High-Speed Turbine Geared to Drive a Generator
A turbine rotates at about n =8000 rpm and drives, by means of a helical gearset, a 250 kW (335 hp) generator at 1000 rpm, as depicted in Figure 12.8. Determine:
a. The gear dimensions and the gear tooth forces.
b. The load capacity based on the bending strength and surface wear using the Lewis and Buckingham equations.
c. The AGMA load capacity on the basis of strength only.
Given: Gearset helix angle \psi=30^{\circ} and
\text { Pinion: } N_p=35, \quad \phi_n=20^{\circ}, \quad P_n=10 \text { in. }^{-1}
Design Assumptions:
1. Moderate shock load on the generator and a light shock on the turbine.
2. Mounting is accurate.
3. Reliability is 99.99%.
4. Both pinion and gear are through hardened, precision shaped, and ground to permit to run at high speeds.
5. The pinion is made of steel with 150 Bhn, and gear is cast iron.
6. The gearset goes on a maximum of c=18 \frac{1}{2} in. center distance. However, to keep pitch-line velocity down, gears are designed with as small a center distance as possible.
7. To keep stresses down, a wide face width =8 in. large gearset is used.
8. The generator efficiency is 95%.
See Figures 12.6 and 12.8 and Tables 11.5 through 11.9.
a. The geometric quantities for the gearset are obtained by using Equations (12.1) through 12.5. Therefore,
p_n=p \cos \psi, \quad p_a=p \cot \psi=\frac{p_n}{\sin \psi} (12.1)
P p=\pi, \quad P_n p_n=\pi, \quad P_n=\frac{P}{\cos \psi}, \quad P=\frac{N}{d} (12.2)
m=\frac{1}{P} \quad m_n=\frac{1}{P_n} (12.2′)
\tan \phi_n=\tan \phi \cos \psi (12.3)
d=\frac{N p}{\pi}=\frac{N p_n}{\pi \cos \psi}=\frac{N}{P_n \cos \psi} (12.4)
c=\frac{d_1+d_2}{2}=\frac{p}{2 \pi}\left(N_1+N_2\right)=\frac{N_1+N_2}{2 P_n \cos \psi} (12.5)
\phi=\tan ^{-1} \frac{\tan \phi_n}{\cos \psi}=\tan ^{-1} \frac{\tan 20^{\circ}}{\cos 30^{\circ}}=22.8^{\circ}
P=P_n \cos \psi=10 \cos 30^{\circ}=8.66
d_p=\frac{N_p}{P}=\frac{35}{8.66}=4.04 \text { in. }
N_g=N_p\left(\frac{n_p}{n_g}\right)=35\left(\frac{8000}{1000}\right)=280
d_g=\frac{N_p}{P}=\frac{280}{8.66}=32.3 in.
It follows that
\begin{aligned} c & =\frac{1}{2}\left(d_p+d_g\right) \\ & =\frac{1}{2}(4.04+32.3)=18.17 in . \end{aligned}
Comment: The condition that the center distance is not to exceed 18.5 is satisfied.
