AGMA 14FTM05-2014 A Different Way to Look at Profile and Helix Inspection Results.pdf

《AGMA 14FTM05-2014 A Different Way to Look at Profile and Helix Inspection Results.pdf》由会员分享，可在线阅读，更多相关《AGMA 14FTM05-2014 A Different Way to Look at Profile and Helix Inspection Results.pdf（7页珍藏版）》请在麦多课文档分享上搜索。

1、14FTM05 AGMA Technical Paper A Different Way to Look at Profile and Helix Inspection Results By J.M. Rinaldo, Atlas Copco Comptec LLC 2 14FTM06 A Different Way to Look at Profile and Helix Inspection Results John M. Rinaldo, Atlas Copco Comptec LLC (The statements and opinions contained herein are t

2、hose of the author and should not be construed as an official action or opinion of the American Gear Manufacturers Association.) Abstract The traditional inspection of involute gear profile and helix deviations results in plots of deviations from a perfect involute and from a perfect helix. While th

3、is is appropriate for gears with an unmodified profile or helix, it is not ideal for gears that have intentional modifications. This paper explores the advantages of looking directly at deviations from the design shape. This type of analysis is implied but not explicitly stated nor is it pictured in

4、 ISO 1328-1:2013. Also presented is a modification to zone based tolerance evaluation as presented in ISO 1328-1:2013, with limits on the total deviation from design given graphically. Copyright 2014 American Gear Manufacturers Association 1001 N. Fairfax Street, Suite 500 Alexandria, Virginia 22314

5、 October 2014 ISBN: 978-1-61481-097-1 3 14FTM06 A Different Way to Look at Profile and Helix Inspection Results John M. Rinaldo, Atlas Copco Comptec LLC Introduction Elemental inspection of gears is commonly carried out with computer numerically controlled (CNC) machines. While these range from spec

6、ial purpose gear measuring machines with a precision rotary table to 3-axis co-ordinate measuring machines (CMM) with software adapted for gear measurement, what these inspection machines have in common is they produce graphical output that shows deviations of the profile from a perfect involute and

7、 deviations of the helix from a perfect helix. For gears designed without any profile or helix modifications, this is appropriate and sufficient. However, it has become very common for gears to be designed with a design profile that deviates from a perfect involute shape and a design helix that devi

8、ates from a perfect helix 1. For these gears, a graphical output showing deviations of the profile from the design shape can be very helpful. Background and proposal The proper specification of design shape is very important for the proper performance of the gear. Design shape modifications may be u

9、sed to improve the noise, vibration and harshness (NVH) of a gear set, prevent tooth collisions in heavily loaded gears, compensate for changes in tooth shape due to shaft bending and thermal deformation that occur during normal operation, or for other reasons. In many gears, proper tooth shape modi

10、fications are essential for both smooth operation and long life 2 The designer specifies what the tooth shape should be, but it is then up to the machine operator or inspector to verify that the design intent has been met. Unfortunately, for gears with modified profiles, typical gear charts require

11、a high level of expertise to properly evaluate how the gear deviates from the design shape. What is proposed here is that since the design profile is the ideal shape, the deviations from the design profile should be displayed in addition to the deviations from a perfect involute. No additional data

12、collection will be required, it is simply an alternate method to display the data gathered by an inspection machine. Graphical displays of deviations from the design shape are much easier to evaluate, and can be a very useful addition to the inspection processes. These deviations should of course be

13、 zero, so the plot of deviations from design profile should be a straight line coinciding with the axis. These new charts are not intended to be a replacement for traditional charts, but rather an additional chart that in combination with traditional gear charts will make understanding of the deviat

14、ions much easier. Each method of display has its own advantages; used together they can quickly lead to a full understanding of the deviations. Examples Figure 1 shows a typical output of gear profile and helix (sometimes called lead) charts. These charts show the measured traces for both left and r

15、ight flanks of 3 teeth spaced approximately 120 apart. Figure 2 is a schematic based on ISO 1328-1:2013 figure 8 showing how a single profile trace is analyzed for a gear with a design profile that has both root and tip relief. Note that the orientation of the chart is not critical as long as it is

