbar to move horizontally but not much tought was given as to how they were going to be fixed to the beams. Overall the basic design of the crane was good but there was not enogh time to think about the more detailed parts of the crane such as the pins and screws.

Group Presentation:

New Crossbar Design

The new crossbar has a triangular face with a base of 125mm and a height of 90mm

nb. it should be 5mm thick

Minutes: 27/04/2010

Tasks achieved:
Stress Analysis completed for final design. (R. Dhillon & A. Daniels)
CAD Modelling of Crane complete, engineering drawings, animations and rendered images were also produced for insertion into the presentation. (J. Collins)
Tender Presentation almost complete, awaiting financial analysis, tasked to A. Dhillon, other constituent parts have all been given to A. Compton for compilation. (A. Compton)


Tasks identified:
Final Presentation Group Rehearsal
Conclusions/Final Analysis of project from group members?

Attendees:

J. Collins
A. Daniels
A. Compton
R. Dhillon

Future Meetings:
Final tender presentation - 10am - Rm 568

CAD

Close up of the end of the crane, showing detail of position of pins, beam end caps and telescopic legs.



Crane with legs collapsed



Crane with legs extended



Short video showing an animation of the components of the crane being exploded.

New Leg Design

During the stress analysis we didn't realise how thin the walls were in the crane legs at just 1mm so a new design was made. The walls are now 10mm thick so during the new stress analysis a larger second moment of area was calculated.

I = 1.0479e-6 m^4
P(critical) = 55,862N
mass = 7.53kg

Crossbar Calculations

The crossbar was designed to be hollow instead of solid so the same equations were used in the stress analysis but a different second moment of area was used.

Crossbar ( initial )

The crossbar which was initially designed was similar to andy's , however, andy's design was picked as we developed it to suite the needs of the rest of the crane. Even so, the stress analysis which was initially done for the crossbar is given below.

Basic sketch for the crane design .

After all the stress analysis was done, a basic sketch was done of the design to see what it would look like after the open top legs and the 1.7m legs were decided. The CAD which will be done will show the dimensions to a greater degree of accuracy, however, this basic sketch allows the CAD to be formulated. Below is the sketch.

Calulations for the crossbars

The original idea which was posted up by romi was constructive , however, a sample of calculations for the crossbar have been given below . It was important to make sure the stresses were correct on the crossbar as it has a lot of loading. Below are a sample of calculations.

Calculations for the sidebars

The sidebars took quite some time to do as they were an important part of the structure , hence everything had to be moulded around the dimensions for the sidebars. Below are examples of the sidebars being calculated with a second image showing a more realistic result when doing

the calculations .

The bar was concluded as being 300 mm in depth and 50 mm wide.

initial calculations for the legs

When working out the level at which the legs will buckle at in accordance with the amount of stress induced, a force of 250 g is applied from top . Basic stress analysis was required for the legs. Eulers equations were used to determine buckling. A sample of calculations can be seen below.

Calulations for End bars

The end bars are the two bars at the back of the crane whilst the side sidebars are the bars running along the side of the beam Calculations needed to be made for the end bars so that they could fit inside the top part of the legs, and appropriate dimensions were calculated obtaining a suitable weight . The end bars were circular rather than rectangular like the rest of the bars. The calculations are shown below.



The calculations were fairly straight forward and simple , however, the only hardship was to get the right dimensions in accordance to the other bars in the crane.

Tender Proposal: Leg & endbar calculations

Leg

• Aluminium
• E = 70 E9 N/m ^2
• Stress = 40,000,000 N/m^2
• Stress (crane ) = P= ((Pie ^2) *E*I) / 4L ^2 = 8659 N ( Max load = 2453N)
• b = 15 mm
• d= 52 mm
• I = 1.4489e-7m^4
• 5 mm thick
• Volume = 9.69 e-4 m ^3 ( minus the cut away = 5.94e-4 m^3)
• Density = 2690 kg / m^3
• Mass = 2.61 kg

