Maybe you’ve never heard this before but I appreciate how slow you talk. That way when it’s a hard concept or one I’m not familiar with I can listen to it at regular speed. To fully understand it and take the information as it’s being presented. And when it’s a concept I’m generally familiar with I can speed it up to 1.25 and 1.5 and it still sounds like regular speech and information is still clear and easy to hear. Thank you for these videos, hard to find consistent videos that go through the topics in a linear fashion while touching on every topic.
Thank you for your videos! I've been in quality for 8 years, You can teach anyone how to read a blueprint but not many have the actual comprehension of gd&t.
Thanks! I agree, anyone can look at a view and understand the shape of the object and gather the dimensions that define the size, it’s the tolerances that require training or people will try to make parts as perfect as possible.
Very informative way of teaching. I like the reference between manufacturing , QA and Engineering. Design for manufacturing it’s critical today. I’m retired QA 45 years. We need more instructors that can break it down as you do. Well done.
Thanks so much for the input! I’m always thrilled to get feedback from anyone in industry. I agree, with a CMM and a solid model, profile is no problem at all. I feel bad for anyone with a height gage and a complex curved surface to inspect though.
Excellent video, I always look for your videos if i need more information or any doubts related to GD&T and the way you explain the concepts are really good and have learnt a lot from your videos . you are doing a great job , I can't thank you enough.
Hi, yes. The next one will be position, but it’s a tough topic to cover in the way I want to do it. I’ve recorded several takes over the last few months and I can’t seem to get it the way I want.
25:00 What does the reference to Datum C do? I think it puts the tolerance zone of the first profile at 48.00 +/- 0.375 in. If the Datum C was committed, it would be a free XX.XX +/- 0.375 in tolerance zone. Is my reasoning correct? Thank you!
I have a question that my collegue and i often discuss and we cant find a definitive answer to this. Does the "all around" Symbol only specify for the outline of a part, or also for internal features. Say a Sheetmetal part with a complex outline and a rectangular window inside. My Collegue would only use one Profile tolerance box on the outside with an "all around" sign and i would also put Profile tolerances on the inside contour. Who would be right?
Do you have any videos explaining how profile can control an angle that is basic? Say a 10.500 degree angle controlled by a .010 profile and determining your angular tolerance with the profile in mind without having to draw it in a dimensioning or cad program. I hope my question is clear. I love your vids. Great stuff
Nice video, How does this tie in with point coordination system? Reason I ask is that a large amount of views would be required to follow true profiles down a pipe that is being bent. I am a strong believer in true views and profiles, but is there a way this can be captured within the ASME standard. Seems like engineers are not always following this standard even when they should be.
Can we make the profile tolerarance control 0.01 with respect to datum A,B,D instead? Then we no need to use composite profile in this case and we don't have to worry the long basic dimension back to Datum C.
Can you explain how Datum C is establish in Figure 4-4 of the 2009 standard? I'm not sure why both Profile of Surface and Parallelism with respect to Datum A are used to establish Datum C. Is the profile of surface required since the parallelism callout is a refinement?
Hi, The profile located the surface, because it is related to the datum with a basic dimension. It only needs a single reference because the feature & datum are parallel planes. The parallelism refines the surface in orientation, but not location. It would mean the same thing in this case to use composite profile with the same datum references.
I'm about to do a presentation for our engineers at our company about GD&T callouts, so this is good stuff for a quality guy. Is it wrong to think that the engineer could just change the basic dimension rather than specifying something extra in the feature control frame, for unilateral tolerances? Or is their benefit to thinking of profile in different terms of MMC and LMC, that might help control tolerance stack up of other nominals?
Hi, that’s a great question. I recommend keeping all tolerances as equal bilateral, whether plus minus or geometric. It makes things easier for programming CNC and for tolerance stackups. Since the limits are absolute, there is no practical or theoretical difference between a unilateral or equal bilateral tolerance as long as the decimal places are the same.
Great video. If I want to check the shape and position of a machine part relative to the perfect shape of my CAD model that includes this machine part, I use the "0.75 with respect to ABC" principle, right? and if i only want to control the shape of the features but not the position of the features i use the .01 in your video at about 23:40 or if just want to know the shape I put .01 without referring to datums? I want to control the "internal" shape, or how to express it, because its a sealing surface. Edit: I think you talk about what I mean it in this video czcams.com/video/ZteA93KsKB8/video.html , controlling the shape but it can "float" around a bit regarding position. Another question: Do you have something about unilateral straightness? if there is such a thing. Greetings from Sweden 🙂
Hello Sir, Could you make a video about projected tolerance zone? I found it hard to understand what is meaning of it, and when we apply it to the design. Thanks
I am taking my notes with this series. It's amazing for a mechanical engineer or anyone who has interest in it.
Great to hear! Thanks!
Maybe you’ve never heard this before but I appreciate how slow you talk. That way when it’s a hard concept or one I’m not familiar with I can listen to it at regular speed. To fully understand it and take the information as it’s being presented. And when it’s a concept I’m generally familiar with I can speed it up to 1.25 and 1.5 and it still sounds like regular speech and information is still clear and easy to hear. Thank you for these videos, hard to find consistent videos that go through the topics in a linear fashion while touching on every topic.
Thank you for your videos! I've been in quality for 8 years, You can teach anyone how to read a blueprint but not many have the actual comprehension of gd&t.
