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True position of a hex center? 7
- Thread starter alkung
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If the machinist is using a rotary broach, then it probably is. It depends on the machinist.
See for an example. There are other suppliers; Google search put this one at the top of my list.
Other than that, the callout is really so the inspector can verify that the part meets requirements and for the engineer to accurately record a solution to the problem. If the solution requires uniformity of shape and that shape needs to be located in some way, then profile is a correct choice.
See for an example. There are other suppliers; Google search put this one at the top of my list.
Other than that, the callout is really so the inspector can verify that the part meets requirements and for the engineer to accurately record a solution to the problem. If the solution requires uniformity of shape and that shape needs to be located in some way, then profile is a correct choice.
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Another solution could be:
Directly toleranced size hex dimension, phantom maximum inscribed circle around the inside hex and position associated with it. Position could be at MMC to help functional gaging for assembleability.
True profile of the inside hex would be dimensioned with basic angles and basic corner radii.
I got this concept from another discussion where pmarc participated and I would like to know if can be applied here. All the credit ( if solution is acceptable) shall go to pmarc.
Of course the OP has to use 2009 versiun of ASME Y14.5 so the position callout can be applied to irregular features of size.
Directly toleranced size hex dimension, phantom maximum inscribed circle around the inside hex and position associated with it. Position could be at MMC to help functional gaging for assembleability.
True profile of the inside hex would be dimensioned with basic angles and basic corner radii.
I got this concept from another discussion where pmarc participated and I would like to know if can be applied here. All the credit ( if solution is acceptable) shall go to pmarc.
Of course the OP has to use 2009 versiun of ASME Y14.5 so the position callout can be applied to irregular features of size.
Well, if the thread is doing the job of orienting this part in the assembly, probably is a good choice to be a primary datum.
What else COULD orient this part? How this part physically interacts with its mating components in the assembly? Physical realities of this assembly.
What else COULD orient this part? How this part physically interacts with its mating components in the assembly? Physical realities of this assembly.
Just was surprised that no one mentioned it. Every GD&T author that I have read says to never use threads as datums unless you absolutely have to. That sentence is usually followed up with one that says even if you have nothing else to choose from you should still consider not using them.
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pmarc
Mechanical
- Sep 2, 2008
- 3,248
greenimi,
This solution would be the last I would use and recommend in this case, unless there is really a functional need to define something working along dynamic-profile-tolerance-zone lines. The reason I came up with this method was that in the 2009 version of the standard there is no tool that would work similarly to "dynamic tolerance zone" modifier (as proposed in the new draft of Y14.5). The tricky part of it is that hex contour is not fully defined with basic dimensions, and so many people may see this as a violation of the profile tolerance application rules. I personally think it is more like extension of principles (supported by the infamous figures from the standard where cones are controlled by combination of directly toleranced +/- diameter and profile tolerance).
With that said there are at least couple other ways to control hex features, and most likely at least one of them will grasp the design intent (some of them have been already mentioned):
1.Three position feature control frames applied to each pair of parallel faces and referencing to A. Tricky part of it: inspection will have to know that these position callouts apply simultaneously, so in fact the angles between center planes of pairs of faces are also indirectly controlled.
2. Simple all-around profile callout wrt A.
3. Composite all-around profile callout with upper segment referencing A (location control) and lower segment with or without A (size/form, or size/form/orientation control).
4. Combination of datumless all-around profile tolerance and position at MMC.
5. Combination of datumless all-around profile tolerance applied directly to hex contour and position at MMC wrt A applied to a phantom maximum inscribed circle.
6. A little bit more tricky application of combination of datumless all-around profile tolerance applied directly to hex contour and position at RFS wrt A applied to a phantom maximum inscribed circle.
This solution would be the last I would use and recommend in this case, unless there is really a functional need to define something working along dynamic-profile-tolerance-zone lines. The reason I came up with this method was that in the 2009 version of the standard there is no tool that would work similarly to "dynamic tolerance zone" modifier (as proposed in the new draft of Y14.5). The tricky part of it is that hex contour is not fully defined with basic dimensions, and so many people may see this as a violation of the profile tolerance application rules. I personally think it is more like extension of principles (supported by the infamous figures from the standard where cones are controlled by combination of directly toleranced +/- diameter and profile tolerance).
With that said there are at least couple other ways to control hex features, and most likely at least one of them will grasp the design intent (some of them have been already mentioned):
1.Three position feature control frames applied to each pair of parallel faces and referencing to A. Tricky part of it: inspection will have to know that these position callouts apply simultaneously, so in fact the angles between center planes of pairs of faces are also indirectly controlled.
2. Simple all-around profile callout wrt A.
3. Composite all-around profile callout with upper segment referencing A (location control) and lower segment with or without A (size/form, or size/form/orientation control).
4. Combination of datumless all-around profile tolerance and position at MMC.
5. Combination of datumless all-around profile tolerance applied directly to hex contour and position at MMC wrt A applied to a phantom maximum inscribed circle.
6. A little bit more tricky application of combination of datumless all-around profile tolerance applied directly to hex contour and position at RFS wrt A applied to a phantom maximum inscribed circle.
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- #11
These are all great answers guys, thanks!
All these make sense to me however I am relatively new to GD&T, how would you carry out number three? Would it be like in this picture?
And if it is like in the picture does it essentially mean that the bottom part provides a hexagonal shaped tolerance zone of 0.02 (constraining the actual profile of the hex) and then the top part provides a 0.05 tolerance zone (also hexagonal) in which that pattern must fit?
Thanks again!
All these make sense to me however I am relatively new to GD&T, how would you carry out number three? Would it be like in this picture?
And if it is like in the picture does it essentially mean that the bottom part provides a hexagonal shaped tolerance zone of 0.02 (constraining the actual profile of the hex) and then the top part provides a 0.05 tolerance zone (also hexagonal) in which that pattern must fit?
Thanks again!
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Regarding the use of threaded features as a datum - meh... they make Jo Plugs for a reason. There are occasions where a threaded feature is actually serving more functions than simply fastening, but I absolutely agree that it should be treated as exceptional.
You'd be hard pressed to prove your case if the thread in question was something like a 1/2-13 UNC-1A though...
You'd be hard pressed to prove your case if the thread in question was something like a 1/2-13 UNC-1A though...
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