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-take two points on each of two perpendicular faces. Using the coordinates of the two points you can calculate the slope of the two lines. -By taking tangent-inverse of the slopes you will get the angle. -Then you can calculate the difference between the two angles and see if they are...

I am sorry I don't really understand this question?? What is a find no?

If you want +/- 1 tolerance as per your drawing standard, then use one place decimal. If you wanted a looser or tighter tolerance then I would explicitly call it out e.g. 1660 +/- 2 or 1660.0+/- 0.5. Depends on how much deviation from the length you can tolerate on the part.

Thanks Kenat and Chris, really appreciate it!

Hi Everybody, Can you guys point me to some good resources on the net for tolerance stack analysis. Also are there any good books available for the same. Greatly appreciate all answers. Thanks to everyone who answers in advance! Thank you, Siva

Interesting thanks!

Sdeters, how would we control the offset between the two planes if we use a single datum A? If it is A & B, we can control it using a basic dimension and a profile callout as dave mentions. Is there an alternate way of controlling it if it were a single datum A?

Yes my part mounts on both these planes simultaneously (although they are offset) that why I have to use both as my primary

Thanks Dave, I agree, that was very helpful. Sdeters and Kenat, I think I am going to go with Dave on this one. Thanks for all replies!

I have this part which has two planes offset from each other. 1. can I call one plane A, and another Plane B, and call Primary as A-B 2. If i do the above How do I tolerance those two planes relative to each other? Should i call out a profile tolerance relative to A-B? 3. Where would the...

Hi All, I have this plastic part that is warped in free state. But it works well in the assembly which is all I want. What is the best way to call out a note in the drawing saying that the part is to be measured with the datums constrained. I looked up some notes and one says "NOTES (UNLESS...

Thanks guys! That was helpful. I guess for this case I would just put a size tolerance across the width and call it as my Datum. B on horizontal ones, and C on vertical ones. Paul, No , luckily we don't bend any tabs, because they are pretty short and have generous chamfers and fillets on the...

Thanks Drawoh and Kenat! Drawoh, I was considering putting a datum across the width of the slot. But since the opposing planes of the slot are staggered, I read in a book that it should not be size tolarnced unless there is some overlap. THey say that only if there is overalap, I can call it...

Hi Paul, Thanks for your reply. In my original message I have actually described how the part is assembled and what the mating features are. May be I didn't do a very good job of it, so let me try again. -The sheetmetal plate mates against a U channel (also sheetmetal) on the face that has...

Another Typo, Presently I have D-E as tertiary datum (not C-D). Thank you!

The title should read "....slot with non-overlapping opposing edges"

Hi Everyone, My questions pertain to the attached figure. -I have a sheetmetal part. -I have a face that goes against another part, and so am using that plane as Datum A. This face constrains Translation in Z, and rotation about X and Y. -I have six staggered dog-bone type feature (see...