A second pair if educated eyes is invaluable in accuracy of the final engineering product. Many companies now have deleted the seperate checking function, relying on CAD accuracy and expecting the drawing generator to review their own work before filing and submitting it. IF you find a mistake...
As an old job shopper, I've seen several different methods of defining quantities adjacent to balloons. What I like best is a well defined company DRM which unifies the method of qty definition on assembly drawings; noting that the BOM is the ultimate authority, and assy dwgs must agree with it...
I love GD&T as much as anyone, but in this case, I would treat that wire the same way I would treat a single line bent pipe spool, and forget the GDT altogether. Not saying you couldn't come up with a method, but since it is coated anyway, why bother?
I've done this before and there is a couple ways. You can dimension the slot and the counterbore slot to the same datums each having it's own FCF and maybe a relaxed tolerance on the counterbore, or you can positional tolerance the slot a per the standard and give it a datum, say D. then...
Since KENAT is checker and I am a checker, can we trust the comments of "CheckerHater"? [wink].
Nice to be back. A former client dragged this old job shopper out of retirement and brought him back to check again, for a while. We may be a dying breed, but not just yet.
Seems like company preference is the bottom line. The places I have been at recently like to put the notes in the upper right, sufficiently below the Revision Block, in order to make more room for drawing space. This works good for detail part drawings.
For assemblies, is is better to have them...
As Jim Sykes says, don't confuse Roughness Max and Roughness average Max.
ASME Y14.36 para 4.3 "Roughness Average (Ra)" states "The principle parameter specified for roughness average, Ra, defined in ASME B46.1. It is the value shown in position "a" of the surface texture symbol (i.e. directly...
I am not a big Pro/E guy, but my officemate says:
Sounds like doing family tables to large assemblies is going in the wrong direction. You should try looking at simplified reps to create your individual subassemblies as needed. That will allow you to turn parts on and off.
Thanks, John-Paul. In kicking these ideas around with my colleagues, we came to the same conclusion as you, that the first two examples are really not features of size. Para 1.3.17 of 1994 ed. seems to say that, and the expanded explanations in 1.3.32 of 2009 clarify it for us.
Let me throw another monkey wrench into the works. What if I need to make dimension A width a symmetry datum for other symmetrical features, but the the 2 sides of dimension A are not directly oppoded so that I can put a calipers or mic across them. Isn't it still a feature od size? Bottom...
Belanger, your last post re: directly toleranced dimensions raises a question in my mind on SeasonLee's sample above. Wouldn't you say that dimension A is a directly toleranced dimension in all three examples, directly opposed or not?
I can envision fitting dimension A on all 3 examples into a...
B46.1 Appendix B1 Specification says this:
"(a) Surface texture should not be controlled on a drawing or specification unless such control is essential
to the functional performance or appearance of the product.
Unnecessary restrictions may increase production
costs and mitigate the emphasis on...
The term "OR BETTER" is clearly redundant, as is MAX. It has been eluded to above, most clearly by dgallup, that a stated roughness average (Ra) is: (per Figure 5 of ASME Y14.36)"The specified roughness average shall indicate the maximum value and any lesser value shall be acceptable."
The...
ditto on ASME B1.1. Also most thread calcs for tensile or shear use the thread root area. Most conservatively based on min minor of external thread. www.boltplanet.com is a good source for such thread data
