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question though: We place the datum targets (especially the POINT and LINE) with TEDs (Theoretical Exact DImensions). Looking at Datum Target Regions, this I can understand. The actual reference point in should touch the part within that circle. But now the POINT and LINE..... a TED gives an EXACT dimension. so no tolerance... what indicates the TOLERANCE on the location of a Datum Target Point (or line)?

1.5/2(bolt hole radius)+6.5/2(bolt circle radius)=4, which is also the radius of the cylinder. Does that mean the edges of the holes and the cylinder actually intersected?

How to find machining force

Great video! Can you perform stack up analysis for one part that has both a chain and baseline dimensions?

Very well explained. Thanks for making this video.

I’m not sure that you can calculate the standard deviation like you did, unless you consider that the CP for each “components” is 1. Then you can apply the formula that you did.

question when using an insert do I use MMC for hole?

7:11

Very Informative! Thank you!

Nice good job

sigma methodology has been demonstrated very nicely

I'm glad they removed concentricity from the new standard. It was, without a doubt, one of the most misunderstood controls in the standard.

Such a useful tool, in theory it gives the hole pattern more freedom to the datum whilst still enabling mating parts to fit in the holes but unfortunately manufacturers just look at it and charge you more because there's more GD&T.

Thanks for this information. It is useful to me. I have to learn about GD&T. Because I have to use it at work.

Great graphics and examples using ASME Y14.5 Standards. Thanks for the quality video on functional GD&T design. Go & No-go Gages and functional gaging are unique to precision inspection. THANKS and keep up the efforts! T J (Tom) Vanderloop, Author, Mechanical Designer, & Consultant: ATEA, AWS & SME Leader & Memberships

Thank you for your time and good teaching ... The best.

Well explained

Hi, so only when you've made the part that's when you can determine the "t" value and therefore determine the width of the tolerance zone?

If i have LMC on true position box ? Can i apply like MMC to get bonus on torrence zone?

So what is use of profile of line though..since the components will always be 3d..and we can chosse directly profile of a surface over profile of a line? Am I missing something?

Great explanation. Respect Sir! God bless you.

thank you

th-cam.com/video/ILXGSd4OSoo/w-d-xo.html

Great work man

how to do tolerance analysis and tolerance standard?

Thanks bro.

Great lecture . Thank you.

Virtual condition is always the worst case condition regardless of hole or pin size. How can that be? An infiniately large hole should have a larger VC than a 1" hole. Please explain. Thx

Great explanation John. I have a question for you. Could a primary datum plane be defined by using more than three datum target points? I have a drawing that specifies datum targets A1, A2, ..., and A7. How should I use them?

Sir how have u decided .05 value

where to get .1 sir..is there any chart we have to follow?

Hi Sir, can you explain the cumulative effect of tolerance based on Sure fit law and truncated normal law

MMB for Datum feature B aint bonus tolerance, it is just shift, other than that, i love the video

I think code should be 1,1,0

draws far two many lines

You can use E isn't it?

John, can you please share the presentation?

extremely well explained concepts, thanks a lot. please make more videos. thanks again

Amazing explanation! Thank you very much!

thanks

Very nice explanation

If MMC on thread holes, which diameter can be calculate for tolerance zone.pitch diameter or inner holes.

@5:30 you say Datum A is primary, but isn't Datum B the primary datum?

explained very well, this is very helpful. Found this calculator for stackup : smlease.com/entries/tolerance/tolerance-stackup-calculator

Quite Easily Explained :-), great job John

Is cylindricity double the concentricity?

Very Helpful - Thank you!

A typical reaction to GD & T in Canadian industries in the province of Ontario: 1. Too much time is consumed to draft. They love to work by the nominal dimension and a general tolerance of +/-0.005 (0.127mm) .....and the features (holes and mating parts have no connection to the gen. tolerance during planning the clearances. And if one wants the part to be "super" accurate then one must increase the nominal dimension after the decimal to 4 or 5 places!! But the gen. tol. is again +/-0.005!! 2. When the tolerance units exceed 4 to 5 places after the decimal in GD & T flag...everyone flips. Engineers, machinist and inspection. They cannot think beyond 0.005" 3. They love to think and talk in fractions and expect everyone to understand. Well, we all understand fractions but very difficult to visualize the distance when your're from the metric world. 4. GD & T will bring up the cost of manufacturing...as per many. The GD & T flags are intimidating per many and give them a vertigo. 5. The machinist said: The machine will give the accuracy it can. We cannot ask for more accuracy... It is very frustrating to work with unskilled and arrogant engineering personnel.

I'm sorry I couldn't understand how u arranged the chart. Could've started with some small table first and then moved on to the next.

very nice & detailed teaching ... ,😀😵