Endbar

• Aluminium
• E = 70 e 9 N / m^2
• stress = 40,000,000 N/ m^2
• Stress ( crane) = 6,688,013 N/m^2
• diameter = 50 mm
• I = 2.6704 e-7 m^4
• 10 mm thick
• Density = 2690 kg / m ^ 3
• Mass = 20 .282 kg
• Volume = 7.5398 e-3 m ^3

Tender Proposal - crossbar calculations

Crossbar

• mild steel
• E = 200x10^9 N/m^2
• σ yield = 220 MN/m^2
• σ = 71,038,835 N/m^2
• b = 40 mm
• d = 120 mm
• I = 2.4325x10^-6 m^4
• 5mm thick
• volume = 0.0018750 m^3
• density = 7825 kg/m^3
• mass = 14.672 kg

Sidebar

• aluminium
• E = 70x10^9 N/m^2
• σ yield = 40 MN/m^2
• σ = 10,006,703 N/m^2
• b = 50 mm
• d = 500 mm
• I = 1.2867x10^-4 m^4
• 5 mm thick
• volume 0.0054 m^3
• density = 2690 kg/m^3
• mass = 14.526 kg

Minutes: 22/04/2010

Tasks followed up:
Stress analysis for crane complete.
CAD drawings for crane in progress.

Tasks for next Meeting:
Presentation Finalisation
Presentation Rehearsal


Future Meetings:
Monday 26th Apr.

Attendees:
A. Compton
A. Daniels
R. Dhillon

Runner for Crossbar

This is a website for the runner that the crossbar will use to move in the horizontal direction.

http://www.hepcomotion.com/en/psd-screw-driven-linear-actuator-pg-14-get-24

Stress calculations for alluminium sliding beam

It would have been great to 'get the hopper' or just 'get that hopper in' , however, it seems as though destiny does not want it to be dear team mates . After doing some calculations for stress , the grasshopper design has some problems, hence why me and andy have decided that it would be a lot less problematic to do the second design we came up with as it fits the specification ; does its job and is a lot more simple to calculate the stresses and strain on the struts.



Moving on to the important stuff now, lets recall the second design which had 4 struts as legs with a sliding bar in the middle to move the load in the x direction. Calculations below have been done for this bar which will lift the load . Calculations for other struts ( e.g the legs) will be done during the course of this week. For the sliding strut, different combinations of length , materials ( steel or alluminium) , etc have been taken into consideration when doing the calculations. I have pointed these points out below. The first set of calculations were done to these specifications :

• material: alluminium




• length : 1.25m




• deflection : 1mm or 0.001
  
  


• weight of beam : 1020 g ( 1000kg of load plus 20 kg for winch ) = 10006.2 N
  

The calculations are below.

By using the formula y ( deflection) = wl cubed divided by 48 EY i could work out the second moment of area . This allowed me to work out the dimensions of the beam . The weight of the beam would be 18.71 kg and the level of stress the beam would withstand with such loading at a 1mm deflection would be 32.21 MN/m2. However, in reality, the properties of alluminium do indicate that alluminium is not as stiff as some other metals although it has good tensile strength. In reality, under such loading, alluminium would not deflect by 1mm and would rather deflect by up to 5 mm hence i did another set of calculations with the deflection value set at 4mm but with every other value as the same. What i wanted to gain from doing this was to see how much extra stress the beam would have to take if there was more deflection. Below are the calculations :

















































By changing the level of deflection of the beam to a more realistic estimate, the level of stress went up to 81.7 MN/m2 from 32.21 MN/m2. This shows that the level of deflection has a positive correlation with the amount of stress being applied to the beam . Also the yield stress of alluminium is 100 mPA . This shows that the alluminium strut at a deflection of 4 mm would be nearing the yield stress . In reality deflection could be even more than 4mm which is why the sliding beam should NOT be made out of alluminium. In the next post, the same calculations have been made for steel to see if it is more suitable for the sliding beam .

Minutes: 25/03/2010

Tasks followed up:

Company name: Crane-tacular solutions!