16、properly labeled, many charts present the traces vertically as in figure 1 while in ISO 1328-1:2013 the traces are presented horizontally. Figure 1. Typical profile and helix charts 4 14FTM06 a) Total profile deviation, Fb) Profile form deviation, ffc) Profile slope deviation Key: Cf Profile control

17、 Nf Start of active profile Fa Start of tip break a Tip L Profile evaluation length g Length of path of contact F Profile deviation, total ff Profile form deviation fH Profile slope deviation Figure 2. Typical analysis of profile deviations The same profile is shown in Figure 3, but this time the de

18、viations from the design profile are shown rather than the deviations from a perfect involute. Since this figure shows deviations from the design profile, the design profile will always be represented as a straight line on this figure. Therefore, no matter what the shape of the design profile, the m

19、ean profile line on this plot is a single straight line which is the best fit line of the deviations from the design profile over the profile evaluation range,. This corresponds with the statement in ISO 1328-1 clause 4.4.8.2 that “the straight-line gradient of the profile measurement is found by ap

20、plying the least squares method to the deviation of the measured profile trace from the specified design profile.” With the individual deviations and the best fit line through the deviations, it becomes very simple to find the total, slope, and form deviations. The total profile deviation is simply

21、the maximum deviation minus the minimum deviation from the design profile. This value is of course the same as that illustrated in Figure 2(a). In fact, the way Figure 2 is created is to first find the maximum and minimum deviations from the design profile, and then use these values to position facs

22、imiles of the design profile in Figure 2(a). Most inspection machine software actually works as illustrated in Figure 3; it just does not plot it that way1. The mean profile trace in Figure 2 is found by adding the ordinates of the straight line gradient to the design profile. So again, the data nee

23、ded to create Figure 2 could just as easily be used to also create Figure 3, unfortunately this data is normally hidden. Figure 3. Deviations from design profile with alternate analysis 1This statement is based on conversations the author has had with engineers from a number of different inspection

24、machine manufacturers. 5 14FTM06 The form deviation is found by first calculating the deviation minus the mean profile for all the points in the evaluation range. The difference between the maximum and minimum of these values is the form deviation. Again, the value found for form deviation will be t

25、he same in both Figures 2(b) and 3. The profile slope in Figure 3 is the distance between two horizontal lines that intersect the mean profile at the profile control diameter and at the tip diameter. This can be simplified to just the difference between the values of the mean profile at the profile

26、control diameter and the tip diameter. Of course the value found for slope deviation will be the same in both Figures 2(c) and 3. To further illustrate the concept, Figures 4 through 7 show first the deviations from a perfect involute, then deviations from the design profile. In the three copies of

27、the deviations from the design profile, the total, slope, and form deviations are shown. In Figure 4 the design profile is a perfect involute, so there is no difference between Figures 4(a) and 4(b). Figure 5 is for a gear that has a barreled profile specified. The steepness of the rise in excess ma

28、terial at both the tip and root is more obvious in Figure 5(b), which shows the deviation from design, compared to 5a, which shows deviations from a perfect involute. The profile slope, although it can be deduced from Figure 5(a), is very obvious in Figures 5(c) and 5(d). Figure 6 is for a gear with

29、 tip relief. The profile slope deviation again is very obvious when deviation from the design shape is shown. Figure 7 is another example with tip relief. The display of deviation from design shape indicates that the profile is crowned with respect to the design shape. a) Profile deviations from ide

30、al involute b) Total profile deviation (deviation shown from design profile) c) Profile slope deviation d) Profile form deviation Figure 4. Design profile: unmodified involute a) Profile deviations from ideal involute b) Total profile deviation (deviation shown from design profile) c) Profile slope

31、deviation d) Profile form deviation Figure 5. Design profile: modified involute (example with full contour) 6 14FTM06 a) Profile deviations from ideal involute b) Total profile deviation (deviation shown from design profile) c) Profile slope deviation d) Profile form deviationFigure 6. Design profil

32、e: modified involute (example with tip relief only) a) Profile deviations from ideal involute b) Total profile deviation (deviation shown from design profile) c) Profile slope deviation d) Profile form deviation Figure 7. Design profile: modified involute (example with tip relief only) By looking bo

