Archive > 2015 > February 2015 > Desktop Engineering - How to Calculate Dynamic and Static Load Ratings

Desktop Engineering â€“ How to Calculate Dynamic and Static Load Ratings

Introduction When comparing bearing suppliers, engineers are often left with few options other than to compare dynamic load ratings and corresponding life calculations. Of course, we can look at steel and manufacturing quality; but if we are comparing sources of similar quality, those items may not provide a large contrast. It often surprises people to learn that bearing capacities are calculated values, not tested values. Lately, however, a trend is emerging for bearing suppliers to increase their ratings for higher performance bearings that have premium features such as higher quality steel and specilaized heat treatment. Bearing companies are under intense competitive pressure to make every feature add to the dynamic capacity of their bearings because it is very well understood that an increase in capacity adds to the bottom line. As a result, it is important that the end user develop a keen understanding of how capacity ratings and subsequent life calculations are generated in order to make a true comparison, or be left to comparing the claims of well-heeled marketing departments.

Dynamic Capacity

Nearly every calculation surrounding bearing life begins with the dynamic capacity, Cr. Cr is the equivalent load that would result in an average service life of one million revolutions. The formula is imperfect and standard bearings arenâ€™t designed to handle 100% of Cr; but, those are annoying nuances we have to understand and live with. In the past, most bearing companies would follow the dynamic capacity formula to ISO or ABMA standards and then increase the resulting life calculation by some factor based on heat treatment and other premium features in addition to the increase that would come through ISO 281 or 16281 using a-iso factors. The issues that end users have with this is that enhanced life calculation factors are not always shown on the bearing print and the print is the primary legal document that exists between the end user and the bearing manufacturer. Some end users interpret this as being an escape route for the bearing companies if something goes wrong â€“ which it is not. Consequently, the competition and end users are pushing bearing companies to increase capacity ratings on the print. This is where the math starts getting fuzzy. We will walk through the formula with a couple of real bearings and determine where these numbers are coming from. The ISO/ABMA Cr formula:

For this example, letâ€™s look at two high-quality competitors, each producing their own design of the HM804846/10, a popular inch-series tapered roller bearing. Weâ€™ll refer to these as Company A and Company B.

Figure 1 Company A(Left), Company B(Right).
Figure 2 Measuring major and minor Inner raceway diameters for Dpw.

Right off, we see bm is defined by ISO as 1.1. For i, both bearings have 1 row; i = 1. The bearing half-angle, a, will be provided by the manufacturer, so we can skip that measurement. Both of these bearings are around 20Â° (though a side-by-side comparison clearly shows they are not identical angles). Z, the number of rollers, is easy enough to count â€” both have 18 rollers. The remaining values â€” fc, Lwe, Dwe and Dpw â€” are often not provided, but we can physically measure these features. Customer models will typically leave off just enough features to prevent an accurate measurement. We could get fancy and have these set up on a CMM and measure to 3 decimal places, but if you glance at the load ratings in the catalog you will see everything is rounded to the nearest 500 N. None of these factors will change your results greater than the rounding error if you are within 0.5 mm of accuracy. This sounds like a job for calipers.

We will skip fc for now because that is a tabulated value which we need two of our other unknowns for. Letâ€™s start with the effective roller length Lwe. ABMA defines Lwe as:

The theoretical maximum length of contact between a roller and that raceway where the contact is shortest. NOTE: This is normally taken to be either the distance between the theoretically sharp corners of the roller minus the roller chamfers, or the raceway width excluding the grinding undercuts â€” whichever is the smaller.

Figure 3 Measuring roller length for Lwe.
Figure 4 Measuring roller ends for Dwe.

The roller chamfer can be be hard to identify with the naked eye, and will usually involve a little guesswork.

Usually, the Lwe will be 1-1.5 mm shorter than the entire length of the roller. We can check ourselves before we are done, so donâ€™t worry too much about your estimate for now. For a 21 mm roller, an Lwe of 19.5 mm is a good guess.

Now on to Dwe â€” the mean roller diameter. This is very straightforward; measure the large diameter at the bottom and the small diameter at the top and average the values for Dwe.