Calculations for grass-hopper design are in progress, getting close to a solution during meeting.
Winch preferances and weights established.
Preferred materials identified.

nb. density of steel 7800 kg/m^3
density of aluminium 2700 kg/m^3

Tasks for next meeting:

CAD analysis and drawings etc.
Finalised calculations
Costings for crane parts
Write proposed presentation for development with group at next meeting

Future meetings:

Monday 19/04/2010 - 10am Guild loft.

Attendees:

A. Compton
J. Collins
A. Daniels

R. Dhillon - Apologies given.

Boom fixings and real mini crane pictures

This post will explore a few methods of fixings and boom development from original sources. The bulldog crane now named 'The Grasshopper' as of now, has to be marketable and innovative. I personally believe that idea number 3 looks like a grasshopper.

Slogans such as "Get the Hopper" and "I need help, I need The Grasshopper" are catchy and have a history of adding lasting appeal to a product and gives it a separate identity, a sort of quirky uniqueness.

fig.1

Above (fig.1) is a picture of a green grasshopper for visual aid. (Idea 3 will be shown at a later date.)

Now moving on to more serious matters...

Below is a crane, it uses a 'cradle' to move the object picked up in the x-direction. The object is picked up using chains and hooks, once secure it is elavated to the desired position.

fig.2

This is an excellent model for us to work from. We can use a inverted T beam for the boom itself. An 'I 'beam will work also but will add unnecessary weight, we will try to avoid it unless the stress calculations require the boom to have extra strength. Remebering idea 3 is supported from both ends and is not wall mounted as this one is therefore should be able to hold considerably more than 500kg.

fig.3

Figure 4. shows how the wheels that allow the cradle to move along the boom are fixed. The wheels are on both sides of the boom. They are fixed in place using a bracket that stops them from moving in unwanted directions or falling off. The wheels can be replaced and the entire cradle removed by unscrewing the bolts. This makes it a separate component from the boom, making it easier to transport.
fig. 4

Talking about portability, the boom will roughly be 4m+ so carrying this around either by man or machine power (landrover defender) is dfficult. So a 'hinge' is in order, and I have one that may suite our needs...wala!

fig.5

We can develop and modify this one to suite our needs. OR the two parts of the boom can be separate but connected with bolts.

Heavy duty materials must be used and an accurate stress test is required to determine most of the positioning of the components and type of fixing required.

This post is designed to develop idea no.3 though a considerable amount of the post can be used for idea no.2 also.

These photos are property of Amardeep Singh Dhillon and can only be used with permission from the owner, me.

Types of electric winch:

Winch example (1)

Found: http://www.liftingonline.com.au/products/JDN603

1000KG X 3M, JDN 'MINI' AIR HOIST

Specifications: (Extensive specifications given in a table on the link above)

"1000KG X 3M, JDN 'MINI' AIR HOIST *Extremely compact at a minimum of weight *High flexibility for varying working places *Few components for easiest operation and maintenance *Ideal as an inexpensive alternative compared to hoists with other driving media *Suitable for lube free operation, no additional oiler required *Suitable for application in hazardous areas *suitable for horizontal pulling *Newly developed braking system with little wear."
Weight: 26.0 Kg


Winch example (2)

Found: http://www.portablewinch.com/en/02.asp

• Portable

There is no fixed link to a vehicle; therefore you can take the winch anywhere. Tether it to any solid object: a tree, a post, a rock or even to the ball hitch of your vehicle.

• Powerful - Up to 2000 kg (4400 lb) of pulling power

The Portable Winch^TM will pull 1000 kg (2200 lb) single line. If you need to pull extremely heavy loads, we offer a snatch block kit including a swing-side pulley and locking steel carabiner. The pulley is attached to the load with the carabiner, and the rope is attached to the winch anchor. This lightweight system effectively doubles the pulling power of the winch to an amazing 2000 kg (4400 lb) pulling capacity!

• Lightweight - Weighs only 16 kg (35 lb)

Both winches have differing merits, the second example is most likely to be the one our group will use during our calculations as it is portable, and could be carried by hand, it will not add significantly to our overall payload, and could be modified to enable it to take a greater weight.