The pitch-line velocity equals
V=\frac{\pi d n}{12}=\frac{\pi(4.04) 8000}{12}=8461 fpm
The power that the gear must transmit is about 335/0.95=353 hp. The transmitted load is then
F_t=\frac{33,000 hp }{V}=\frac{33,000(353)}{8461}=1.38 kips
As a result, the radial, axial, and normal components of tooth force are, using Equation (12.10),
\begin{aligned} & F_r=F_t \tan \phi \\ & F_a=F_t \tan \psi \\ & F_n=\frac{F_t}{\cos \phi_n \cos \psi} \end{aligned} (12.10)
\begin{gathered} F_r=F_t \tan \phi=1380 \tan 22.8^{\circ}=580 lb \\ F_a=F_t \tan \psi=1380 \tan 30^{\circ}=797 lb \\ F_n=\frac{F_t}{\cos \phi_n \cos \psi}=\frac{1380}{\cos 20^{\circ} \cos 30^{\circ}}=1696 lb \end{gathered}b. From Equation (12.7b), we have
N^{\prime}=\frac{N}{\cos ^3 \psi} (12.7b)
N^{\prime}=\frac{N}{\cos ^3 \psi}=\frac{35}{\cos ^3 30^{\circ}}=53.9
Then, for 53.9 teeth and \phi=22.8^{\circ} by interpolation from Table 11.2, Y =0.452. Using Table 11.3, \sigma_o \approx 18 ksi. Applying Equation ((11.33), modified) with K_f =1,
F_b=\frac{\sigma_o b}{K_f} \frac{Y}{P} (11.33)
F_b=\sigma_o b \frac{Y}{P_n}=18(8) \frac{0.452}{10}=6.51 kips
Corresponding to \phi=22.8^{\circ} , interpolating in Table 11.9, K \approx 68 psi. Through the use of Equation (11.40),
Q=\frac{2 N_g}{N_p+N_g} (11.40)
Q=\frac{2 N_g}{N_p+N_g}=\frac{2(280)}{35+280}=\frac{112}{63}
The limit load for wear, by Equation ((11.38), modified), is
F_w=d_p b Q K (11.38)
\begin{aligned} F_w & =\frac{d_p b Q K}{\cos ^2 \psi} \\ & =\frac{4.04(8)(68)(112)}{60\left(\cos ^2 30^{\circ}\right)}=5.21 kips \end{aligned}
Because the permissible load in wear is less than that allowable in bending, it is used as the dynamic load F_d . So from Equation ((11.24c), modified),
F_d=\frac{78+\sqrt{V}}{78} F_t \quad(\text { for } V>4000 fpm ) (11.24c)
\begin{aligned} F_d & =\frac{78+\sqrt{V}}{78} F_t \\ 5.21 & =\frac{78+\sqrt{8461}}{78} F_t=2.18 F_t \end{aligned}
or
F_t=2.39 kips
c. Application of Equation (11.36) leads to
\sigma_{\text {all }}=\frac{S_t K_L}{K_T K_R} (11.36)
\sigma_{\text {all }}=\frac{S_t K_L}{K_T K_R}
where
S_t = 20.5 ksi (interpolating, Table 11.6 for a Bhn of 150)
K_L = 1.0 (indefinite life, Table 11.7)
K_T = 1.0 (from Section 11.9)
K_R = 1.25 (by Table 11.8)
The preceding equation is therefore
\sigma_{\text {all }}=\frac{20,500(1.0)}{(1.0)(1.25)}=16.4 ksi
The tangential force, by Equation (11.35) with \sigma =\sigma _{all} , is
\begin{aligned} & \sigma=F_t K_o K_{ \upsilon } \frac{P}{b} \frac{K_s K_m}{J} \quad \text { (US customary units) } \\ & \sigma=F_t K_o K_{ \upsilon } \frac{1.0}{b m} \frac{K_s K_m}{J} \text { (SI units) } \end{aligned} (11.35)
F_t=\frac{\sigma_{\text {all }}}{K_o K_{ \upsilon }} \frac{b}{P} \frac{J}{K_s K_m} (a)
Here, we have
K_o =1.5 (Table 11.4)
K_ {\nu} =2.18 (from curve B of Figure 11.15)
K_s =1.1 (from Section 12.5)
K_m =1.5 (by Table 11.5)
J =0.47 (for N_p =35 and \psi= 30, Figure 12.6(a))
J − multiplier=1.02 (for N_g=280 and \psi= 30, Figure 12.6(b))
J =1.02×0.47=0.48
Equation (a) is then
F_t=\frac{16,400(8)(0.48)}{(1.5)(2.18)(8.66)(1.0)(1.5)}=1.48 kips
compared to the approximate result 2.39 kips for part b.
Comments: The tangential load capacity of the gearset, 1.48 kips, is larger than the force to be transmitted, 1.38 kips (allowance is made for 95% generator efficiency); the gears are safe. Since a wide face width is used, the design should be checked for combined bending and torsion at the pinion [1].
Remarks: A turbine is a rotary mechanical device that extracts energy from a fluid flow and converts it into work. This work created by a turbine-generator assembly can be used for generating electrical power. A turbine is a turbomachine with at least one moving part termed a rotor assembly, that is, a shaft with blades attached. Moving fluid acts on the blades so that they move and transmit rotational energy to the rotor. Basic types of turbines are water, steam, gas, and wind turbines. The identical principles apply to all turbines; however, their specific designs differ sufficiently to merit separate descriptions.
