I went back to be sure I hadn't read the book wrong.
Vaughn never actually wrote the 500 ft-lbs number. I calculated that using his equation applied to the geometry of my barrel joint. I asked myself if I calculated it wrong. I could have.
I had done a quick calculation while drinking a cup of coffee and eating a cookie (I'm a cookie monster) and I might have gotten it wrong. I don't usually, but if I had it wouldn't have been the first time. I found the scrap of paper in the wastebasket, double checked what I did, and using Vaughn's published equation and friction factor I got the same number, 471 ft-lbs which I rounded up to 500 ft-lbs. I also noticed that he says in one place that 250 ft-lbs gives him about 10,000 pounds of preload which, even though he had a different thread pitch, correlated with what I got doing the math. OK, I did the math right.
Studying the equation, there is one coefficient in it, the coefficient of friction between the mating surfaces in the joint, that is a bit uncertain. He used 0.24 lb/lb, and so did I when I ran the numbers. I wasn't expecting a debate (though i should have been
) so I just used his number.
I looked that coefficient up in Machinery's handbook and found that number to be on the high side. Most values for lubricated metal are between 0.07 lb/lb and 0.15 lb/lb. So I did some parametric evaluation of the equation, that is, I substituted different likely values of friction coefficient, and got some interesting numbers.
In the table below:
- Tmax is the torque in ft-lbs to get to 20,000 pounds of joint preload, which Vaughn says is about all the threads will take based on his analysis of the strength of the threads.
- F is the axial preload in pounds resulting from 150 ft-lbs of applied torque.
- f is the friction coefficient in lb/lb. The conditions for the friction coefficient are at the end of each line - from Machinery's Handbook, 25th edition, page 1403. This is for bolts and nuts, but it should be close.
- f=0.24 lb/lb Tmax=471 ft-lb F=6,336 lb This is Vaughn's value for friction factor.
- f=0.15 lb/lb Tmax=300 ft-lb F=10,000 lb This machine oil lubricated steel
- f=0.11 lb/lb Tmax=224 ft-lb F=13,440 lb Moly disulfide grease
- f=0.07 lb/lb Tmax=150 ft-lb F=20,042 lb Graphite in Petrolatum or Oil (AKA Assembly Lube, which is what I used)
Sorry the table is so hard to read, but this forum editing sw isn't table friendly.
That being the case, this second assembly has the threads at some place between 13,440 and 20,000 pounds of preload, probably closer to 20,000, which is about as close to perfect as one can get if the goal is 20,000 pounds but no more. The first time I assembled it I was probably closer to the 6,300 pound number because the joint had only residual oil lubrication. I was lucky I didn't gall the threads! I won't do that again. I used the assembly lube the second time mainly to avoid the possibility of galling since it is a stainless nut on a stanless barrel. Assembly Lube is good stuff. Gritter's uses a lube sort of like it in his video. Ed Franklin doesn't.
I wish I had done this evaluation before I torqued the joint, I would have if it was going in a space craft, but the end result, serendipitous as it was, is about as good as I could have gotten, so I'll take it.
Standard practice, as I pick it up here based on the discussion that accompanied the "snap tite" discussion, is to torque to around 100 ft-lbs. Depending on what lube is used, this results in between 6,674 and 13,610 pounds of preload. That may be enough given the reduced forces from the relatively wimpy (compared to a .270Winchester) bench rest cartridges. It may also be that some of the high end bench rest folks, who don't publish what they are doing, are using torque values closer to 150 ft-lbs and assembly lube, which gets them up much closer to 20,000 ft-bls.
I don't have any indispensible ego attached to any of this, so have at it.
Fitch