As an R&D engineer, it's quite fun to watch your lectures and repeat the details of GDT, I hope you'll continue to share new topics! All the best Professor!
I'm glad you are enjoying the review! I will be sharing new topics, but it takes me some time and focus to get a lecture to the level I want it before posting. I'm teaching circuits for the first time this fall, and I hope to generate a few videos while going through that course. Thanks for watching!
Thanks for your kind contribution! I have gotten pretty busy with many other things besides video making, but I do still plan to put out another video or two in the GD&T space! Thanks for watching!
The fact that I fully comprehend how composite (PLTZF & FRTZF) vs multiple single segment FCF yield subtly different results on first watch… exceptional clarity!
I have truly understood the feature control frame with respect to the location of the hole and the allowed tolerance that dictates the exact location of the hole. Due to the fact a diameter symbol is being used to relate to the location of the hole and a callout for positional tolerance, I was mixing up it to the diameter symbol of the actual size of the hole and its associated tolerance call out. Your video has cleared that for me and now I can really understand the examples that are in the GeoTol Pro book by Scott and Al Neumann. Nice work explaining.
Over the years, I've studied numerous video compilations devoted to GD&T but always gravitate back to the TheBom_PE series. Anyone interested in learning GD&T from scratch should watch this video series in order and read Chapter 20 on GD&T in Shigley's Mechanical Engineering Design. I cannot think of a more thorough and comprehensive starting point.
I just found this channel, and I wanted to say that I'm very glad I did. The concepts are explained well, and are easy to digest. Thank you for creating content like this. Please keep up the great work.
Thank you, you are very kind! Here are some of my other playlists in case you haven't seen them yet and might be interested: ENGR122 (Statics & Engr Econ Intros): ru-vid.com/group/PL1IHA35xY5H52IKu6TVfFW-BDqAt_aZyg ENGR220 (Statics & Mech of Mat): ru-vid.com/group/PL1IHA35xY5H5sjfjibqn_XFFxk3-pFiaX MEMT203 (Dynamics): ru-vid.com/group/PL1IHA35xY5H6G64khh8fcNkjVJDGMqrHo MEEN361 (Adv. Mech of Mat): ru-vid.com/group/PL1IHA35xY5H5AJpRrM2lkF7Qu2WnbQLvS MEEN462 (Machine Design): ru-vid.com/group/PL1IHA35xY5H5KqySx6n09jaJLUukbvJvB (MEEN 361 & 462 are taught from Shigley's Mechanical Engineering Design) Thanks for watching!
Thank you for the great videos!! Your videos are extremely helpful and your way of explaining makes it easier to understand. We look forward to new videos in this series.
I'm glad I could provide something useful! As a note, I plan on redoing this lecture soon. There are some things in here I want to correct and do better. Thank you for watching!
This is great! I wish you'd give more examples and explain more thoroughly the difference between the gray and purple on 1:02:00 min on the lecture. For example, from what I understand, if you took off datum B of the gray option, it would be exactly identical to the purple option. Am I right?
Sir without a doubt your lectures are miles away but we need more of your lectures in action. Please go for some more outstanding concepts and questions
I'm still working on some more content! I would like to address surface roughness in one of them, but I don't have a timeframe for that just yet. Thank you for your interest though!
Great Lecture Professor. Thank you about that video! I have only one question. About Multiple Single Segment FCF, If we have a circular pattern of holes and we want the framework to rotate but not to transfer along B, and C datums, then how can describe that? Thank you in advance!
ISO 5459 says a feature of size can be: The features of size can be a cylinder, a sphere, two parallel opposite surfaces, a cone or a wedge. So in this case a cone or wedge can be either. However they do not fulfill the definition of 2 opposite surface, or be a cylinder or sphere. Is it different from ASME? In ASME only the one of the section so a circle could be a feature of size. For example if I have molded parts with truncated holes/pins, then what is the feature of size? The smallest (base) circle of the hole and the biggest one for a pin? I do not understand how to use position tolerance for cones, wedges. Moreover how to use modifiers for them like MMC/LMC/MMB. Thank you
Hi Professor, It's so helpful. Can you please do more videos of mechanical designs and also tooling, maybe a bit Additive Manufacturing lectures? Please!! all the best
Here are a few videos you might be interested in: Power Screws: ru-vid.com/video/%D0%B2%D0%B8%D0%B4%D0%B5%D0%BE-zgIPRXd0rBM.html Journal Bearings: ru-vid.com/video/%D0%B2%D0%B8%D0%B4%D0%B5%D0%BE-UGthutGbDCo.html ru-vid.com/video/%D0%B2%D0%B8%D0%B4%D0%B5%D0%BE-U6MYvY0ST8Q.html Choosing Ball Bearings: ru-vid.com/video/%D0%B2%D0%B8%D0%B4%D0%B5%D0%BE-cU0wQHcYSSU.html Drum Brake: ru-vid.com/video/%D0%B2%D0%B8%D0%B4%D0%B5%D0%BE-MLmomyoCZp4.html Playlists based in Shigley's Mechanical Engineering Design, 10th edition: ru-vid.com/group/PL1IHA35xY5H5AJpRrM2lkF7Qu2WnbQLvS and ru-vid.com/group/PL1IHA35xY5H5KqySx6n09jaJLUukbvJvB All the best to you!
