Slot Profile Tolerance
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That being said, I am thinking of applying two single segment profile of surface tolerance frames, all around, to both subgroups of 5 slots (tolerance values are exmplary, slots geometry and location are assumed to be defined by basic dimensions. A simple example would be a set of holes (pattern) used to affix a name plate. The relative position of the holes is important (tighter tolerance), in order to match the same hole on the plate itself, but the absolute position of the entire pattern on the part may be less critical (looser tolerances) as long as the orientation is good.Profile Tolerance for Slots
*Profile, desired surface finish and tolerance specifications. Even with these noted walls thickness due to the complexity and the press’ that are available some profiles may need more material thickness. 6063 / 6463.045 1.143mm.050 1.27mm.062 1.574mm And the trend continues. Uniform wall thickness.
*Profile T-Slot Nut Heavy-Duty T-Slot Nut; L5: 1,000N: N/A: L6 Standard: 3,500N: N/A. Torsion tolerance T mm inch for length L mm inch from to up to 1000mm 39.
*Holes and Slots Standard Holes. Standard hole sizes for bolts are made 1/16-in. Larger in diameter than the nominal size of the fastener body. This provides a certain amount of play in the holes, which compensates for small misalignment’s in hole location or assembly, and aids in the shop and field entry of fasteners.Profile Tolerance for SlotsSlot Profile Tolerance MeaningHello Everyone,
I have a flat plate with 5 slots in a linear pattern. Primary Datum A is one face of the plate, and secondary and tertiary datums B&C are 2 perpendicular sides of the plate. I would like to use GD&T to locate and orient the slots. I am not so interested in tightening the distance of the slots from the datums (edges of the plate). I am, however, interested that regardless of where the pattern is, that the slots themselves remain controlled to each other. I would also not like them to be significantly rotated with respect to the plate edges, but translation is ok. If these were holes, is ASME, they could be described using a composite position tolerance from the datums such as:
|Pos|Diam 0.5|A|B|C|
| |Diam 0.1|A|B|
Or as I have learned from this board by the new ISO standard
|Pos|Diam 0.5|A|B|C|
|Pos|Diam 0.1|A|B><|
I’m working to ISO. In this case, however, I am locating slots and not holes. From my research, it seems I can use a surface profile tolerance to locate and orient the slots from the datums. This has brought up a number of questions regarding the use of the profile tolerance.
1) First of all, what would be the best way to achieve what I want to achieve as described above?
2) I have seen a couple of different ways to tolerance slots using GD&T. One was a video from Tec-Ease (ASME) where the callout looked something like:
|Profile|1|
|Pos|Diam 0.5|A|B|C|
I’m not exactly sure what the position is referring to specifically in this feature control frame. Is it referring to the theoretically perfect profile, or a centerpoint, or a centerline? Can this be done in ISO?
3)Other methods which I have seen involved using the profile as a location and orientation and form control, as in:
|Profile|1|A|B|C|
In this case, as I understand it, the slot (assuming we’re talking about a slot) would be located to the datums with basic dimensions and the actual profile could be +0.5 or -0.5 the size of the exact theoretical profile at the exact theoretical location. Therefore, the actual slot would have to be located within these boundaries. Why would one use the method specified in question 2 instead of this method?
4)When using a profile control on a slot, is it necessary to use the all-around symbol on the leader? Is this symbol even available in ISO? I’ve only seen it in the ASME books I have. When is it actually necessary to use this symbol?
5)If a profile tolerance were to be used on a slot to control the form, location and orientation, how would it be measured properly without the use of CMM? Is there a way to do this without very complicated and expensive measuring tools?
Thanks!
Let’s go back to the question box —
“Why is profile allowed to be designated as one-sided? Can other GD&T symbols also be one-sided?” First, let’s address a couple of points: there are two profile symbols: profile of a line and profile of a surface. Yes, each of them can have the tolerance amount that is unilateral (one-sided) or bilateral (both sides of the intended profile). Also realize that the profile symbols can be “unequal bilateral” where there is tolerance on both sides of the perfect shape, but more tolerance exists on one side. Some examples:
No other GD&T symbol can use these options; there is no such thing as unilateral flatness or unilateral parallelism. Why is that? Well, when we talk about flatness or parallelism, the feature in question has no curvature. So the surface “is where it is.” Profile tolerances, however, have a curve (usually) and also one or more basic dimensions that describe the radius or other values. The prescribed radius is important, and if the curve dips in or out, it is directly impacting the given radius. With this in mind, I should point out the tolerance zones for some other GD&T symbols can float to one side or the other. For instance, a parallelism tolerance of 0.5 allows a surface to tilt 0.5 mm in either direction, but that is not considered a unilateral tolerance, because it is a flat surface. (If it curves in or out, it doesn’t have to follow a particular radius.)Slot Profile Tolerance Definition
Whether you our your company need a GD&T refresher or a comprehensive training program, please contact us for information about how we can help everyone in your group get on the same page when it comes to the language of GD&T!