Alternative websites also viewed:

http://www.northerntooluk.com/winches-and-hoists/electric-hoists/?sortby=priceascending&cm_ven=Performics&cm_cat=PPC&cm_pla=Google&cm_ite=electric%20chain%20hoist

http://www.winchsolutions.co.uk/

http://www.nextag.com/Master-Lock-Co-2953AT-506261517/prices-html?nxtg=26900a1c0512-35D7477F7F5880CA

http://www.nextag.com/portable-winch/compare-html

Minutes: 22/03/10

Tasks followed up:

Materials, winches and bearings suitable for the task were suggested (posted to blog and details also brought to meeting) along with their tolerances and specifications.

Calculations for the design chosen last meeting were attempted and it was established by most group members at the weekend that this design, although probably effective, was too complicated for us to successfully analyse.

As a consequence Designs (1), (2), and (3) were proliferated and given a basic analysis. Designs (2) and (3) were chosen by the group in the meeting.

Tasks for next meeting:

Finalise calculations for designs (2) and (3) to enable a choice of options for final proposal - for thursday.

Think of options for linking parts together - Pinning, slot parts?

Begin materials costings. (Aluminium for legs, steel for boom? - more durable? weight reduction?) (nb. Land-rover payload max 1500kg, tow 3000kg.)

Find weight of electric winches and post examples.

Future meetings:

Thur 25/03


Attendees of todays meeting:
A. Compton
J. Collins
A. Daniels
R. Dhillon
A. Dhillon

Types of Bearing

When considering bearings, the main factor to consider is the type of load required for the bearing to withstand, the two main types are radial and thrust.


For use in the turning mechanism of the crane, a large thrust load and very small radial load will be applied to the bearing.

Plain Bearing


This is the most simple type of bearing, which simply consists of two surfaces that move past each other with no other mechanism. Often one or both of the surfaces is coated in a non-stick layer as well as being lubricated to further reduce the friction. This type of bearing has a very high load carrying capacity but also creates a lot of friction. They have a fairly high radial and relatively low thrust capacity.


Ball Bearing


Ball bearings have both a high radial and thrust capacity, and are found in a large range of applications where the load is small. Any load applied is focused onto a very small area, which makes it run smoothly and quietly, however this creates high internal pressures which may deform the balls should the bearing be overloaded.


Roller Bearing


Roller bearings are similar to ball bearings in the way they are made, having the key difference that they contain cylindrical rollers instead of balls. The rollers distribute the internal forces over a larger area, which reduces the internal pressure, making the components less likely to deform and vastly increasing the radial load capacity. Although the radial load performance is increased, this type of bearing has a very low thrust load capacity comparatively.


Magnetic Bearing


Magnetic bearings are ideal for high speed applications as they support the load using magnetic levitation which has zero friction and requires no maintenance. These bearings require a constant power supply as well as a sensor circuit to keep the inner and outer rings at a constant distance. This means that often a set of backup bearings is required in the event that a power loss to the device occurs. They have a relatively low radial load and extremely low thrust load capacity, and are most suited to continuous low load applications such as power generation or machine tooling.


Ball/Roller Thrust Bearing


This type of bearing is similar to ball and roller bearings in the way which they work, however the layout of the components allows a far greater thrust load capacity. This type of bearing is well suited to high thrust load applications, where radial load requirements are low. Rollers have the benefit of increased total load capacity, while ball bearings are smoother and run a lot more quietly as a result of decreased friction.

Original Design (from meeting 18/03/10)

Initial Design


After discussing each of our initial designs as a group, we came to the conclusion that the best type of crane to meet the specification would be a luffing crane with a counterbalance. A basic schematic of the layout was drawn in order to give a sense of the proportions and scale of the design.

With a 2.6 metre boom at 40 degrees to the horizontal, the total reach of the crane would be 2 metres about the centre of its rotational axis. This allows for an object to be lifted and moved a total of 4 metres from its initial point of pick up. Using a large base, and keeping the main body of the crane fairly low to the ground will lower its centre of gravity and increase stability.


