Beyta Gear Service
No matter how much care is taken in the design and manufacture of gears, they are sure to fail if improperly assembled or inadequately mounted. Many “gear” problems are caused by lack of attention to the accuracy required in machining the housing, in assembling the gears and bearings to the shafts, and in aligning the sub-assemblies. The author knows of gearboxes that, after giving 30 years of excellent service, have failed within hours of “field” rebuilding by inexperienced mechanics. If you are not sure how to handle a particular aspect of a design or maintenance project, ask for help or check the reference books listed in this manual. Most bearing manufacturers will be happy to review your drawings and bearing selections at little or no charge. If your gear supplier has an engineering department, they may also be available to “consult” on your design project or to train your maintenance and assembly people in proper methods of handling and adjusting gears.
Backlash is one of the most misunderstood concepts in gearing. An individual gear cannot have backlash — it can only have a tooth thickness. Backlash occurs when gears are mated together on a given center distance and the sum of their tooth thicknesses is less than their circular pitch. The backlash of a pair of gears will vary at some points in the rotational cycle due to run-out and cutting inaccuracies. If the center distance is increased the backlash will increase; if it is reduced the backlash will decrease. Don’t confuse “low backlash” with “high quality”. Except for applications that require positioning accuracy, such as index tables or radar drives, or that are subject to frequent reversing loads, “too much” backlash seldom effects gear performance. Not having enough backlash can result in the gears “binding” under some conditions, especially at low temperatures when steel gears are used in an aluminum housing. Gears that bind are certain to fail.
When low backlash is required, the best approach is to use “anti-backlash” gears or adjustable centers (see Figure 4.1). Tight tolerances on tooth thicknesses and center distances are seldom effective and can be very expensive. Anti-backlash gears consist of two gear halves that are spring loaded to adjust the “effective” tooth thickness to fill in the space available on the mating part. These gears are not used to transmit significant amounts of power, as the required spring pressures become hard to obtain in the space available. Adjustable centers can handle slightly higher loads but are expensive to manufacture. The reference books discuss “backlash” extensively and some manufacturers include a limited range of anti-backlash gears for instrument use in their catalogs.
The difference between a “good” gear and a “bad” one can often be traced to how accurately the blank was machined. In a production run of gears, for example, those having bores close to the low limit (or maximum material condition) will fit the cutting arbor more snugly and usually exhibit the least “run-out”. If gears are to be cut in a “stack” the perpendicularly of the blank sides to the bore will similarly influence the results. It is important to “match” the tolerancing of those part features — which will be used for work-locating during the machining process — to the accuracy needed in the final part. Your gear supplier may have some specific requirements in this area, but the values shown in Tables 4.1 to 4.3 are a good place to start.
(Courtesy of Quaker City Gear Works)
AGMA |
Q6 |
Q7 |
Q8 |
Q9 & Q10 |
Q11 & up |
Diameter of Bore |
.002 |
.001 |
.0007 |
.0005 |
.0002 |
Taper of Bore (No portion to exceed tolerance) |
.001/in of length Max .002 |
.0007/in of length Max .001 |
.0005/in of length Max .0007 |
.0003/in of length Max .0005 |
.0002 |
Concavity of Mounting & Register Surfaces |
.001/in of radius for rigid blanks |
.0005/in of radius for rigid blanks |
|||
Convexity of Mounting & Register Surfaces |
None for any class | ||||
Lateral Runout of Bevel & Face Gears |
.001/in of radius Max .002 |
.0008/in of radius Max .0016 |
.0005/in of radius Max .001 |
.0004/in of radius Max .0008 |