Turbines are often part of a large machine. Almost all electric power on earth is generated with a turbine of some type. Gas, steam, and water turbines have a casing around the blades that contains and controls the working fluid. A steam turbine is used for the generation of electricity in thermal power plants, such as plants using coal, fuel oil, or nuclear fuel. Gas turbines are sometimes referred to as turbine engines. Such engines usually include an inlet, fan, compressor, combustor, and nozzle in addition to one or more turbines. Water turbines convert the potential energy of water on an upstream level into kinetic energy.
A wind turbine, illustrated in the following photo, is designed to convert the wind energy that exists at a location to electricity. We observe that, in this turbine there are three components: the blades converting wind energy to low speed rotational energy; the housing (including a drive shaft, gear train, high speed shaft, couplings, and generator); the structural support consisting of tower, rotating thrust bearing, and rotor yaw mechanism. Aerodynamic modeling is used to find the optimum tower height, control systems, number of blades, and blade shape.
TABLE 11.5 Mounting Correction Factor K_m |
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Face Width (in.) | ||||
Condition of Support | 0–2 | 6 | 9 | 16 up |
Accurate mounting, low bearing clearances, maximum deflection, precision gears | 1.3 | 1.4 | 1.5 | 1.8 |
Less rigid mountings, less accurate gears, contact across the full face Accuracy and mounting such that less than full-face contact exists |
1.6 Over 2. 2 |
1.7 | 1.8 | 2.2 |
TABLE 11.6 Bending Strength S_t of Spur, Helical, and Bevel Gear Teeth |
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S_t | ||||
Material | Heat Treatment | Minimum Hardness or Tensile Strength | ksi | (MPa) |
Steel | Normalized | 140 Bhn | 19−25 | (131−172) |
Q&T | 180 Bhn | 25−33 | (172−223) | |
Q&T | 300 Bhn | 36−47 | (248−324) | |
Q&T | 400 Bhn | 42−56 | (290−386) | |
Case carburized | 55 R_C | 55−65 | (380−448) | |
60 R_C | 55−70 | (379−483) | ||
Nitrided AISI-4140 | 48 R_C case | 34−45 | (234−310) | |
300 Bhn core | ||||
Cast iron | ||||
AGMA grade 30 | 175 Bhn | 8.5 | (58.6) | |
AGMA grade 40 | 200 Bhn | 13 | (89.6) | |
Nodular iron ASTM grade | ||||
60–40–18 | 15 | (103) | ||
80–55–06 | Annealed | 20 | (138) | |
100–70–18 | Normalized | 26 | (179) | |
120–90–02 | Q&T | 30 | (207) | |
Bronze, AGMA 2C | Sand cast | 40 ksi (276 MPa) | 5.7 | (39.3) |
Source: ANSI/AGMA Standard 218.01. | ||||
Note: Q&T, quenched and tempered. |
TABLE 11.7 Life Factor K_L for Spur and Helical Steel Gears |
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Number of Cycles | 160 Bhn | 250 Bhn | 450 Bhn | Case Carburized (55–63 R_C ) |
10^3 | 1.6 | 2.4 | 3.4 | 2.7–4.6 |
10^4 | 1.4 | 1.9 | 2.4 | 2.0–3.1 |
10^5 | 1.2 | 1.4 | 1.7 | 1.5–2.1 |
10^6 | 1.1 | 1.1 | 1.2 | 1.1–1.4 |
10^7 | 1.0 | 1.0 | 1.0 | 1.0 |
Source: ANSI/AGMA Standard 218.01. |
TABLE 11.8 Reliability Factor K_R |
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Reliability (%) | 50 | 90 | 99 | 99.9 | 99.99 |
