Tolerance symmetric Dimension to centerline
Tolerance symmetric Dimension to centerline
(OP)
Hi Guys,
I need to tolerance two opposing symmetric features with regards to their common centerline. The tolerance must be equal for both features.
Suppose i placed the tolerance only on one feature. Would it be obvious for the machinist that the opposing feature has the same tolerance (with regard to the centerline)?
Or better tolerance both features independent with regards to the centerline?
Thank you all!
I need to tolerance two opposing symmetric features with regards to their common centerline. The tolerance must be equal for both features.
Suppose i placed the tolerance only on one feature. Would it be obvious for the machinist that the opposing feature has the same tolerance (with regard to the centerline)?
Or better tolerance both features independent with regards to the centerline?
Thank you all!





RE: Tolerance symmetric Dimension to centerline
Or, you could try making the center line a datum and dimensioning the total span with symmetry within the confines of your total allowable tolerance? The ASME Y14.5-2009 book shows figure C-2 in the appendix, and there is a symbol for symmetry in that table. Additionally, Section 7.7.2 discusses the use of that symbol and shows some examples (Fig. 7-66).
If GD&T isn't an option, I would say you'd need to place a tolerance on both sides.
-Brad
RE: Tolerance symmetric Dimension to centerline
However, you can still use the GD&T "symmetry" method as long as you have another feature to use as the datum.
Also, after third thoughts, a center line should imply symmetry about itself. You may not even have to worry about it. What I assume is that when you place a dimension on opposing features that share a center line, the dimension and accompanying tolerance are evenly split by convention. I can't back that assumption up with a citation at the moment... but I'm pretty confident it's correct.
RE: Tolerance symmetric Dimension to centerline
Assuming you are following Y14.5 standard, it offers some options to do this properly, but I agree it would be really good to see at least a simple sketch of considered situation.
For sure avoid placing datum feature symbol on a centerline - it is not allowed in Y14.5 std.
Also, even that you are trying to control symmetry of features, I would recommend position tolerance, but to give further details a sketch would be helpful.
RE: Tolerance symmetric Dimension to centerline
What is Engineering anyway: FAQ1088-1484: In layman terms, what is "engineering"?
RE: Tolerance symmetric Dimension to centerline
When I have features symmetric about a centreline, I dimension across the centre from feature to feature. I use whatever feature defines the centreline, as a datum. I Apply positional or profile tolerances to the features.
I try to avoid dimensioning from centrelines, because these do not exist and you cannot measure from them. I consider a ± tolerance from a centreline to be meaningless.
RE: Tolerance symmetric Dimension to centerline
However, I will dimension off a centerline sometimes to establish a relationship between features. When I do this, I still provide a dimension to that centerline, and I understand that my tolerances are effectively doubled (not halved, as is commonly misbelieved) when doing this.
It seems to me that many informally trained drafters (i.e., engineers) confuse the function of nearly defunct Symmetrical Outline with that of GD&T's almost as nearly defunct symmetry. Instead of using Symmetrical Outline, I would use Profile. Instead of using symmetry, I would use Positional Tolerance.
Matt Lorono
Lorono's SolidWorks Resources & SolidWorks Legion
&
RE: Tolerance symmetric Dimension to centerline
RE: Tolerance symmetric Dimension to centerline
p.s. the plate has a tight fit with a flattened axle.
RE: Tolerance symmetric Dimension to centerline
As dimensioned, the flats can be 23.2 to 23.4 apart. If you follow my suggestion, you'll get 23.2 to 23.4 also, and add a location tolerance wrt the outer diameter to achieve your specific location need, etc.
It's the end of the day and my brain's fried. I might be totally wrong.
Thanks!
RE: Tolerance symmetric Dimension to centerline
What is Engineering anyway: FAQ1088-1484: In layman terms, what is "engineering"?
RE: Tolerance symmetric Dimension to centerline
"Good to know you got shoes to wear when you find the floor." - Robert Hunter
RE: Tolerance symmetric Dimension to centerline
Am I wrong? Maybe at least partially correct?
RE: Tolerance symmetric Dimension to centerline
To my knowledge this is viable, but i'm not 100% sure.