Register here: http://gg.gg/v8yjp
https://diarynote.indered.space
That being said, I am thinking of applying two single segment profile of surface tolerance frames, all around, to both subgroups of 5 slots (tolerance values are exmplary, slots geometry and location are assumed to be defined by basic dimensions. A simple example would be a set of holes (pattern) used to affix a name plate. The relative position of the holes is important (tighter tolerance), in order to match the same hole on the plate itself, but the absolute position of the entire pattern on the part may be less critical (looser tolerances) as long as the orientation is good.Profile Tolerance for Slots
*Profile, desired surface finish and tolerance specifications. Even with these noted walls thickness due to the complexity and the press’ that are available some profiles may need more material thickness. 6063 / 6463.045 1.143mm.050 1.27mm.062 1.574mm And the trend continues. Uniform wall thickness.
*Profile T-Slot Nut Heavy-Duty T-Slot Nut; L5: 1,000N: N/A: L6 Standard: 3,500N: N/A. Torsion tolerance T mm inch for length L mm inch from to up to 1000mm 39.
*Holes and Slots Standard Holes. Standard hole sizes for bolts are made 1/16-in. Larger in diameter than the nominal size of the fastener body. This provides a certain amount of play in the holes, which compensates for small misalignment’s in hole location or assembly, and aids in the shop and field entry of fasteners.Profile Tolerance for SlotsSlot Profile Tolerance MeaningHello Everyone,
I have a flat plate with 5 slots in a linear pattern. Primary Datum A is one face of the plate, and secondary and tertiary datums B&C are 2 perpendicular sides of the plate. I would like to use GD&T to locate and orient the slots. I am not so interested in tightening the distance of the slots from the datums (edges of the plate). I am, however, interested that regardless of where the pattern is, that the slots themselves remain controlled to each other. I would also not like them to be significantly rotated with respect to the plate edges, but translation is ok. If these were holes, is ASME, they could be described using a composite position tolerance from the datums such as:
|Pos|Diam 0.5|A|B|C|
| |Diam 0.1|A|B|
Or as I have learned from this board by the new ISO standard
|Pos|Diam 0.5|A|B|C|
|Pos|Diam 0.1|A|B><|
I’m working to ISO. In this case, however, I am locating slots and not holes. From my research, it seems I can use a surface profile tolerance to locate and orient the slots from the datums. This has brought up a number of questions regarding the use of the profile tolerance.
1) First of all, what would be the best way to achieve what I want to achieve as described above?
2) I have seen a couple of different ways to tolerance slots using GD&T. One was a video from Tec-Ease (ASME) where the callout looked something like:
|Profile|1|
|Pos|Diam 0.5|A|B|C|
I’m not exactly sure what the position is referring to specifically in this feature control frame. Is it referring to the theoretically perfect profile, or a centerpoint, or a centerline? Can this be done in ISO?
3)Other methods which I have seen involved using the profile as a location and orientation and form control, as in:
|Profile|1|A|B|C|
In this case, as I understand it, the slot (assuming we’re talking about a slot) would be located to the datums with basic dimensions and the actual profile could be +0.5 or -0.5 the size of the exact theoretical profile at the exact theoretical location. Therefore, the actual slot would have to be located within these boundaries. Why would one use the method specified in question 2 instead of this method?
4)When using a profile control on a slot, is it necessary to use the all-around symbol on the leader? Is this symbol even available in ISO? I’ve only seen it in the ASME books I have. When is it actually necessary to use this symbol?
5)If a profile tolerance were to be used on a slot to control the form, location and orientation, how would it be measured properly without the use of CMM? Is there a way to do this without very complicated and expensive measuring tools?
Thanks!
Let’s go back to the question box —
“Why is profile allowed to be designated as one-sided? Can other GD&T symbols also be one-sided?” First, let’s address a couple of points: there are two profile symbols: profile of a line and profile of a surface. Yes, each of them can have the tolerance amount that is unilateral (one-sided) or bilateral (both sides of the intended profile). Also realize that the profile symbols can be “unequal bilateral” where there is tolerance on both sides of the perfect shape, but more tolerance exists on one side. Some examples:
No other GD&T symbol can use these options; there is no such thing as unilateral flatness or unilateral parallelism. Why is that? Well, when we talk about flatness or parallelism, the feature in question has no curvature. So the surface “is where it is.” Profile tolerances, however, have a curve (usually) and also one or more basic dimensions that describe the radius or other values. The prescribed radius is important, and if the curve dips in or out, it is directly impacting the given radius. With this in mind, I should point out the tolerance zones for some other GD&T symbols can float to one side or the other. For instance, a parallelism tolerance of 0.5 allows a surface to tilt 0.5 mm in either direction, but that is not considered a unilateral tolerance, because it is a flat surface. (If it curves in or out, it doesn’t have to follow a particular radius.)Slot Profile Tolerance Definition
Whether you our your company need a GD&T refresher or a comprehensive training program, please contact us for information about how we can help everyone in your group get on the same page when it comes to the language of GD&T!
Register here: http://gg.gg/v8yjp
https://diarynote.indered.space
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