For the pair of gears shown in Figure 8–1, compute all of the features of the gear teeth described in this section. The gears conform to the standard AGMA form and have a diametral pitch of 12 and a 20° pressure angle.
For the pair of gears shown in Figure 8–1, compute all of the features of the gear teeth described in this section. The gears conform to the standard AGMA form and have a diametral pitch of 12 and a 20° pressure angle.
Given P_d = 12; N_p = 11; N_G = 18; \phi = 20°.
Analysis Unless otherwise noted, we use equations from Table 8–1 to compute the features. Refer to the text in this section for explanation of terms.
Note that results are reported to four decimal places as is typical for precise mechanical devices like gears.
A similar level of accuracy is expected for problems in this book.
Results Pitch Diameters
For the pinion,
D_{p}=N_{p} / P_{d}=11 / 12=0.9167 \text { in }
For the gear,
D_{G}=N_{G} /P_{d}=18 / 12=1.5000 \mathrm{in}
Circular Pitch
Three different approaches could be used.
p=\pi / P_{d}=\pi / 12=0.2618 \text { in }
Note that data for either the pinion or the gear data may also be used. For the pinion,
p=\pi D_{p} / N_{p}=\pi(0.9167 \mathrm{in}) / 11=0.2618 \mathrm{in}
For the gear,
p=\pi D_{G} / N_{G}=\pi(1.500 \mathrm{in}) / 18=0.2618 \mathrm{in}
Addendum
a=1 / P_{d}=1 / 12=0.8333 \text { in }
Dedendum
Note that the 12-pitch gear is considered to be coarse. Thus,
b=1.25 / P_{d}=1.25 / 12=0.1042 \text { in }
Clearance
c=0.25 / P_{d}=0.25 / 12=0.0208 \text { in }
Outside Diameters
For the pinion,
D_{o P}=\left(N_{P}+2\right) / P_{d}=(11+2) / 12=1.0833 \text { in }
For the gear,
D_{o G}=\left(N_{G}+2\right) / P_{d}=(18+2) / 12=1.6667 \text { in }
Root Diameters
First, for the pinion,
D_{R P}=D_{P}-2 b=0.9167 \text { in }-2(0.1042 \text { in })=0.7083 \text { in }
For the gear,
D_{R G}=D_{G}-2 b=1.500 \text { in }-2(0.1042 \text { in })=1.2917 \text { in }
Whole Depth
h_{t}=a+b=0.0833 \text { in }+0.1042 \text { in }=0.1875 \text { in }
Working Depth
h_{k}=2 a=2(0.0833 \mathrm{in})=0.1667 \mathrm{in}
Tooth Thickness
t=\pi /\left[2\left(P_{d}\right)\right]=\pi /[2(12)]=0.1309 \text { in }
Center Distance
C=\left(N_{G}+N_{P}\right) /\left(2 P_{d}\right)=(18+11) /[2(12)]=1.2083 \text { in }
Base Circle Diameter
\begin{aligned}&D_{b P}=D_{P} \cos \phi=(0.9167 \mathrm{in}) \cos \left(20^{\circ}\right)=0.8614 \mathrm{in} \\&D_{b G}=D_{G} \cos \phi=(1.5000 \mathrm{in}) \cos \left(20^{\circ}\right)=1.4095 \mathrm{in}\end{aligned}
TABLE 8–1 Gear and Tooth Features, Diameters, Center Distance for a Gear Pair | |||||||
Formulas | |||||||
U.S. Full-depth involute system | Metric module system (mm) |
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Number of teeth and Pitches | Symbol | Definition | Typical unit | General formula | Coarse pitch P_d < 20 (in) | Fine pitch P_d ≥ 20 (in) | |
Number of teeth | N | Integer count of teeth on a gear | |||||
Circular pitch | P | Arc distance between corresponding points on adjacent teeth | in or mm | p = πD/N | p = π/P_d | p = πm | |
Diametral pitch | P_d | Number of teeth per inch of pitch diameter | in^{-1} | P_d = N/D | |||
Module | m | Pitch diameter divided by number of teeth | mm | m = D/N | m = 25.4/P_d | ||
Diameters | |||||||
Pitch diameter | D | Kinematic characteristic diameter for a gear; Diameter of the pitch circle | in or mm | D = N/P_d | D = mN | ||
Outside diameter | D_o | Diameter to the outside surface of the gear teeth | in or mm | D_o = (N + 2)/P_d | D_o = m(N + 2) | ||
Root diameter | D_R | Diameter to the root circle of the gear at the base of the teeth | in or mm | D_R = D – 2b | |||
Gear Tooth Features | |||||||
Addendum | a | Radial distance from pitch circle to outside of tooth | in or mm | a = 1.00/P_d | a = 1.00m | ||
Dedendum | b | Radial distance from pitch circle to bottom of tooth space | in or mm | b = 1.25/P_d | b = 1.20/P_d + 0.002 | b = 1.25m^1 | |
Clearance | c | Radial distance from top of fully engaged tooth of mating gear to bottom of tooth space | in or mm | c = 0.25/P_d | c = 0.20/P_d + 0.002 | c = 0.25m^1 | |
Whole depth | h_t | Radial distance from top of a tooth to bottom of tooth space | in or mm | h_t = a + b | h_t = 2.00/P_d | h_t = 2.20/P_d + 0.002 | h_t = 2.25m^1 |
Working depth | h_k | Radial distance a gear tooth projects into tooth space of mating gear | in or mm | h_k = a + a = 2a | h_k = 2.25/P_d | h_k = 2.25/P_d | h_k = 2.00m^1 |
Tooth thickness | Tensile strength | Theoretical arc distance equal to 1/2 of circular pitch | in or mm | t = p/2 | t = π/[2(P_d)] | t = πm/2 | |
Face width | F | Width of tooth parallel to axis of gear | in or mm | Design decision | Approximately 12/P_d | ||
Pressure angle | \phi | Angle between the tangent to the pitch circle and the perpendicular to the gear tooth surface | degrees | Design decision | Most common value = 20° Others: 14 1/2°, 25° |
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Center Distance | C | Distance from between centerlines of mating gears | in or mm | C = (D_P + D_G)/2 | C = (N_P + N_G)/2P_d | C = m(N_P + N_G)/2 |