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displacementexercise

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    micro Stress vs Strain Machine

    Drawingboard Return

    With #2 feeling somewhat unloved ('both overdesigned and underdesigned'), I'm back at the basics for #3. There's a few major selections, and decisions to make:

    Material Selection

    -> ALU, FR4(G10), Acrylic?

    While aluminum is my go-to for machine design, and is ostensibly possible to mill on a shopbot by a motivated user (see jens), there is some hesitation to use it.

    Material Young's Modulus (GPA) Specific Young's Cost for 6mm x 24x24" Machinability
    ABS 2 ? 52 Not Dimensionally Stable, but OK to Machine
    Nylon 6 3 2.5 130 Painful
    HDPE 1 ? 23 Easy
    Acetal (Delrin) 2.8 ? 89 Breezy, also lasers, and non-cracking
    Cast Acrylic 3.3 2.8 46 Breezy, esp. w/ Lasers
    6061 ALU 69 22 87 Breezy with WJ, Painful on Shopbot
    FR1/CE (Canvas / Phenolic) 6 ? 81 TBD, probably WJ Pain and Ease on SB
    FR4/G10 (Fiberglass) 22 ? 98 Painful on a WJ, Slightly Easier on a Shopbot

    data

    That said, ALU lands pretty well 1 order of magnitude above Canvas Phenolic ('FR1' or 'CE') for strength, while costing a similar amount of dollars. Fiberglass is a nice candidate, so machining G10 is likely a worthwhile experiment. However, both composites have anisotropic-ness and are sensitive to the size of local features (and to localized loads), making them less favourable.

    !TODO: beam equations for the above, to size req' depth !TODO: shear forces for the same, !TODO: cost not-mcmaster, and acrylic, some composite like hydrostone w/ fiber

    • ... composite vendors at fabclass website

    Transmission Design

    How Many kNs ?

    We want lots of force, with very fine control of position. This means a nice linear transmission. To estimate the forces we might want to see, I wrote a quick table of forces required to rip apart ~ 3mm square (0.001mm^2) samples of a few materials.

    Material Yield (MPA) F at Break (N)
    ABS 40 360
    Nylon 6 70 630
    HDPE 15 135
    6061 ALU 310 2790
    4140 Stainless 655 5895
    6AL-4V Ti 950 8550

    Brinell hardness tests range from 10N through to 30kN (for steel and cast iron) but non-ferrous materials normally see 5kN only.

    So, a ballpark of ~ 10kN would be ideal - this is a big number - off the bat I'm going to estimate that 5kN will be a more reasonable target. 1kN is enough for a complete set of plastics, but that's only allowing for a realtively small sample.

    -> Ballscrews, Belt Rack and Pinion, Rack and Pinion

    Generating kNs of force is no easy feat, especially when we want to do it very smoothly while displacing very small amounts.

    I will start by mentioning that this is dead easy with ballscrews. With a 1605 ballscrew, (16mm diameter, 5mm per turn) and a NEMA23 with 3Nm of torque, we can generate about 3kN of linear force (per motor) - to land at 5kN total no problem.

    However, these are somewhat cumbersome and expensive - and they land in fixed sizes. Towards more parametric machines, we can look at a rack and pinion type axis.

    ballscrew maths

    Because tooth geometry very sensitively affects linear-ness of drive, especially where (down below the mm) we will be driving an entire instron test-cycle inside of one tooth-phase, I want to discount a traditional rack and pinion right off.

    I am curious about a belt-driven rack, similar to this design.

    !TODO: compare by transmission ratios (abstract from motor) and cost of parts. !TODO: belt spec for hight (huge) load belts: tooth shear, and stiffnesses.

    Motor Torques

    To generate the force required, we're going to need some motor / transmission oomph. Here's a list of typical NEMA size motors, and the torques they can generate. The atkstepper can supply enough current to power any of these.

    Motor kg Nm
    N23 56mm 1.2 1.3
    N23 100mm 1.8 3.0
    N34 68mm 1.8 3.4
    N34 156mm 5.4 13.0
    N42 150mm 10.9 22.0

    Racks and Pinions

    We'll be using two linear stages (one on either side of the platform), so, from our N34 156mm motor with 13Nm of torque we'll need 26, 5.2 and 2.6mm lever arms respectively for 1, 5 and 10kN total force.

    Considering practical limits on pinion diameter (with a shaft of 14mm, and 19 3mm-pitch teeth, we'll have an 18mm diameter pinion - 9mm lever arm) we will only realistically achieve 1.44kN of linear force per motor with direct-drive rack and pinion on a Nema 34 size motor. This makes a 3kN machine, but to add some safety factor we're at at 2kN goal with this approach.