Hi Doc, reaching out for a doubt. What is criteria that decides on whether a material condition would be allowed on any of the geometric charatceristic. Ref: Table at 25:42. Also thank you for all the value you are putting in through these series and others.
I'm glad you're finding the content useful. The shortest way to answer your question is that my focus in this series is primarily on the ASME Y14.5-2009 standard, and those are the rules in that standard. Your question may be about the underpinnings of the rules, but the answer on that would have to get into each control and might be a bit too involved to answer here. Thanks for watching!
If that tolerance is one hundreds of an inch it should be written without zero in front of decimal point, placing zero in front makes it metric. Check out 1.6 Types of Dimensioning (Y14.5-2009 page 9)
hello professor. i got a question. as far as i know, rule #1 only ensures perfect form at mmc. but it seems in the video that you say there are perfect forms at both mmc and lmc. are you sure of this?
In this video I'm using an HP Zbook X2. For many of my videos I use a Fujitsu T901 with a gen2 i7, nvidia graphics, and 16GB ram. Both computers have Wacom digitizers, and that is one of the the keys to good inking experiences IMO. As far as software, in this video, I'm using PowerPoint. Most of my videos, though I use OneNote as the software. Maybe this helps?
I believe you are asking how designers should go about determining appropriate tolerance values to specify. I will try to show a little bit of this in upcoming lectures, but there is a good bit of art to this that good designers generally have to learn through experience.
@@TheBomPE thank you. Yes, you are right as a product designer it is very difficult everytime to know the manufacturing process capability for different machines. But as we have to define our tolerance value for position, perpendicularity, angularity, flatness and similarly for other gd&t symbols. Please cover these things also in your upcoming video with the live example.
Again, I will try to show some more examples in upcoming lectures that will [hopefully] illustrate some effective uses of GD&T techniques and annotations. But I will also confirm that good technique generally requires awareness of the capabilities and limitations of the tools that will be used to make and inspect the parts. I will reiterate that as you gain experience in designing, your art will improve with respect to minimizing cost via your tolerances while maintaining reliable part and system functionality.
GD&T provides a language and a system to specify how much deviation from desired geometry is acceptable. It is more or less agnostic regarding the specific manufacturing methods used to achieve the part geometry.
@@eartheartbaratheon791 Actually there is tolerance stackup for GD&T. It relates for example to how 2 matting parts will be able to fit with a position tolerance for each corresponding holes.
@@TheBomPE Great, thank you sir. Is there anyway you could make the PPT files accessible to your subscribers? It would be easy to make notes and study.
I'm doing ok, I've just gotten very busy with other responsibilities. Teaching 100% online has required me to spend time and effort in ways I haven't needed to before, and it hasn't translated into steady video output. Also, working from home is not quite as efficient due to many distractions. Plus, RU-vid isn't the most lucrative way to spend my effort! :) oh well. I'm working on one that should be ready soon though!
i disagree with you that position control does not control the form. actually in your examples, position control tolerances are larger than form controls. in that case, the tighter form controls controls the shape. however, if your position controls are tighter than the forms, they dictate the forms as well. in general, position controls form and orientation. orientation controls form and orientation, form only controls form. Thus, it is the most common to have the most relaxed tolerances for position tolerances.
position only controls orientation, not form. Otherwise you'd be unable to use position on a conical feature whose ends are concentric and share a common axis, the exterior of the cone feature could be rough, or casted, but still maintain a closely tolerance axis perpendicular to another feature. In such a case I don't care about the variation in the form of the part, only the orientation and perpendicularity of the axis. The actual form may deviate by +/- .100", but I'm not concerned about that, I just want the axis orientated precisely. The position control, controls a the location and orientation of a point, axis or center plane of a feature and nothing else. No form control is implied. Only the size of the feature, or a separate from control, will control the form of the part.
