Motor-Belt-Drive Shaft Design for Steady Loading
A motor transmits the power P at the speed of n by a belt drive to a machine (Figure 9.4(a)). The maximum tensions in the belt are designated by F_1 and F_2 with F_1 > F_2 . The shaft will be made of cold-drawn AISI 1020 steel of yield strength S_y . Note that the design of main and drive shafts of a gear box will be considered in Case Study 18.5. Belt drives are discussed in detail in Chapter 13.
Find: Determine the diameter D of the motor shaft according to the energy of distortion theory of failure, based on a factor of safety n with respect to yielding.
Given: Prescribed numerical values are
L=230 mn \quad a=70 mm \quad r=51 mm \quad P=55 kW
n_0=4500 rpm \quad S_y=390 MPa \quad(\text { from Table B.3) } n=3.5
Assumptions: Friction at the bearings is omitted; bearings act as simple supports. At maximum load F_1 = 5F_2 .
TABLE B.3 Mechanical Properties of Some Hot-Rolled (HR) and Cold-Drawn (CD) Steels |
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UNS Number | AISI/ SAE Number | Processing | Ultimate
\text {Strength}^a S_u (MPa) |
Yield
\text {Strength}^a S_y (MPa) |
Elongation in 50 mm (%) | Reduction in Area (%) | Brinell Hardness (H_B) |
G10060 | 1006 | HR | 300 | 170 | 30 | 55 | 86 |
CD | 330 | 280 | 20 | 45 | 95 | ||
G10100 | 1010 | HR | 320 | 180 | 28 | 50 | 95 |
CD | 370 | 300 | 20 | 40 | 105 | ||
G10150 | 1015 | HR | 340 | 190 | 28 | 50 | 101 |
CD | 390 | 320 | 18 | 40 | 111 | ||
G10200 | 1020 | HR | 380 | 210 | 25 | 50 | 111 |
CD | 470 | 390 | 15 | 40 | 131 | ||
G10300 | 1030 | HR | 470 | 260 | 20 | 42 | 137 |
CD | 520 | 440 | 12 | 35 | 149 | ||
G10350 | 1035 | HR | 500 | 270 | 18 | 40 | 143 |
CD | 550 | 460 | 12 | 35 | 163 | ||
G10400 | 1040 | HR | 520 | 290 | 18 | 40 | 149 |
CD | 590 | 490 | 12 | 35 | 170 | ||
G10450 | 1045 | HR | 570 | 310 | 16 | 40 | 163 |
CD | 630 | 530 | 12 | 35 | 179 | ||
G10500 | 1050 | HR | 620 | 340 | 15 | 35 | 179 |
CD | 690 | 580 | 10 | 30 | 197 | ||
G10600 | 1060 | HR | 680 | 370 | 12 | 30 | 201 |
G10800 | 1080 | HR | 770 | 420 | 10 | 25 | 229 |
G10950 | 1095 | HR | 830 | 460 | 10 | 25 | 248 |
Source: ASM Handbook, vol. 1, ASM International, Materials Park, OH, 2020. | |||||||
Note: To convert from MPa to ksi, divide given values by 6.895. | |||||||
{ } ^ {a} Values listed are estimated ASTM minimum values in the size range 18–32 mm. |
Reactions at bearings. From Equation (1.15), the torque applied by the pulley to the motor shaft equals
kW =\frac{F V}{1000}=\frac{T n}{9549} (1.15)
T_{A C}=\frac{9549 P}{n_0}=\frac{9549(55)}{4500}=116.7 N \cdot m
The force transmitted through the belt is therefore
F_2-\frac{F_1}{5}=\frac{T_{A C}}{r}-\frac{116.7}{0.051}=2288 N
or
F_1=2860 N \text { and } F_2=572 N
Applying the equilibrium equations to the free-body diagram of the shaft (Figure 9.4(b)), we have
\Sigma M_A=3432(0.3)-R_B(0.23)=0, \quad R_B=4476.5 N
\Sigma F_y=R_A+R_B-3432=0, \quad R_A=1044.5 N
The results indicate that R_A and R_B act in the directions shown in the figure.
Principal stresses. The largest moment takes place at support B (Figure 9.4(c)) and has a value of
M_B=3432(0.07)=240.2 N \cdot m
Inasmuch as the torque is constant along the shaft, the critical sections are at B . It follows that
\tau=\frac{16 T}{\pi D^3}=\frac{16(116.7)}{\pi D^3}=\frac{1867.2}{\pi D^3}
\sigma_x=\frac{32 M}{\pi D^3}=\frac{32(240.2)}{\pi D^3}=\frac{7686.4}{\pi D^3}
and \sigma _y = 0. For the case under consideration, Equation (3.33) reduces to
\sigma_{\max , \min }=\sigma_{1,2}=\frac{\sigma_x+\sigma_y}{2} \pm \sqrt{\left(\frac{\sigma_x-\sigma_y}{2}\right)^2+\tau_{x y}^2} (3.33)
\begin{aligned} \sigma_{1,2} & =\frac{\sigma_x}{2} \pm \sqrt{\left(\frac{\sigma_x}{2}\right)^2+\tau^2} \\ & =\frac{3843.2}{\pi D^3} \pm \frac{1}{\pi D^3} \sqrt{\frac{(7686.4)^2}{4}+(1867.2)^2} \\ & =\frac{1}{\pi D^3}(3843.2 \pm 4272.8) \end{aligned}
from which
\sigma_1=\frac{8116}{\pi D^3} \quad \sigma_2=-\frac{429.6}{\pi D^3} (b)
Energy of distortion theory of failure. Through the use of Equation (6.14),
\left(\sigma_1^2-\sigma_1 \sigma_2+\sigma_2^2\right)^{1 / 2}=\frac{S_y}{n} (6.14)
\left[\sigma_1^2-\sigma_1 \sigma_2+\sigma_2^2\right]^{1 / 2}=\frac{S_y}{n}
This, after introducing Equation (b), leads to
\frac{1}{\pi D^3}\left[(8116)^2-(8116)(-429.6)+(-429.6)^2\right]^{1 / 2}=\frac{390\left(10^6\right)}{3.5}
Solving,
D=0.0288 m =28.8 mm
Comment: A commercially available shaft diameter of 30 mm should be selected.