.0003/in of radius Max .0005 |
Lateral Runout of Spur & Helical Gears |
.002/in of radius Max .004 |
.0015/in of radius Max .0025 |
.001/in of radius Max .002 |
.0007/in of radius Max .0015 |
.0005/in of radius Max.001 |
Non-Parallelism |
.002/in of radius Max .004 |
.0015/in of radius Max .0025 |
.001/in of radius Max .002 |
.0007/in of radius Max .0015 |
.0005/in of radius Max.001 |
(Courtesy of Quaker City Gear Works)
Diametral Pitch | AGMA Q5 TO Q8 | AGMA Q9 & up |
1 – 4 | 0.015 | 0.009 |
5 – 8 | 0.010 | 0.006 |
9 – 13 | 0.006 | 0.004 |
14 – 19 | 0.004 | 0.003 |
20 – 39 | 0.003 | 0.002 |
40 – 79 | 0.002 | 0.0015 |
80 & finer | 0.001 | 0.001 |
D.P. | +0 | D.P. | +0 | ||
3 | −0.020 | 40 | −0.005 | ||
5 | −0.015 | 48 | −0.004 | ||
8 | −0.010 | 64 | −0.003 | ||
10 | −0.008 | 72 | −0.003 | ||
12 | −0.007 | 80 | −0.002 | ||
14 | −0.007 | 96 | −0.002 | ||
18 | −0.007 | 120 | −0.002 | ||
20 | −0.007 | 124 & up | −0.001 | ||
32 | −0.006 | ||||
(Courtesy of Quaker City Gear Works)
Straight-Bevel Gears — All Classes
D.P. | Tol. ±.000 |
20 – 30 | −0.005 |
31 – 40 | −0.004 |
41 – 56 | −0.003 |
57 – 94 | −0.002 |
95 & finer | −0.001 |
Bevel Gears
D.P. | Tol. ±.000 |
20 – 46 | −0.002 |
47 & finer | −0.001 |
±1°
max. 125 Micro
0.0000 – 0.0002 | 8 Micro |
0.0002 – 0.0005 | 16 Micro |
0.0005 – 0.0010 | 32 Micro |
All units to be chamfered for:
141 ⁄2° P.A. | 15° |
20° P.A. | 20° |
60° P.A. | 30° |
Sharp corners to be broken to 0.005 – 0.01500 radius.
0 – 600 | ±.005 |
6 – 1200 | ±.010 |
±1 ⁄2°
Class 2 fit
Mill Standard
Concentricity of bearing journals, in respect to true center of part, shall be held within the total tolerance of bearing journal diameter size.
Examples:
• Bearing diameter size .125 ± .0003
• Concentricity to true centerline .0003 T.I.R.
• Bearing diameter size .500 ± .0005
• Concentricity to true centerline .0005 T.I.R.
Selecting the proper quality class for a particular application is one of the most controversial areas of gear design. AGMA has provided a chart in AGMA 2000 (formerly AGMA 390.03) that can be used to select the quality level needed. Many of the texts listed in the reference section of this guide have additional information on this topic. Quality level should be a function of application, power level, and operating speed. Table 4.4 is the author’s suggestion for minimum quality level vs. maximum pinion pitch-line velocity when relatively smooth applications are considered.
For uni-directional service and relatively smooth power flow:
(If these conditions are not present, a higher quality level may be needed.)
Maximum | Minimum-Suggested |
plv in ft/min | AGMA Quality Level |
250 | 6 |
500 | 7 |
1500 | 8 |
2500 | 9 |
3500 | 10 |
5000 | 11 |
7500 | 12 |
10000 | 13 |
It is very important to remember that increased quality levels cost money. If you want cost-effective designs you must resist the urge to “solve” your gear problems by over-specifying quality levels. Even the “best” gears will fail if they are not mounted accurately, or properly sized for the load and system dynamics. Table 4.5 shows the quality levels normally achievable for various gear elements by modern manufacturing techniques. The column on “relative cost” reflects not only the additional time and effort needed to make the gear teeth, but also the extra expense of increased blank accuracy.
Manufacturing | Involute | Spacing | Relative | ||
Method | Run-out | Profile | Lead | (Pitch) | Cost |
Hobbing (Class b Hob) | 8 to 10 | 8 to 9 | 8 to 9 | 8 to 9 | 1.0 to 1.25 |
Hobbing (Class a Hob) | 9 to 11 | 8 to 9 | 9 to 11 | 8 to 10 | 1.25 to 1.5 |
Hobbing (Class aa Hob) | 9 to 12 | 8 to 11 | 9 to 11 | 9 to 11 | 1.5 to 1.75 |
Shaping (Commercial Cutter) | 8 to 10 | 8 to 10 | 8 to 11 | 8 to 10 | 1.25 to 1.5 |
Shaping (Precision Cutter) | 9 to 11 | 9 to 10 | 9 to 11 | 9 to 11 | 1.5 to 1.75 |
Shaving | 10 to 12 | 8 to 10 | 8 to 12 | 8 to 12 | 2.0 to 2.5 |
Grinding | 9 to 14 | 9 to 14 | 8 to 14 | 9 to 14 | 3.0 to 4.0 |
Lower quality levels are generally achievable under most conditions.
Upper quality levels require special controls on blanks, tooling, and machinery. This can increase costs significantly.
