Exhaustive research supports new methods for designing and manufacturing straight bevel gears that are stronger and more cost-effective than ever before.

The optimal — or “rational” — design of gears can be a challenge due to the high number of variables, limitations, and interrelationships involved. And also because, in each separate case, the objective functions, restrictions, and independent variables are generally different. Many of the specialists who have approached gear optimization by means of exhaustive search methods [Dana (1969), Escanaverino (1984), and López (1993)] first organized an evaluation of the objective function with reasonable design parameter values in place, and then compared and retained the most extreme results of the function in each step.

In this particular case a functional methodology is given, with the objective being to establish general principles and procedures for the rational calculation of gears, with an emphasis on straight bevel gears. The procedure utilized has as its starting point a mathematical model based on the ISO standards for gear load capacity and a system generated with interrelation between gear geometry and resistance. The ISO standards for the load capacity calculation of bevel gears (ISO 10300-1,2,3) was used to develop the relationships between the geometry and tooth resistance. Additionally, the procedure includes the verification of the gear’s geometric qualities by means of “indicators” to establish restrictions in the field of possible solutions. Some of them are:

• Transverse contact ratio ( Eva ) greater than a minimum value
• Tooth topland thickness (sa) greater than a minimum value
• Tooth interference occurrence is inadmissible
• Dimension of the outer tip diameter on gear (dÊ2) smaller than a maximum value

### Maximum Torque on a Pinion Based in ISO Formulae for Verification of the Surface Load Capacity

The actual bevel gear-tooth rating formulae for pitting resistance are based, firstly, on Hertz’s results for the calculation of contact pressure between two curved surfaces. They have also been improved with modifications in the ISO standards to consider load sharing between adjacent teeth, the position of the center of pressure on the tooth, the shape of the instantaneous area of contact, and the load concentration resulting from manufacturing uncertainties. Taking all of this account, the ISO formulae for the calculation of surface durability of bevel gears (ISO 10300-2 and ISO 6336-5) were the basis to determine the objective function for evaluation of the maximum torque on a pinion according to the higher load capacity.

Where:

KV Dynamic factor
K Face load factor for contact stress
KHa Transverse load factor for contact stress
dm1 Mean reference diameter on pinion (mm)
ZM-B Mid-zone factor
ZH Zone factor
u Gear ration
lb Length of the line of contact (mm)
(sigma)HP Permissible contact stress (MPa)
[T1C] Permissible (maximum) torque on pinion according to contact stress (Nmm)

### Maximum Torque on a Pinion Based in ISO Formulae for Verification of the Tooth Root Strength

The actual bevel gear formulae for bending-strength rating are based on cantilever-projection theory and can be used for determining a load rating that will prevent tooth root fillet fracture (bending fatigue) during the design life of the gear teeth. In most cases, the maximum tensile stress at the tooth root (arising from bending at the root when the load is applied to the tooth flank) can be used as the criterion for the assessment of the bending tooth root strength, as when the allowable stress number is exceeded the teeth can experience breakage. When calculating the tooth root stresses of straight bevel gears, it is considered that the load is applied at the tooth tip of the virtual cylindrical gear, and that it is subsequently converted to the outer point of single-tooth contact with the aid of the contact-ratio factor Ye. Just the same as in the calculation of tooth contact stress for pitting resistance, the calculating of tooth root strength takes into account load sharing between adjacent teeth, an increment of nominal load due to non-uniform distribution of load on the tooth face, and some external and internal dynamic load resulting from manufacturing uncertainties and tooth elastic deformation.

Taking this state of the art into account, the ISO formulae for the calculation of tooth root strength of bevel gears (ISO10300-3 and ISO 6336-5) were the basis to determine the other objective function for evaluation of the maximum torque on a pinion according with the higher load capacity.