What do you guys think?
p.s. i'm using the German standard
RE: Tolerance symmetric Dimension to centerline
RE: Tolerance symmetric Dimension to centerline
Then again, I'm no expert. I'm just not convinced it's easy to measure to that imaginary diameter created when the flats are added.
RE: Tolerance symmetric Dimension to centerline
You're calling for symmetry about "A" datum which in this case it physically impossible. "A" datum is one of your flats, and it can't be symmetric about itself. I could be wrong, but it doesn't seem to work out in my head.
I'll work on a quick sketch of my idea and post it up in a few...
RE: Tolerance symmetric Dimension to centerline
Regardless, I think true position would be a much better choice than symmetry.
"Good to know you got shoes to wear when you find the floor." - Robert Hunter
RE: Tolerance symmetric Dimension to centerline
Thanks!
RE: Tolerance symmetric Dimension to centerline
I seem to recall symmetry is one of the places ISO is different from ASME and that it may be used more there.
However, I can't recall details.
Certainly I believe you still need a real feature as your datum feature, not an imaginary one.
The outside diameter looks tempting but I don't know function and I'm not up on ISO either.
To 14.5 I'd probably look to use position as ewh says.
What is Engineering anyway: FAQ1088-1484: In layman terms, what is "engineering"?
RE: Tolerance symmetric Dimension to centerline
RE: Tolerance symmetric Dimension to centerline
If I had to follow ISO standards I would use dia.82H8 feature as a datum feature A (but maybe dimensioned a little bit different that I am not using imaginary extension lines) and assign symmetry for 58.8 dim.
If I had to follow Y14.5 std, I would do similarly with one exception - position callout instead of symmetry.
RE: Tolerance symmetric Dimension to centerline
1) Are you interested in controlling the location of the surfaces only, location of the centerplane derived, orientation of the surfaces/centerplane or form?
2) Is the ID diameter you reference real (hidden) or just an extension of the radii for dimensioning purposes?
3) Do you really not care about the relationships to the OD?
4) is this for a mating fit? How does it mate?
Welcome,
Frank
RE: Tolerance symmetric Dimension to centerline
-establish a and b datums
-a dim across the flats
-apply a positional tol to that dim that references a and b
Datum a should be the perpendicular plan which these features pierce. Datum b could the outside dia. I realize the outside dia may not be functionally important, but imagine how this part will be fixtured while it is being made.
Another option is to use datums a and b and apply a profile tol to the entire interior (rounds and flats together).
Matt Lorono
Lorono's SolidWorks Resources & SolidWorks Legion
&
RE: Tolerance symmetric Dimension to centerline
- yes, this is according our ISO standard
- the ID has two flats sides, i see the previous setup gave rise to misinterpretations, my mistake to make.
- i simply want to center the centerline of the flats to the center of the ID (or otherway around, the hole with regard to the centerline of the flats).
Pls see attachment. what do you think, is the sketched tol.zone a coorect interpretation of the GD&T sheme used?
RE: Tolerance symmetric Dimension to centerline
Yes, that makes sense. Pls see attachment.
p.s. i do lot's of drawings, but never came across this before and want to be sure what i do makes sense.
Thanks again.
RE: Tolerance symmetric Dimension to centerline
If you want to control location (symmetry) of centerplane of flats in relation to ID the second scheme (4.jpg) is incorrect - you are controlling location of the axis of ID in relation to centerplane of flats.
First scheme (3.jpg) is the one you should choose, but you have to delete either position or symmetry feature control frame and leave only one of them - these two controls you put have exactly the same meaning in ISO standards so it does not make any sense to use both of them. A decision which to choose (position or symmetry) is only up to you. It is also good idea to add concentricity (position) control of OD relative to ID.
RE: Tolerance symmetric Dimension to centerline
"these two controls you put have exactly the same meaning in ISO standards so it does not make any sense to use both of them"
Yes, i know. I did it to emphasis the fact.
RE: Tolerance symmetric Dimension to centerline
One control is for sure enough. Adding something extra can only cause a lot of confusion.
RE: Tolerance symmetric Dimension to centerline
fully agree. My intension was to reiterate that they have the same meaning, not to use both.
Thank you all!