Relative costs compared to Class b hobbing for operations needed to finish gear teeth only. Material and heat-treat costs are not included in this comparison.
If heat treating is done after tooth finishing, quality level can drop by two levels or more.
The surface finish of gear teeth is another controversial aspect of gear design. One common misconception is that specifying an AGMA quality class also specifies a tooth-surface finish. AGMA 2000 does not include surface finish in its tolerancing. Table 4.6 shows the surface finishes normally produced by common production methods. Comparing this table with the one on quality vs. production method (Table 4.5) shows that there is an indirect relationship between “quality” and “surface finish”.
Tooth | Effort | ||||
Size | Required | Hobbing | Shaping | Shaving | Grinding |
1 to 3 dp | Normal | 125 | 80 to 125 | 63 | 32 |
Extra | 80 | 80 | 32 | 16 | |
3 to 10 dp | Normal | 80 | 63 to 80 | 63 | 32 |
Extra | 63 | 63 | 32 | 16 | |
10 to 24 dp | Normal | 80 | 63 to 80 | 50 to 32 | 32 |
Extra | 63 | 63 | 16 | 16 | |
24 to 40 dp | Normal | 80 | 63 | 50 to 32 | 32 |
Extra | 63 | 63 to 32 | 16 | 16 | |
40 dp and up | Normal | 80 | 63 | not practical | 32 |
Extra | 63 | 63 to 32 | 16 | ||
Normal effort involves typical production feeds and speeds.
Extra effort involves special controls and procedures on tools and machines. Cycle time may increase significantly.
Finishes shown are for through-hardened steel of 230 – 310 bhn.
Finish may be poorer on steel below 230 bhn or above 310 bhn.
Surface finish may be slightly better in brass, bronze, aluminum, or stainless steel, provided proper feeds and speeds are selected.
Surface finish for surface-hardened gears that are not finished after heat treating may be slightly worse due to scale-removal operations.
When you specify a tooth surface finish (Table 4.7) you are often requiring costly gear-finishing processes (Table 4.8) that do not increase “quality” as defined by AGMA 2000. It is important to satisfy yourself, by studying whatever information is available (or through field testing), that you need a particular finish to meet your performance objectives. Surface finish has an effect on lubricant film-thickness requirements. While no consensus “standard” has been published on what lubricant viscosities are needed with what surface finishes, it is clear that heavier oil is needed when coarser finishes are present. The use of the heavier lube may or may not be possible in some applications due to cold-starting conditions, thermal considerations, or other issues.
Symbol |
Description |
Indicates that the surface is very rough and uneven within the dimensional requirements. |
|
Indicates that the surface is rough and uneven within the dimensional requirements. |
|
Indicates that the surface must be smooth and even to a degree obtainable by tools removing large chips or shavings. Machining marks and grooves discernible to the eye and to touch are permitted, if the surface meets dimensional requirements. |
|
Indicates that the surface must be smooth and even to a degree obtainable by tools removing medium chips or shavings. Machining marks and grooves discernible to the eye are permitted, if the surface meets dimensional requirements. |
|
Indicates that the surface must be smooth and even to a degree obtainable by tools removing small chips. Machining marks and grooves discernible to the eye are permitted, if the surface meets the dimensional requirements. |
|
Indicates the surface must be smooth and even to a degree obtainable by tools removing small particles. Machining marks such as grooves must not be discernible to the eye or touch, if the surface meets the dimensional requirements. |
|
Indicates that the surface must be very smooth and even to a degree obtainable by tools removing very small particles. Machining marks such as grooves must not be discernible to the eye or touch, if the surface meets the dimensional requirements. |
|
Indicates that the surface must be even to a degree obtainable by tools removing minute particles, generally by grinding. Machining marks such as the fine patterns resulting from grinding must not be discernible to the eye or touch and the surface must have a polished appearance and meet dimensional requirements. |
|
Indicates that the surface must be even to a degree obtainable by tools removing very minute particles, generally by honing, lapping, or super-finishing. Machining marks such as very fine patterns must not be discernible to the eye or touch and the surface must have a highly polished appearance and meet dimensional requirements. |