Factor K_R | 0.70 | 0.85 | 1.00 | 1.25 | 1.50 |
Source: From ANSI/AGMA Standard 2001-C95. |
TABLE 11.9 Surface Endurance Limit S_e and Wear Load Factor K for Use in the Buckingham Equation |
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K | ||||||
Materials in Pinion and Gear | S_e | \phi=20^{\circ} | \Phi=25^{\circ} | |||
Both steel gears, with average | 50 | (345) | 41 | (0.283) | 51 | (0.352) |
Bhn of pinion and gear | ||||||
150 | ||||||
200 | 70 | (483) | 79 | (0.545) | 98 | (0.676) |
250 | 90 | (621) | 131 | (0.903) | 162 | (1.117) |
300 | 110 | (758) | 196 | (1.352) | 242 | (1.669) |
350 | 130 | (896) | 270 | (1.862) | 333 | (2.297) |
400 | 150 | (1034) | 366 | (2.524) | 453 | (3.124) |
Steel (150 Bhn) and cast iron | 50 | (354) | 60 | (0.414) | 74 | (0.510) |
Steel (200 Bhn) and cast iron | 70 | (483) | 119 | (0.821) | 147 | (1.014) |
Steel (250 Bhn) and cast iron | 90 | (621) | 196 | (1.352) | 242 | (1.669) |
Steel (150 Bhn) and phosphor bronze | 59 | (407) | 62 | (0.428) | 77 | (0.531) |
Steel (200 Bhn) and phosphor bronze | 65 | (448) | 100 | (0.690) | 123 | (0.848) |
Steel (250 Bhn) and phosphor bronze | 85 | (586) | 184 | (1.269) | 228 | (1.572) |
Cast iron and cast iron | 90 | (621) | 264 | (1.821) | 327 | (2.555) |
Cast iron and phosphor bronze | 83 | (572) | 234 | (1.614) | 288 | (1.986) |
TABLE 11.2 Values of the Lewis Form Factor for Some Common Full-Depth Teeth |
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No. of Teeth | 20°Y | 25° Y | No. of Teeth | 20° Y | 25° Y |
12 | 0.245 | 0.277 | 26 | 0.344 | 0.407 |
13 | 0.264 | 0.293 | 28 | 0.352 | 0.417 |
14 | 0.276 | 0.307 | 30 | 0.358 | 0.425 |
15 | 0289 | 0.320 | 35 | 0.373 | 0.443 |
16 | 0.295 | 0.332 | 40 | 0.389 | 0.457 |
17 | 0.302 | 0.342 | 50 | 0.408 | 0.477 |
18 | 0.308 | 0.352 | 60 | 0.421 | 0.491 |
19 | 0.314 | 0.361 | 75 | 0.433 | 0.506 |
20 | 0.320 | 0.369 | 100 | 0.446 | 0.521 |
21 | 0.326 | 0.377 | 150 | 0.458 | 0.537 |
22 | 0.33 | 0.384 | 200 | 0.463 | 0.545 |
24 | 0.337 | 0.396 | 300 | 0.471 | 0.554 |
25 | 0.340 | 0.402 | Rack | 0.484 | 0.566 |
TABLE 11.3 Allowable Static Bending Stresses for Use in the Lewis Equation |
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Material | Treatment | \sigma_0 | Average Bhn | |
ksi | (MPa) | |||
Cast iron | ||||
ASTM 35 | 12 | (82.7) | 210 | |
ASTM 50 | 15 | (103) | 220 | |
Cast steel | ||||
0.20% C | 20 | (138) | 180 | |
0.20% C | WQ&T | 25 | (172) | 250 |
Forged steel | ||||
SAE 1020 | WQ&T | 18 | (124) | 155 |
SAE 1030 | 20 | (138) | 180 | |
SAE 1040 | 25 | (172) | 200 | |
SAE 1045 | WQ&T | 32 | (221) | 205 |
SAE 1050 | WQ&T | 35 | (241) | 220 |
Alloy steels | ||||
SAE 2345 | OQ&T | 50 | (345) | 475 |
SAE 4340 | OQ&T | 65 | (448) | 475 |
SAE 6145 | OQ&T | 67 | (462) | 475 |
SAE 65 (phosphor bronze) | 12 | (82 7) | 100 | |
Note: WQ&T, water-quenched and tempered; OQ&T, oil-quenched and tempered. |
TABLE 11.4 Overload Correction Factor K_o |
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Load on Driven Machine | |||
Source of Power | Uniform | Moderate Shock | Heavy Shock |
Uniform | 1.00 | 1.25 | 1.75 |
Light shock | 1.25 | 1.50 | 2.00 |
Medium shock | 1.50 | 1.75 | 2.25 |