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David Slopsema
เข้าร่วมเมื่อ 15 มิ.ย. 2012
This is a channel about Geometric Dimensioning and tolerancing as specified in the ASME Y14.5 Standard
วีดีโอ
Boundary, Maximum material
มุมมอง 4512 ชั่วโมงที่ผ่านมา
This video explains the definition of Maximum Material Boundary
Boundary, Least Material
มุมมอง 2312 ชั่วโมงที่ผ่านมา
This video explains the definition of Least Material Boundary
What is Angularity per the ASME Y14.5 2018 Standard
มุมมอง 42วันที่ผ่านมา
This video explains the term angularity and contrasts it with angularity tolerance.
What are basic dimensions vs reference dimensions
มุมมอง 39วันที่ผ่านมา
This video describes what basic dimensions are and what reference dimensions are. My hope is to clear up the confusion people have about them.
Calculating RMB per figure 7-24 from ASME Y14.5 2018
มุมมอง 51วันที่ผ่านมา
This video explains how to calculate the RMB for various scenarios shown in figure 7-24 of the ASME Y14.5 2018 standard
Calculating LMB per figure 7-23 from ASME Y14.5 2018
มุมมอง 4114 วันที่ผ่านมา
This video shows how to calculate LMB for the various scenarios shown in figure 7-23 of the ASME Y14.5 2018 Standard
Calculating MMB per figure 7-22 from ASME Y14.5-2018
มุมมอง 13214 วันที่ผ่านมา
This video explains how MMB is calculated in Figure 7-22 in the ASME Y14.5 2018 Standard
Flatness tolerance applied to a surface is unilateral
มุมมอง 45หลายเดือนก่อน
This video examines flatness tolerance applied to a surface. It is not centered, it is not plus and minus. It is unilateral.
Part 3 of datum features constraining degrees of freedom - datum sequence
มุมมอง 126หลายเดือนก่อน
In this video, we see how switching the datum sequence affects which datum features constrain which degrees of freedom
Part 2 of datums constraining degrees of freedom pattern datums
มุมมอง 94หลายเดือนก่อน
This video shows how a planar datum primary and a pattern datum secondary constrain the six degrees of freedom
Part 1 of constraining the six degrees of freedom with datum features
มุมมอง 178หลายเดือนก่อน
This video describes how to constrain the six degrees of freedom with three mutually perpendicular planar datum features.
Features of size controlled by multiple feature control frames
มุมมอง 83หลายเดือนก่อน
This video shows how features of size, when controlled by multiple feature control frames, must meet all of the requirements of all of the feature control frames. It shows the gages necessary for meeting those requirements.
Perpendicularity tolerance is not evil. Please use it!
มุมมอง 200หลายเดือนก่อน
This video shows why perpendicularity error should be controlled with Perpendicularity tolerance and not with position tolerance.
Part 3 of datums, datum features, datum feature simulators, and simulated datums
มุมมอง 952 หลายเดือนก่อน
Part 3 of datums, datum features, datum feature simulators, and simulated datums
Part 2 of datum features, datum feature simulators, and datum reference frames
มุมมอง 562 หลายเดือนก่อน
Part 2 of datum features, datum feature simulators, and datum reference frames
Datums, datum features, datum feature simulators, and datum reference frames.
มุมมอง 522 หลายเดือนก่อน
Datums, datum features, datum feature simulators, and datum reference frames.
Stop confusing datums, datum feature symbols, and datum targets
มุมมอง 1062 หลายเดือนก่อน
Stop confusing datums, datum feature symbols, and datum targets
Using simultaneous requirements to help your design
มุมมอง 622 หลายเดือนก่อน
Using simultaneous requirements to help your design
Self paced Fundamentals of GD&T training
มุมมอง 563 หลายเดือนก่อน
Self paced Fundamentals of GD&T training
What's your facebook?
你好，你从事过GD&T和CMM工作吗？
Hello sir i am beginning to GD & T. Please guide me on how to learn it and how to apply it as a fresher mechanical designer.
Just keep watching my videos. I plan to keep posting. I also have a pretty comprehensive presentation of GD&T on at this URL: www.dimensionalconsulting.com/free-online-textbook.html
C yanlış yerde. C en uzun mesafe olmalı. Rotasyon en uzun yerden yapılmalı.
Thanks David for perfect video. What is the change if we add profile tolerence ? Both of them make same job ?
Profile tolerance without any datum references would do exactly the same thing. Profile tolerance with datum references could do a lot of different things. I'll have more videos coming about that.
Could you please add video also about mathematically defined surface, why we use it ? Usage example etc .( asme 4.13)
Sir, nice lecture. Is this Datum B calledout on surface of cylinder or axis. Also at 1:05 ,what is the gauge size if Datum B( RFS ) and B(MMC).How it is changing in both condition.kindly a replay.
Datum feature B is the pin. Datum B is the axis of the pin.
If datum feature B were referenced MMB, the gage would have a fixed size hole, but we don't have enough information on the drawing to calculate the size of the hole in the gage. As it is, with datum feature B referenced RMB, the hole in the gage is a variable size so that it can exactly surround the pin with no looseness.