|
ref: Gear Handbook by Dudley, Table 9-16
Symbol |
Quality class |
Description |
Max. rms value, micro in. |
Suitable range of total tolerance |
Typical fabrication methods |
Approx. relative cost to produce |
|
Extremely rough |
Extremely crude surface produced by rapid removal of stock to nominal dimension |
1,000 |
0.063 – 0.125 |
Rough sand casting, flame cutting |
1 |
|
Very rough |
Very rough surface unsuitable for mating surfaces |
500 |
0.015 – 0.063 |
Sand casting, contour sawing |
2 |
|
Rough |
Heavy toolmarks |
250 |
0.010 – 0.015 |
Very good sand casting, saw cutting, very rough machining |
3 |
|
Fine |
Machined appearance with consistent toolmarks |
125 |
0.005 – 0.010 |
Average machining — turning, milling, drilling; rough hobbing and shaping; die casting, stamping, extruding |
4 |
|
Fine |
Semi-smooth without objectionable tool marks |
63 |
0.002 – 0.005 |
Quality machining — turning, milling, reaming; hobbing, shaping; sintering, stamping, extruding, rolling |
6 |
|
Smooth |
Smooth, where toolmarks are barely discernible |
32 |
0.0005 – 0.002 |
Careful machining; quality hobbing and shaping; shaving; grinding; sintering |
10 |
|
Ground |
Highly smooth finish |
16 |
0.0002 – 0.0005 |
Very best hobbing and shaping; shaving; grinding, burnishing |
15 |
|
Polish |
Semi-mirror-like finish without any discernible scratches or marks |
8 |
0.0001 – 0.0002 |
Grinding, shaving, burnishing, lapping |
20 |
|
Super-finish |
Mirror-like surface without tool grinding or scratch marks of any kind |
4 |
0.00004 – 0.0001 |
Grinding, lapping, and polishing |
25 |
ref: Gear Handbook by Dudley, Table 9-17
One thing that all gear experts agree on is that you can’t make a good gear from a bad blank. “Bad” doesn’t just mean poor workmanship: it also refers to poor design or poor tolerancing. A good way to prevent these problems is to become familiar with the processes used to make gears and make provisions in the design of the part to use those processes to your advantage. Once you understand the manufacturing techniques you’ll be able to determine which parts of your gear system are likely to be problems while there is still time to make design changes. This is a good time to remember the old adage “If it looks right it probably is.” Many gear problems are really “proportion” problems. Long spindly shafts, large gears with small rim or web thicknesses, inadequate housing supports, and poor “packaging” have caused more “gear failures” than anyone cares to count. Take a careful look at the general “appearance” of your design before making the final drawings.
One of the first steps in designing a gear is the selection of the tooth form to be used. To a certain extent this decision is based upon rating requirements, but the choice made will also effect the manufacturing processes used. Table 4.9 shows the “popular” tooth forms in use today. There are many other forms available, and each has its proponents. The author urges caution on the part of anyone who is thinking of using a tooth form not on Table 4.9, as the availability of cutting tools will be limited. The actual variation in tooth strength from one form to another is slight. For critical applications tooth form might make the difference between success and failure, but those instances are rare, and should be left to the “real experts.” Unless very low numbers of pinion teeth are involved, the author sees little need to use anything other than 20 full-depth teeth on new designs. If low numbers of pinion teeth (< 20) are needed, 25 full-depth is the best choice. When making modifications to existing designs, you may have to work with the other forms shown on Table 4.9, but they should be considered “obsolete” for new designs.
Dimensions shown are for 1 ndp.
For other sizes, divide dimensions shown by ndp needed.
Normal | ||||||
Tooth |
Pressure | Whole | Fillet | Circular | ||
Form |
Angle | Depth | Addendum | Dedendum | Radius | Pitch |
Full Depth |
14.5° | 2.157 | 1.00 | 1.157 | 0.21 | 3.1416 |
Full Depth |
20° | 2.157 | 1.00 | 1.157 | varies | 3.1416 |
Full Fillet |
20° | 2.250 | 1.00 | 1.250 | 0.30 | 3.1416 |
Pre-Shave or Pre-Grind |
20° | 2.350 | 1.00 | 1.350 | 0.30 | 3.1416 |
Stub |
20° | 1.800 | 0.80 | 1.000 | 0.20 | 3.1416 |
Full Depth |
25° | 2.250 | 1.00 | 1.250 | 0.25 | 3.1416 |
Full Fillet |
25° | 2.300 | 1.00 | 1.300 | 0.30 | 3.1416 |
Fellows Stub (x ⁄ y) |
20° | 2.25 ⁄ y | 1.00 ⁄ y | 1.25 ⁄ y | varies | 3.1416 ⁄ x |
Nutall |
20° | 1.728 | 0.79 | .943 | varies | 3.1416 |
Fellows stub is also called “combination pitch.”
Nutall system should not be used for new designs.