Where:
b Face width (mm)
z1 Number of teeth on pinion
m Outer normal module (cutter module) (mm)
YX Size factor for tooth root stress
YßrelT Relative sensitivity factor
K Face load factor for bending stress
KFa Transverse load factor for bending stress
YFa Tooth form factor for load application at tip
YSa Stress correction factor for load application at tooth tip
YE Contact ratio factor for tooth root stress
YK Bevel gear factor
(sigma)FP Permissible tooth root stress (MPa)
[T1F] Permissible (maximum) torque on pinion according to tooth root strength (Nmm)

### A Rational Calculation of Straight Bevel Gear with High Load Capacity for the Condition of Tooth Pitting and Bending Fatigue

In the proposed method, the rational parameters of the straight bevel geometry are obtained by means of an organized evaluation of the two objective functions that allows, in each step, to compare and to retain the extreme value in the functions (instantaneous optimum) and all values of each design parameter involved. The design parameters obtained by these means belong to the group of acceptable values and possible solutions in the design problem. In this case, the variable to maximize was the pinion torque applied in the gear transmission with restrictions of:
• Maximum load capacity to contact and bending stresses
• Transverse contact ratio greater than a minimum value
• Not tooth interference occurrence
• Tooth topland thickness greater than a minimum value
• Outer tip diameter on gear no greater than a maximum value

Due to space limitations, a simplified algorithm of the calculation procedure of the rational geometry for a straight bevel gear is shown in Figure 1a and Figure 1b.

### Results Obtained Using the Proposed Calculation Procedure

The described procedure was the base for two computation programs in Visual Basic 4.0. The results obtained in the various running of computation programs showed the possibilities of these procedures for the analysis of new bevel gear designs. The validation of rational design results was achieved by taking 98 straight bevel gears referenced in technical catalogues and literature by American companies such as The Gleason Works, Browning Manufacturing, and Martin Sprocket & Gears. Results for two groups of designs are presented in Figure 2.

It can be noted that in Figure 2 the load capacities calculated according to ISO 10300 were superior in an average of 9 percent on straight bevel gears whose geometry was obtained using the procedures exposed. Taking into account all straight bevel gears in the validation, the ISO load capacity was greater than an average of 15 percent. The results reflected in Figure 3 are corresponding with a rational geometric synthesis of straight bevel gears at 90° shaft angle, with maximum ISO load capacity and restrictions of the outer tip diameter of the gear. Due to space restrictions, only some of the results obtained are presented here.

### Conclusions

A procedure was developed for the rational calculation of straight bevel gears at 90°. This procedure was based on the new standard ISO 10300. It is conservatively considered to provide economic savings of 10 percent, taking into account a more-compact design with higher load capacity. The results achieved using the procedures given were compared with successful straight bevel gears, and they demonstrated possibilities to increase the load capacity up to 15 percent. Moreover, the results have shown that the exhaustive search technique is very effective in the optimized calculation of gears. The results presented in Figure 3 can be used to obtain a rational design according to the declared conditions.

### References

1. Dana, D (1969) “Computer-Aided Spur Gear Design,” SAE Paper 690564, Caterpillar Co., EUA.
2. Escanaverino, J.M. y Uli, E (1984) “Algunas Experiencias en el Diseño de Engranajes con Ayuda de Computadoras.” IV Conferencia Científica de Ingeniería y Arquitectura. ISPJAE.
3. López, R (1993) “Practical Optimization of Helical Gears Using Computer Software,” Gear Technology, Pages 16-21, Vol. 10, No. 3.
4. ISO Standard 10300. Calculation of Load Capacity of Bevel Gears, ISO TC60-WG6, 2001.
5. ISO Standard 6336-5. Calculation of load capacity of spur and helical gears – Part 5: Strength and quality of materials. 2000.
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is a professor of mechanical engineering in the mecatronic division at Universidad Tecnológica de Aguascalientes, Mexico. He is an AGMA member with expertise in the area of ISO/TC60/WG6-13. He can be reached at (52)449-2992683 or via email at gonzalo.gonzalez@utags.edu.mx.