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Hii Thanks for the comment. I tried that, It worked. But again is gives another error message saying "invalid matching". Cannot compute neighbouring facets for the given start facet. And the referrence stage 1 in not computed. Any idea what to do?

But wouldn't the proper way to set that up be TP of C to AB and then use Best fit TP Callout, using the feature in the TP callout as a Datum seems wrong.

Datum C is just for stopping rotation - it's like using bestfit rotation. Nothing bad here. You still have to have correct distance from B origin.

True positions don't have to fully constrain a part. You can TP to one datum if youd like (You get only perpendicularity, but its legal). The positions apply with whatever constraints are offered. Since datums consume constraints as they are available, you need more information than just ABC to help more.

That might be the issue for us, we've never really changed the location of actuals, it was always default (probably in the plans' folder?)

I have about 300 dimensions for each X,Y and Z. Is it possible to change all tolerances from 1mm to 1.5mm without having to edit each individual dimension? Found it. Using the properties window to the right, under Tolerances I can change all

can may must rule: if a datum feature can (is physically able to) and may (is permitted to by the drawing) constrain a degree of freedom (DOF), then it must do so. Most often, your primary datum will constrain 3 degrees of freedom, your secondary will constrain 2, and your tertiary will constrain 1. But not always, it all depends on what your datum 'can may and must' constrain.

@BlueSky Assuming you saved the measurements and they included the features you want the XYZ data from, tick the XYZ coordinates box for each feature, then do a subsequent evaluation of multiple measurements (under the Plan menu drop down).

Both Machines came from Zeiss yes, they also both have the separate drive and the files like screenshot below, I am not sure what exactly has stopped it though, likely IT. No Acronis file on the desktop and again... all we seem to have on both computers is this cyber protect monitor that doesn't seem to like doing much of anything. @Kyle Johnson I appreciate your response. I'll poke around with it myself more /one day/.

I was facing similar thing on new pc with Calypso 24 - in autorun we had stored pallet programs with headers prefilled - but on new Calypso this was overriden by this "default" value. Also i miss changing comboboxes - on older versions you could focus header and by clicking on keyboard arrows you could change it's value - now it's opening that list. It's a little annoying, but we can live with that 😄

This was the solution. The userfields.ini had a defaultValue=XXXXX. And removing the XXXXX part of it made it work. The confusing part that made it hard to figure out was that every other calypso 2024 installation on the other machines did not act like this (they have default values) but this one new computer needed them blank.

First of all - i would do some basic determination how much are holes variable in position. For alignment - i would use start alignment for manual location. For base alignment - i would use sperical probe, but touching by shaft ( like using cylindrical ) just around and then touch in middle. Then using 9 points for cylinder ( 3 circular paths ). If thickness of material with combination of differences in radius can matter to correct scan, then scan area around to obtain correct origin of circle/cylinder ( depending on scan path )

Thank you, I do have a 3 cad file.

Are you sure that those are not short parallel planes, just below Datum D? If not, I would probably create an intersection to Datum D, or a theoretical plane at a specific distance.

I think on Calypso it's working like what is first it's taking whatever is possible. Exceptions are for points and circles - they should not give vectors - only position. I like it in Zeiss Inspect, where you see result. Also Inspect is much advanced about coordinate systems. It allows you to select multiple features to act like pattern and you can also select if you want from it only direction or point also. So here is an example: Primary: circle -> origin Secondary: line -> rotational axis Tertiary: plane -> stopping rotation

I'm afraid I can't find one, at least not one that I feel comfortable sending out since we don't make it. If you want a simple step by step breakdown, you go through this process for all 6 degrees of freedom possible in a rigid object (i.e. translation and rotation in X, Y and Z): 1. Can - Is the datum physically capable of constraining this degree of freedom? For instance, a plane with the axis in the Z direction can stop translation in the Z, but it CANNOT stop translation in either the X or Y (think of putting that plane on the granite of the CMM, you can't push it further in the Z, but you can slide it in the X and Y as much as you like). Likewise, a cylinder or circle in Z axis can stop translation in the X and Y, but not in the Z (think of putting a pin in the feature). 2. May - Is there a higher priority datum already constraining that degree of freedom? If two datums pass step 1, then the one that comes earliest in the datum structure of the callout gets priority (that's why its primary, secondary and then tertiary). 3. Must - If the datum fulfills the requirements in step 1 and 2, then this datum MUST control that degree of freedom. Hopefully this helps, at least a little. I know it isn't the PDF you were looking for, but in terms of concise explanations, hopefully that gets the job done.

@Matthew S Can you share a snippet of a drawing or elaborate? Without knowing what type of features A, B, and C are this question is hard/impossible to answer.

I am working on and injected molded part and it calls out two planes both slanted away from each other at an 8 degree angle, how do I set this up for a solid inline parallel plane tolerance zone?

@Ramiro Hernandez If you don't have a 3d file available, you are more than likely going to need to have one made from a drawing. The next step would be to use the CAD file to create a reference point system (RPS) alignment. This is a common alignment system used in the auto industry for things like body panels that lack standard geometries. There are threads on here about RPS alignments in Calypso. I haven't used RPS alignments all that much in Calypso, but I do remember that looping the RPS alignment at least 3X is important. Hopefully someone with more RPS alignment experience chimes in. Best of luck sir.

Ok, I realize this is probably a simple one but why can't you call-out TP of Datum C using FCF ABC? I know you can't but how is the part fully constrained if its only called back to AB?

I have asked the German support team about this before and Martin is correct. It is not configurable except by changing the internal names (and even then, if you use predefined fields, that might throw you off).

I've heard this rule several times but I can't find the definition of it anywhere and I was wondering if anyone has a PDF or something I can reference to use it.

Honestly the easiest method would probably be make the relevant circles and then recall the data in that relevant area into them and use caliper distance on those. The other "simpler" way would be to use this caliper distance than use a result element to subtract out half of the length from both cylinders, like how we used to do it before the caliper distance characteristic. There are a couple other methods I can think of, but they would be a bit more involved than either of those solutions and would give pretty close to the same result regardless.

Another thing to note, if these are header fields you made and have defaults set in there, Calypso will reset it to the defaults after every run, at least in newer versions. If I recall correctly, this was a requested change made a few years back.