@@davidslopsema4374 ok thankyou sir, for valuable replay
You're the legend❤
I love it. Respected sir, please continue this series through a step by step so that fresher mechanical engineer like me learnt it in a practical way. Salute to you 🫡
谢谢！
Not sure I understood this correctly but will rewatch later when i have slept. Nonetheless thanks for the video!
yup
I'm not familiar with this but I love it
Thanks for sharing!
I have some questions regarding pattern as datums. Do you have any socials through which i can contact you?
Amazing Explanation, Thanks Dave>
why the heck would you take a pic of dog crap and put it in a video...sick
How about threaded holes with inserts?
Haló haló??
Hello Sir, Thanks for the explanation. I have one question. What to do if we exceed the stack line. i.e, what to do when I need to add additional stack line after 40 stack lines are consumed ? Please help.
It is not expandable past 40 lines. You would need to divide your stack up into two stacks and add the results.
I know it was not covered probably because the focus of video was something else, but how do they know where to put those holes to begin with? Even if the basic dimensions are put there, we need some another datum feature frame, only for positioning the four holes? No?
Brilliant
Can a pattern of slots be used as datum feature? Thanks
Just sent over an email. Hope to hear back. Thanks for the information on the website.
Good information on tolerance "Stack-up" and that is very useful with "GD&T" and mechanical design-CAD. Thanks for all the work you do! Hope to see more down the road! T J (Tom) Vanderloop, Author, Technology-Instructor & Mechanical Designer; ATEA, AWS & SME Leader/Memberships
Good analogy for the "Dog-Lovers" as shop-workers, the use of Profile is Awesome! T J (Tom) Vanderloop, Author, Mechanical Designer, & Consultant: ATEA, AWS & SME Member
Hmm, ok, let's say I dimension a part with a pattern as datum and then go to assess my real part. Let's say your limited in the same way our inspection department is, and need to use a caliper. I pick one of the four holes randomly. I can check its size, but there's no position requirement yet. Let's say I conclude that the hole size is acceptable. I move onto the next hole. Can that hole's position now vary within its position tolerance, or, within its position tolerance PLUS the position tolerance the first hole could vary within given the single feature control frame??
You consider the first hole to be the center of the universe, and then with the other holes calculate position plus bonus plus datum feature shift. You can avoid a lot of calculations if you can have your inspection department give you hole sizes and locations and you can create a gage in CAD and create the part as measured in CAD and see if the part as measured fits on the gage in CAD. I explain this on my web page here: www.dimensionalconsulting.com/tolerance-of-position.html#cmm Otherwise if you need to do the calculations manually, I explain how to do that on my web page here: www.dimensionalconsulting.com/tolerance-of-position.html#advanced
@@davidslopsema4374 awesome. I'll take a close look. Thanks!
Thanks, this helped me to visualize LMB
What if i have regardless material condition and regardless boundaries call out in gd&t means plz
You will have no bonus and no datum shift, only the position tolerance in the feature control frame regardless of the actual size of the features.
Other than being cleaner and “explaining” the intent better, what are the other quality manufacturing problems that the first examples bring?
I have seen this issue causing confusion when people do tolerance stacks. Other than that, I cannot point to any specific quality problems that it causes. It's just a matter of making the GD&T reflect how the part really functions.
Good tip, but for this example wouldn't you want to use MMC on the perpendicularly & position tolerances to take advantage of bonus (additional) tolerance, & MMB on datum features of size B & C to take advantage of datum feature shift?
Yes you would, if you want to allow bonus and shift, and/or if you want to use fixed size gage pins. If for some reason you could not tolerate the bonus and shift, then you would leave it RFS and RMB. It all depends on your product requirements.
<3
haha...intresting
LOVE the video. One question - despite the side of the feature that the arrow points to, is the number following the U symbol always OUTSIDE of material? Example - what if the scenario was pointing to the inside of the feature? Lastly - if you didn't reference datum features, would the profile become only a feature size control? Thanks!
Yes, the number following the U symbol is always outside the material. So if it were pointing at a hole, the number following the U symbol would allow the hole to get smaller. It can indeed control the size of a feature, but I still would not call it a feature of size. A feature of size always has a coordinate tolerance controlling the size.
Is there a method of reporting profile error using variable data? Historically, the formula used was max - min if crossing nominal or if all positive or negative error is observed, 2*max deviation from nominal.
I am not familiar with a standard method of reporting the data. I am guessing that would be determined by whoever requires the data.
I have used the method of reporting my tolerance / my deviation from tolerance. Example for bilateral would be +/- 0.25 / over / actual result. The result could be anything from + to - 0.25. Also - if you wanted to, you could report in the basic feature box the range that you found. Example: Feature is 40mm and you report 39.8 - 40.22 (all acceptable applying that tolerance). Make sense?
I forgot - when I do report actual readings in comparison to the basic features I do NOT accept or reject that data. The accept reject criteria is reported in the profile callout.
Please visit my web site at www.dimensionalconsulting.com
Please visit my web site at www.dimensionalconsulting.com
Please visit my web site at www.dimensionalconsulting.com
Please visit my web site at www.dimensionalconsulting.com
Please visit my web site at www.dimensionalconsulting.com
Please visit my web page at www.dimensionalconsulting.com
I enjoyed your video, however I can't find where to download the PDF file your talking about. Can you please advise me. Thanks
The "Closed Loop" stack up method is much easier to work with.