33、th at a figure showing deviations from a perfect involute and at a figure showing deviations from the design shape, it becomes very easy to quickly get a full understanding of the deviations. The figures and much of the discussion has been on the profile, but the same applies to the helix. Looking a

34、t both the helix deviations from a perfect helix and at deviations from the design helix is just as beneficial as looking at both the profile deviations from a perfect profile and at deviations from the design profile. So while the profile is discussed here, the same methodology can apply to the hel

35、ix. A suggested addition to zone based tolerance evaluation ISO 1328-1:2013 Annex A presents a method for zone-based tolerance evaluation. Since it often is not necessary to control a relieved area quite as closely as the central area, use of such a system can have significant manufacturing advantag

36、es. In a zone-based tolerance evaluation, the profile (or helix) is divided into two or more zones, and each zone is calculated separately and may have different tolerance classes. For example, a profile could be divided into a tip zone, a middle zone and a root zone. A helix could be divided into a

37、 left end zone, a center zone, and a right end zone. The methods presented in ISO 1328-1:2013 Annex A for determining slope and form deviations in each of the zones are reasonable, and do not need any modification. However, the system has 3 problems when it comes to total deviation: 1. The areas bet

38、ween the zones are not well controlled. The areas between the zones are only considered for the plus material condition for form and total deviation. 2. There is an immediate jump in the tolerance when entering a different zone. 3. It is not clear how the total deviation should be applied. The text

39、says that it is measured the same way that a gear without specified zones is measured, which would defeat the purpose of a zone based system. One of the notes then says that the total deviation is often only applied to the middle zone or completely omitted, so there is no control of total deviation

40、in the end zones. If a value for total deviation is applied independently to each zone, since the tolerance bands of adjacent zones are 7 14FTM06 not linked this will result in the total allowed deviation from the design profile varying from gear to gear as shown in Figure 8(b). These problems could

41、 be addressed with a zone based tolerance evaluation system that specifies that the allowable total profile or total helix tolerance varies smoothly from the tolerance at the end of the central zone up to the increased tolerance at the end of the next zone. Figure 8 shows the differences between the

42、se systems. Figure 8(a) shows a trace of deviations from a perfect involute for a profile with tip relief, with the total profile deviation shown. In Figure 8(b) the trace has been redrawn to show deviations from the design profile. If the total deviation tolerance is applied independently to each z

43、one, then since the tolerance bands of adjacent zones are not linked, it can be seen that if the zone 2 tolerance is double the zone 1 tolerance, the allowable deviation relative to zone 1 may be anywhere from 2 to 3 times the zone 1 tolerance and depends on the position of the trace at the beginnin

44、g of zone 2. This may be why there is a note in ISO 1328-1:2013 A.2.3 that says “It is common practice to restrict evaluation to the middle zone or to omit Fa completely.” Unfortunately, this means that the shape of the profile is very poorly controlled in the area where there is tip relief. Figure

45、8c also shows a trace of deviations from a perfect involute for a profile with tip relief. In addition, it shows an example of the proposed tolerances for total profile deviation. It is critical to keep in mind that the tolerances are from the design profile, so that deviations in the positive direc

46、tion just mean less tip relief, and unless they are excessive they do not represent a plus material condition relative to a perfect involute. It should also be realized that all the systems allow for both plus and minus deviations from the design shape; this figure just makes that fact more obvious.

47、 Note that a designer might be tempted to specify an asymmetrical tolerance increase, but it is better to achieve the same result just by changing the design profile to allow for a symmetrical tolerance. It is easy to see how this proposed method can lead to the manufacturing savings that all zone b

48、ased systems share, since they allow for greater tolerances in the tip or end relief areas. This system has the advantage that it will maintain appropriate control over the entire profile or helix. While the figures and the examples used here were for the profile, it should be realized that the same

49、 concepts and advantages apply equally to the helix. Summary For gears with a modified profile or with a modified helix, the addition of plots showing deviations from the design shape can make understanding the deviations easier. Use of deviations from design can also make it easier to appropriately control tip, root, or end relief. References 1. ISO 1328-1:2013 Cylindrical gears ISO system of flank tolerance classification Part 1: Definitions and allowable values of deviations relevant to flanks of gear teeth 2. AGMA P109.16, Profile and Longitudinal Corrections