Developed Initial Design #1


The initial design was then developed to include a cable spanning from the counterbalance to the tip of the boom, as well as a support up from the main body. The rotational axis of the crane was moved back slightly on the base to increase stability, thus reducing the required weight of the counterbalance.

It was also decided that a the crane could be rotated via a handle situated on the counterbalance, and also that a hand powered crank would be situated here to operate the winch.

Legs Of The Crane

After doing some research , I concluded that alluminium alloy would best suit the legs of the crane. There are two types, wrought and cast. Cast alluminium alloys are stronger but there are many types. On overage the properties are given below:

Yield strength = 250-450 Mpa
Density = 2600- 2790 kg/m3
Youngs Modulas = 70 - 74 Gpa
Tensile Strength = 300- 550 Mpa

Disadvantages of Alluminium Alloys

Alluminium has a lower tensile strength than steel hence the diameter of the pipe have to be greater in dimension than that of a steel pipe to deal with the same amount of stress.

Alluminium costs more than steel .

Adavantages of Alluminium Alloys

Has a high strength to weight ratio making the crane easier to carry .

It is immune to corrosion unlike iron or even steel to certain extents.

21/03 - Design 3

Design 3 ( The British Bulldog )



This design is a mixture of design 1 and 2 . It is interesting as it is something totally different to what is out in the market. It consists of a boom with supersonic legs and has the load sliding down the boom . The reason why we called it the british bulldog is because the front 2 legs are higher than the back two and the overall design looks like the shape of a dog. This also has marketability.

Advantages

As the struts or legs give more balance to the boom there may not be such a need for a counterweight.

The crane has a sliding system which is quite simple as there is no need for bearings.

The legs can be adjusted causing the boom to change in angle which can reach loads which are higher up with greater ease .

It can be de-constructed within seconds. The legs can be detached and the boom can retract into 2 causing very little space to be used up within the 4 x 4 rover .

bending moment and stress calculations would not be too complex .

Disadvantages

As the load is sliding down the boom, it may hit the ground before the intended point. It is important that the load is kept close to the crane or enough clearence is givin at the bottom.

There is no rotation which can lead to a bit of restriction.

21/03 - Design 2

Design 2





This design has a different approach all together to design 1 and some may consider it to be more 'simple' . It consists of 4 main legs which will be adjustable with 2 rollers on the upper struts which will roll backwards and forwards in the x direction. There will be 2 winches, one to move the rollers in the x direction and one to move the pulley ( load ) in the y -direction. Andy is working on a sliding system for this design.

Advantages

The bending moments and stress analysis is simple to work out.

The legs are adjustable allowing them to reach places which are not each to get to .

There are no bearings involved which means there is less chance of failure within the crane .

No counterweights are needed for steadyness as the crane will be steady.

Disadvantages

Motion is limited. The load can only be transorted in a linear direction rather than at an angle as there are not bearings for rotation.

The cable can get caught with the winch.

As some legs would be shorter than others in certain situations, there can be a danger of tipping or the load sliding down at a faster speed.

21/03 - Design 1 (simplified from original)

Design 1

This is a simplified version of the original design. The design consists of a hand winch placed above the trunk and has a counterweight to allow steadyness within the crane.

The advantages and disadvantages of this design are stated below.

Advantages

Bearings will allow the crane to rotate , therefore there is greater accessibility for different angles.

The base is steady with four adjustable ( anglular adjustment ) legs.

The base does not take up much space and can access areas which are difficult.

Disadvantages

The bending moments and stress analysis will more complex .

The crane would suffer from the possibility of tipping over.

Bearings make the system more complex.

Beam Dimensions

This is a website for the standard dimensions of I-beams, rectangular hollow section beams flanges etc.

http://www.roymech.co.uk/Useful_Tables/Sections/steel_section_index.htm#tables

Hand Winches

Gear Ratio

One person can't lift 1000kg using a hand winch without a gear ratio of at least 14:1 so that to the person using the winch it would feel like lifting 71.4kg. This is because the amount that an average man man weighs is 60-70kg and the maximum most people can lift is their own body weight.