Thanks! I agree, anyone can look at a view and understand the shape of the object and gather the dimensions that define the size, it’s the tolerances that require training or people will try to make parts as perfect as possible.
Very informative way of teaching. I like the reference between manufacturing , QA and Engineering. Design for manufacturing it’s critical today. I’m retired QA 45 years. We need more instructors that can break it down as you do. Well done.
Great video. As a CMM guy nothing makes me happier than a profile tolerance and a good solid model to work with..
Thanks so much for the input! I’m always thrilled to get feedback from anyone in industry. I agree, with a CMM and a solid model, profile is no problem at all. I feel bad for anyone with a height gage and a complex curved surface to inspect though.
Exelent Explanation of the Profile Tolerance, Got good grades on practice test after watching the lecture. Thank you.
Thank you for this excellent video. One of the best I've seen on this topic.
Thanks so much!
Thanks so much for these series of videos, they are gems!
Thank you so much!
Excellent video, I always look for your videos if i need more information or any doubts related to GD&T and the way you explain the concepts are really good and have learnt a lot from your videos . you are doing a great job , I can't thank you enough.
Thanks so much!
Sir, thanks for video best and simple explanation .
Will you make a part 7 and beyond? I love how you've structured the first 6
Hi, yes. The next one will be position, but it’s a tough topic to cover in the way I want to do it. I’ve recorded several takes over the last few months and I can’t seem to get it the way I want.
@@RDeanOdell no problem! Looking forward to it!!
Great tutorial, as always.
Thanks for the support!
25:00 What does the reference to Datum C do? I think it puts the tolerance zone of the first profile at 48.00 +/- 0.375 in. If the Datum C was committed, it would be a free XX.XX +/- 0.375 in tolerance zone. Is my reasoning correct? Thank you!
I have a question that my collegue and i often discuss and we cant find a definitive answer to this. Does the "all around" Symbol only specify for the outline of a part, or also for internal features. Say a Sheetmetal part with a complex outline and a rectangular window inside. My Collegue would only use one Profile tolerance box on the outside with an "all around" sign and i would also put Profile tolerances on the inside contour. Who would be right?
Hello @R.Dean Odell
The True position without any datum, what does it mean? please, thanks
Awesome informative video!
Just a quick question, do we need to multiply the measurement we got by 2 after measuring with CMM?
Do you have any videos explaining how profile can control an angle that is basic? Say a 10.500 degree angle controlled by a .010 profile and determining your angular tolerance with the profile in mind without having to draw it in a dimensioning or cad program. I hope my question is clear. I love your vids. Great stuff
Nice video, How does this tie in with point coordination system? Reason I ask is that a large amount of views would be required to follow true profiles down a pipe that is being bent. I am a strong believer in true views and profiles, but is there a way this can be captured within the ASME standard. Seems like engineers are not always following this standard even when they should be.
Can we make the profile tolerarance control 0.01 with respect to datum A,B,D instead? Then we no need to use composite profile in this case and we don't have to worry the long basic dimension back to Datum C.
Can you explain how Datum C is establish in Figure 4-4 of the 2009 standard? I'm not sure why both Profile of Surface and Parallelism with respect to Datum A are used to establish Datum C. Is the profile of surface required since the parallelism callout is a refinement?
Hi,
The profile located the surface, because it is related to the datum with a basic dimension. It only needs a single reference because the feature & datum are parallel planes.
The parallelism refines the surface in orientation, but not location. It would mean the same thing in this case to use composite profile with the same datum references.
Does anyone have an example of a tolerance stack up with several parts that all have profile tolerances?
Great video man ! Do you have any videos on non-uniform boundaries, would love to learn more about this
Thanks! I don’t have anything on non-uniform zones, maybe one day, but it’s not a very common requirement.
I'm about to do a presentation for our engineers at our company about GD&T callouts, so this is good stuff for a quality guy.
Is it wrong to think that the engineer could just change the basic dimension rather than specifying something extra in the feature control frame, for unilateral tolerances?
Or is their benefit to thinking of profile in different terms of MMC and LMC, that might help control tolerance stack up of other nominals?
Hi, that’s a great question. I recommend keeping all tolerances as equal bilateral, whether plus minus or geometric. It makes things easier for programming CNC and for tolerance stackups. Since the limits are absolute, there is no practical or theoretical difference between a unilateral or equal bilateral tolerance as long as the decimal places are the same.
@@RDeanOdell Thank you for the response! As well as the great content!
Great video. If I want to check the shape and position of a machine part relative to the perfect shape of my CAD model that includes this machine part, I use the "0.75 with respect to ABC" principle, right? and if i only want to control the shape of the features but not the position of the features i use the .01 in your video at about 23:40 or if just want to know the shape I put .01 without referring to datums? I want to control the "internal" shape, or how to express it, because its a sealing surface.
Edit: I think you talk about what I mean it in this video czcams.com/video/ZteA93KsKB8/video.html , controlling the shape but it can "float" around a bit regarding position.
Another question: Do you have something about unilateral straightness? if there is such a thing.
Greetings from Sweden 🙂
thank you
hi Dean... can't we use H7/G6, H7/k6... all the fit tolerance in gd&t
Hello Sir, Could you make a video about projected tolerance zone? I found it hard to understand what is meaning of it, and when we apply it to the design. Thanks
Hi, I just released a video on projected tolerance zones based on your question.
Thank you, you’re amazing!
perfect :)
Thanks!
You’re very welcome! Thank you!
Hiiii!
at 18:05 👌