The final measurement, Dpw, is also fairly simple. Dpw, the pitch diameter of the roller set, is the theoretical centerline that the rollers run on. This is measured in similar fashion as were the rollers; measure the large and small diameters of the inner ring raceway; take the average to find the diameter in the center, and then add 1 Dwe to get the pitch diameter at the center of the rollers, at the center of the raceway.

With those values measured, we can now find fc, which is a tabulated value based on the quotient.

For example, Company A
Dwe = 10.2
Dpw = 71.2
a = 20
The quotient calculates to:

Letâ€™s compare our values and results:
Plugging these values back into the formula:
Cr = 1.1 Â· 87.4 (1 Â· 21.3 Â· cos 20)7/9 183/4 10.229/27
Cr Company A: 104,675 N
Cr Company B: 106,144 N
If your calculated value is more than 1% different than the published value, adjust the Lwe until the calculated Cr matches the book value.

Figure 6 Measured values for Co;s A and B

Static Capacity

By definition, the static capacity Cor is the calculated maximum-recommended static load value which loosely represents the yield point of the bearing steel. Ideally, this value should represent peak stress levels around 4,000 MPa â€” the ISO-recommended stress limit. Just due to geometry, the highest stress will occur on the inner ring/roller interface. The ball-ball contact between the inner ring and roller has a smaller contact area than the ball-socket contact pattern on the outer ring. Cor is a useful maximum load value if you donâ€™t have bearing software to calculate actual stress values. The benefit with using stress values is that the effects of crowning can be taken into account, and if the bearing has premium heat treatment features that produce a harder surface, stress values up to 4,200 MPa or higher may be permissible. Comparing catalog values of Cor can be very useful because there are no places to add non-standard factors; the formula is completely based on geometry. If you need a quick comparison for the physical amount of steel contact between two different bearings, forget Cr â€” Cor is what you want to compare.

The other good news is, if you collected your Cr values, you already have everything you need to calculate Cor .

Cor Company A: 139,926 N
Cor Company B: 142,337 N
If a bearing company wanted to increase the static rating on paper for a premium bearing, they could easily justify using a 4,200 MPa as a baseline for their rating, though it is not standard ISO/ABMA practice and not a fair comparison to another company that is strictly following ISO standards.

Letâ€™s compare all of our calculated values next to the published catalog values for both companies.

The calculated values for Company A came within 1% of the published values. However, something is quite different with Company B; the published Cr is 38% higher than our calculated value and the published Cor is 10% higher than our calculated value. Company A claims to have similar quality and performance as Company B, but we certainly cannot ignore the fact that Company B has a 41% higher Cr and a 12% higher Cor. This is a significant difference between two relatively similar bearings. What is going on here?

Company B claims that they have lab-tested proof to show that their increased Cr is legitimate and they do not want to be held to an artificially low ISO or ABMA formula, and therefore do not adhere to the standards. On the other hand, Company A claims that they are able to add a performance factor to the calculated L10 life that will give them nearly the same calculated life as Company B. Letâ€™s revisit the basic L10 formula so that we can play along:

Figure 7 Calculated vs. published values

Where L10 is measured in millions of revolutions and P is the applied load. Mathematically, an increase of X in Cr does this:

While a performance factor does this:

Because Cr is raised to the exponent of 10/3, a small increase nets large increases in calculated L10. Letâ€™s see what type of performance factor a 38% increase in Cr would yield:

This means that company A could multiply their calculated L10 by 3.2 times and effectively match the results of Company B. Company A states they are comfortable going with a performance factor of 2.6, but not 3.2 (Note: Until recently, Company B had a Cr of 141 kN that was exactly equivalent to a 2.6 performance factor. Two completely separate companies coincidentally had performance factors of 2.6). What the end users want the bearing companies to do is take the 2 or 2.6 performance factor and increase Cr by that amount on the print rather than just increasing the calculated L10. For example, a performance factor of 2 would mean:

Let Cr/P = 1, then X = 1.23. This means that every 23% increase in dynamic capacity doubles the calculated life. End users want to see 1.23 Ă— Cr, rather than 2 Ă— L10. The perceived benefit is that the increased Cr is shown on the print â€” which is a legal document. The risk in doing this for the bearing companies is that, right or wrong, some engineers are accustomed to designing to rules of thumb based on the published Cr. If Cr is artificially increased on the print, these practices may very easily result in a bearing that is under-designed for the application in terms of operating load and peak static stress.