Maximum Capacity

The winch needed for this design would have to have a maximum capacity of 1000kg or 2200lbs.

Weight

The winch needs to be a suitable weight so that it can be transported manually from the 4x4 vehicle to the disaster area.

Brakes

As the maximum load to be lifted will be 1000kg the winch needs to have a brake so that the person using the winch has time to rest and when the load is at the required height the winch can be locked.

These are the sites of suitable hand winches:

http://www.winchsystems.co.uk/sf-2200-hand-winch.php
http://www.winchsystems.co.uk/sf-5000-hand-winch.php

Additional points for crane specification:

Whilst looking at the initial sketch of the crane it is very important to take into the account the following :

1) The weight of the crane :

A crane which is going to lift 1000kg in weight is not going to be easy to lift as the boom and base will be quite heavy. Therefore it is essential that hollow sections are used for the struts etc. This will decrease the weight of the crane and can still give a reasonable amount of strength. The materials associated would be alluminium or steel. Alluminium would be more desirable but may be more expensive.

2) Hand winch

If you can lift 1000kg then we can make this crane just for u, hoooooowever, it is likely that you can not lift such a weight. The winch in the design would be manual rather than any other option hence we need some kind of a gear system for the winch . Maybe at a 15 to 1 reduction ratio reducing the amount of load from 1000kg to 66 kg etc etc.

3) Standard sections

All diameter of holes need to fit standard sections/tolerences. This would give ease when manufacturing such parts.

Pay-load for a Landrover Defender:

The website I found the following information on:

http://www.landrover.com/gb/en/lr/defender/explore/defender-professional/

"Dropsides

The Defender 130 Dropside in either Single or Double cab format provides huge load carrying capacity and a whole lot more. The corrosion resistant body is constructed from aluminium with zinc plated catches and corner pillars. The totally flat, wheelarchless load floor with hinged removable side boards, back boards and corner pillars all make for fast and easy load management. With a payload of 1200kg through, class-leading towing capability of up to 3500kg and optional tipper functionality, this is a truly remarkable load carrier."

This is relevant to the group becasue it gives us a maximum weight for our crane structure when it is dis-assembled for transport.

Minutes: 18/03/10

Tasks followed up:

- Individual designs verbally SWOT analysed by all of group. (Individual design drawings photographed and posted on blog.)
- R.D's design was deemed most appropriate solution and its SWOT analysis was noted.
- Design issues were then discussed and resolved and dimensions for the crane were established. This was in order to facilitate the group members going away and 're-designing' the 'initial design' with stress and bending moment analysis.
- Types of winch - electronic or hand, examples of both brought to meeting, costings and weights of mechanisms requested.

Tasks for next meeting:

- All group members to return with fully analysed free-body diagram of proposed crane design for comparison.
- Group members are also to look into bearing design for rotation of crane as well as faesible materials for the manufacture of the crane components.


Future Meetings:
Mon 22/03
Thurs 25/03


Attendees:
A. Compton
J. Collins
A. Dhillon
R. Dhillon
A. Daniels

Photographs of sketches brought to meeting by members:

Types of Cranes Research

The different types of cranes available was researched to give a broad idea of the different designs currently in use.

Gantt Chart

Minutes 16/03/10

Minutes: 16/03/10

Gantt Chart Distributed

Tasks Allocated (See Gantt Chart post)

Tasks for next meeting:
Produce Designs for crane x2
Inc. Materials Cost research, Basic Calculations etc.
Prepare for SWOT analysis of designs.

Future meetings:

Thur 18/03
Mon 22/03


Attendees of todays meeting:
A. Compton
J. Collins
A. Daniels
R. Dhillon

Minutes: 09/03/10

Project roles allocated:

· Project Manager – Amy Compton

· Finance Officer - Andy Daniels

· Chief Designer – James Collins

· Stress Analyst – Romi Dhillon

· Materials Specialist - Amardeep Dhillon

Future Meetings decided:
- Thursday's 1pm Loft.
- Monday's 1pm Loft.


Attendees of todays meeting:
A. Compton
J. Collins