    The next step would be to check against tooth shear stress for 3mm pitch.

    From reasonable WEDM (time) and Waterjet (washout) limits, I expect the thickness of any fabricated pinion to have a limit around 12mm. To make this all simple, I'll say 10mm. For the waterjet, this is a bit of a stretch (get it?)...

    To guess at resolutions, we'll take our sample above in aluminium having a length of 100mm - with elongation at break being 12%, we're interested in a 12mm 'long' stress / strain curve. For 1000 pts on this curve, we're interested in a step size of 12 microns.

    From our 18mm diameter pinion having a circumference of 56mm, this means 4667 counts per revolution. In a 200-step motor, we would need 32 microsteps per revolution - most drivers will go to 256 - but microstepping isn't exactly linear. To do this really well, we will want to finish work on closed loop stepper driving, where we can use a 14-bit encoder to control around ~ 4096 counts reliably.

    All in, a direct rack and pinion drive can land us at a 2kN machine with some desired resolution, but we're at or near most of the limits here.

    Belts

    img

    Since I was spinning this up to test on a belt-driven gantry system, I was able to confirm that this is a bad idea. We defeat the elastic stretch of the belt by measuring at the specimen (not through the machine's structural loop) but a meagre GT2 belt profile skips teeth pretty quickly as we approach any tens of kilos of load.

    Ball or Leadscrews

    Racks aside, a ballscrew is the obvious way to do this. Ballscrews can be had for less than hundereds of dollars. Besides transmitting motion smoothly, their ratios are favourable. For example, with a 5mm pitch ballscrew having an efficiency of 85%, we can drive 14kN with our 13Nm motor - so 28kN for the machine.

    For the same ballscrew, to achieve 12 micron resolution we'll only need 416 steps in each rotation - this is easy to get.

    Design Spec / Notes

    The goal here is to design and build a machine, which can be fabricated in $250k size fab labs, that can generate stress-strain curves for a wide set of materials as well as perform hardness testing.

    To ballpark, I'd like to see 100mm diameter plates having a total travel from 0mm separation -> 500mm, this leaves enough room for fixturing etc.

    Sam's note: the ballscrews should be 'pulling' in all cases. Against their fixed, driven side. This is a good note, thank you sam.

    Phoning Home

    Samples are ~ < 1mm thick, and data from Materiom shows loads all falling well under 100N. IMO, the machine should be spec'd somewhere positive of 500N pulling force, so that we can reasonably pull apart big plastic samples. That said, 500N < 5kN.

    Down here, once-reduced belt-and-pinion rack drives feel good. Since I'm looking for a medium high-force actuator to solve a 3D Printing-Bed problem elsewhere, I'm going to try to combine work here again, and develop a 3d-printing + laser-cutter friendly high force linear system. Conservative spec will allow me to even do this with N17 motors,

    Step Two: Force Measurement

    For load measurement, Sam has worked through a great loadcell design.

    cell

    Ok, doing this with a wheatstone-bridge type load cell now.

    I believe I want my ADC to have the green line 'on top' and white on the bottom, of a differential channel.

    Fixturing

    img

    ! important

    uSSM #2

    img

    status machine is designed, fabricated, waiting for adaption of fixturing from 'the generalist' and for squid works controllers.

    Dedicated uSSM

    Here I'm using some

    FEA

    I ran a quick simulation to see that this flexure was OK. Here it is loaded in the direction it is meant to be stiff in, with 2.5kN applied vertically. There are two of these members being tested so this would be equivalent to 5kN of force, about where I expect this thing to top out. Displacing about 40uM (I'm looking at the face-to-face distance between the loaded zone and the fixed zone, not that rotation that appears from my non-rigorous fea constraints) with 70MPa stress maximum.

    fea fea

    And out of plane, with 250N applied, about 20uM displacement. So 1/10th the load and 1/2 of the displacement, it's at least 5x stiffer in one DOF than the other. Is that grounds for a decent flexure?

    fea fea

    uSSM #1: Generalist does uSSM

    To test requisite parts for a small stress and strain machine, I attached some jaws and a load cell to this 'generalist' machine.

    machine

    I used automatakit network controllers and atkapi to program the beginnings of a materials testing system: here I'm just stepping the axis along 25 steps at a time and capturing a photo on each step. No data yet.

    cam bone neck

    gif

    We're going to try to track the endpoints with CV, rather than fancy encoders etc. Sam has done some prior work on this, here.

    Microphone Stiffness Testing

    Alysia did this in FabAcademy and it would probably be a fun piece of kit / example for the NIST Project. Looks pretty simple... and compelling.