The increased rating for Cor is easier to explain. As mentioned earlier, if you calculate the load required to reach a higher-than-ISO-recom-mended peak stress value of 4,000 MPa, you can easily justify the higher rating on the print. Though again, this is not standard practice.

From here it becomes difficult to make a rational decision, because there seems to be a lot of subjectivity going on with the calculations. We have tested vs. calculated dynamic load ratings, performance factors that have questionable origins, and less-than-obvious methods of increasing static load ratings. Recall the earlier statement that the static load rating calculations can be valuable for comparison. If we only compare our calculated static capacities (recall, true steel on steel contact area) we see a marginal difference of only 1%.

With that, we absolutely know that we have similar amounts of surface contact area. Armed with the knowledge that we have comparable geometry between the two bearings, the only real performance difference should be in the rolling fatigue performance of the steel. Again, we are assuming these are both top-shelf companies, so bearing design, manufacturing quality, surface finishes, etc., should be comparable. All of the fancy calculation methods beyond this point are useless for comparing these two bearings; only dyno or field performance tests over the entire loading range will conclusively separate the two. These formulas are easy to set up in a spreadsheet format that will facilitate future comparisons and provide real insight when dealing with your bearing suppliers.

Conclusion

There is an undeniable level of comfort when you see a huge capacity rating on a print that puts your safety factors well into â€śgood nightâ€™s sleepâ€ť territory. It can be argued that both Companies A and B have valid points in the way they handle the premium features. One does not want to be held to capacity ratings that they can outperform by 50%, and the other does not want to deviate from the standards.

The main point of this article is to show that load ratings are based on simple formulas that you can calculate on your own. You should ask a prospective supplier if their capacity ratings and life calculations are based on ISO 281:2007 and ISO 76:2006. If not, you need to completely understand how and why they are using their value. Likewise for any performance factors added to the calculated L10 life; double-check their work and ask questions. Secondly, a supplier is not off the hook just because they donâ€™t put their performance factor on the print. If their calculations are well-documented with all of the latest information you gave them, their analysis is a legal form of communication (though be forewarned â€” contamination levels, temperatures, alignment, roundness of shaft and boresâ€¦all of the factors that go into ISO 281 are subject to review). Finally, capacity ratings are pushed from an engineering and marketing perspective. Companies are expected to live up to their ratings, but with the wide scatter of failure points in any type of fatigue test, it can be difficult to pinpoint a true 20% difference during bench or field testing with a limited number of parts. We need to account for genuine high-performance features on our bearings because we use those factors in our designs. Just be sure that you know how to compare the different methods being used to account for those features.

Norm Parker is the bearing technical specialist for the driveline division at General Motors LLC. Located onsite at the Milford (MI) Proving Grounds, he is regularly tasked with testing theoretical models in the real world, in real time. With his bachelor and master degrees in mechanical engineering from Oakland University (Rochester, Michigan), Parker has developed a keen interest in the academic, commercial and engineering aspects of the bearing industry. Prior to joining GM, he rose through the ranks of traditional bearing companies; by so doing he acquired invaluable experience in working with some of the largest customers â€” with the toughest applications and demands â€” on the planet. Parker plans to continue expanding his expertise and providing substantial personal contributions to bearing technology through metallurgy, design and processing.

References

1. Brandlein, Eschmann, Hasbargen and Weigand. Ball and Roller Bearings: Theory, Design and Application, Third Edition, Wiley & Sons 1999.
2. International Organization for Standardization. Rolling Bearings: Static Load Ratings,
3. ISO 76:2006(E), ISO 2006, Third Edition, 2006-05-01.
4. International Organization for Standardization. Rolling Bearings: Dynamic Load Ratings and Rating Life, ISO 281:2007(E), ISO 2007, Second Edition 2007- 02-15.
5. American Bearing Manufacturers Association. Load Ratings and Fatigue Life for Roller Bearings, ANSI/ABMA 11:2014 (Revision of ANSI/ABMA 11:1990).

The article "Desktop Engineering - How to Calculate Dynamic and Static Load Ratings" appeared in the February 2015 issue of Power Transmission Engineering.