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Turbine Blade Natural Frequency & Campbell Check
Calculate the first-mode natural frequency of a turbine blade (cantilever beam model) and check for harmonic crossings within the operating speed range using a simplified Campbell diagram.
Results
Cantilever Beam Natural Frequency
A turbine blade can be modeled as a cantilever beam fixed at the root. The natural frequencies are:
- λn — eigenvalue: λ₁ = 1.8751, λ₂ = 4.6941, λ₃ = 7.8548
- E — Young’s modulus (Pa)
- I — second moment of area (m⁴) = b·h³/12 for rectangular cross-section
- ρ — material density (kg/m³)
- A — cross-sectional area (m²) = b·h
- L — blade length (m)
Campbell Diagram
The Campbell diagram plots blade natural frequency (horizontal lines) against engine order excitation lines (diagonal lines: f = n × RPM/60). Intersections within the operating speed range indicate potential resonance.
A minimum 10% separation margin between natural frequencies and excitation frequencies at operating speed is generally required.
Mode Shape Ratios
| Mode | λn | fn / f₁ ratio | Character |
|---|---|---|---|
| 1st | 1.8751 | 1.000 | First bending |
| 2nd | 4.6941 | 6.267 | Second bending |
| 3rd | 7.8548 | 17.55 | Third bending |
Given: L = 500 mm, thickness h = 12 mm, width b = 80 mm, Steel (E = 200 GPa, ρ = 7850 kg/m³)
I = 80 × 12³ / 12 = 11,520 mm⁴ = 1.152 × 10⁻⁸ m⁴
A = 80 × 12 = 960 mm² = 9.6 × 10⁻⁴ m²
f₁ = (1.8751² / (2π)) × √(200×10⁹ × 1.152×10⁻⁸ / (7850 × 9.6×10⁻⁴ × 0.5⁴))
f₁ ≈ 44.8 Hz
⚠️ Note: This is a simplified uniform cantilever beam model. Actual turbine blades have tapered profiles, twist, shrouds, platform effects, centrifugal stiffening, and temperature-dependent material properties that significantly affect natural frequencies. Use FEA for detailed design.
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