Reference ID: MET-CDC5 | Process Engineering Reference Sheets Calculation Guide
Introduction & Context
ISO 10816-3 overall velocity is the de-facto screening tool used by maintenance crews to decide whether a large, rigidly-mounted machine (hammer-mills, fans, compressors, etc.) is still fit for service. A single-point velocity spectrum, integrated to vrms, is compared with an empirically-derived limit that depends on machine class and rotational speed. The method is purely empirical—no structural or mass-flow models are required—so it is robust enough for daily work-order decisions.
Methodology & Formulas
Verify operating speed lies within ±5 % of the nominal value:
Range checks for correlation validity (typical bounds):
Parameter
Lower bound
Upper bound
RPM
\text{MIN\_RPM} (=120)
\text{MAX\_RPM} (=15000)
Power (kW)
\text{MIN\_POWER\_KW} (=15)
\text{MAX\_POWER\_KW} (=300)
vrms (mm/s)
\text{MIN\_V\_RMS} (=0.4)
\text{MAX\_V\_RMS} (=45)
Key parameters are:
Overall velocity in mm/s RMS for ISO 10816-3 zone checks
Peak-to-peak displacement (µm) on the mill girth gear for teeth mesh anomalies and eccentricity
High-frequency acceleration (g RMS) in bearing pass bands to expose bearing race defects and gear pitting
Shaft absolute or relative displacement (µm) for sleeve-bearing stability (oil whirl/whip)
Tracking these KPIs gives a balanced view of forcing frequency amplitudes vs. severity standards and supports early escalation of corrective actions.
Use order-domain analysis: tachometer the mill speed and resample data into revolutions. Liner impacts occur at integer multiples of rotation (1×, 2×, 3× RPM orders), whereas gear fault harmonics sit at:
1×, 2×, 3× GMF (Gear Mesh Frequency = Number of Teeth × RPM)
Sidebands spaced ± 1× running speed around GMF and its harmonics
Compare waterfall spectra across loaded vs. shutdown coast-down; liner peaks drop significantly with load loss, while gear-related peaks remain strongly correlated with shaft speed.
Apply load-corrected alarms: base alarm level on historical RMS velocity vs. motor power draw regression
Time-delay triggers ≥ 5 s to ride out short pounding spikes from cascading charge
Band-pass filters around 3-8 kHz (shell resonant modes) to suppress broad-band impact noise from the cascade
Allow separate thresholds for startup vs. steady-state using a PLC signal indicating mill run status and current
These rules can reduce 40-50% of nuisance trips while maintaining sensitivity to incipient bearing and gear defects.
Trend these indicators monthly:
Shell impact energy (e.g., RMS acceleration in the 500-2000 Hz band) rising > 0.5 g month-on-month
Oil analysis Wear Particle Quantification (PQ Index or similar) from ferrography
Gear Mesh Frequency (GMF) amplitude deviation vs. a healthy baseline > +3 dB
A two-phase approach lets you extend 10-15% of the liner life: plan a partial liner change when condition (1) or (2) triggers, and a full reline when all three indicators align. Data-driven maintenance has sustained ≥ 5,000 hours of extra runtime compared with fixed calendar-based stops.
Use 316 L stainless steel armoured cables with PTFE/Teflon insulation rated for continuous operation at 180°C minimum
Mount sensors on clean, grounded, machined pads; torque to manufacturer specification (e.g., 20 Nm) using thread-locking compound (e.g., Loctite 243)
Install stainless steel IP68/69K conduit seal glands and consider a continuous, low-pressure instrument air purge at 0.1-0.2 bar to prevent dust ingress
Perform quarterly bias voltage checks; replace accelerometer units showing a drift > ±10% of specification (e.g., > 0.5 V from a 10 V system) to avoid signal degradation and spiking
Adhering to these steps has reduced annual probe replacement rates from ~30% to under 5% in harsh mill environments.
Worked Example: Vibration Analysis for Hammer-Mill Bearing
A predictive-maintenance crew assesses a hammer-mill with a rigid concrete foundation operating under steady load. The goal is to determine if the bearing is approaching failure based on a single-point velocity spectrum measurement, following ISO 10816-3 guidelines for Class III machines.
Knowns:
Nominal rotational speed: 1500.000 rpm
Measured rotational speed: 1500.000 rpm
Machine power: 75.000 kW
Measured overall velocity (vrms): 4.200 mm/s
ISO 10816-3 Class III limit for 1500 rpm: 4.500 mm/s
ISO validation minimum RPM: 120.000
ISO validation maximum RPM: 15000.000
ISO validation minimum power: 15.000 kW
ISO validation maximum power: 300.000 kW
ISO validation minimum velocity: 0.400 mm/s
ISO validation maximum velocity: 45.000 mm/s
RPM tolerance factor: 0.050
Good status multiplier: 0.700
Caution status multiplier: 1.000
Step-by-Step Calculation:
Validate nominal rpm against ISO 10816-3 Class III bounds. Nominal rpm = 1500.000, which is between 120.000 and 15000.000. Condition satisfied.
Validate machine power against ISO bounds. Power = 75.000 kW, which is between 15.000 kW and 300.000 kW. Condition satisfied.
Validate measured vrms against ISO bounds. vrms = 4.200 mm/s, which is between 0.400 mm/s and 45.000 mm/s. Condition satisfied.
Verify measured rpm is within ±5% of nominal rpm. With nominal rpm = 1500.000 and tolerance = 0.050, allowable range is 1425.000 to 1575.000 rpm. Measured rpm = 1500.000, which is within range. Condition satisfied.
Determine the good threshold. good threshold = GOOD_MUL * ISO_LIMIT = 0.700 * 4.500 mm/s = 3.150 mm/s.
Compare measured vrms to thresholds. measured vrms = 4.200 mm/s. Since 3.150 mm/s < 4.200 mm/s ≤ 4.500 mm/s, the status is CAUTION.
Final Answer: The bearing vibration status is CAUTION. The measured overall velocity of 4.200 mm/s is below the ISO limit of 4.500 mm/s but above the good threshold of 3.150 mm/s. Schedule bearing inspection and/or replacement at the next planned outage.
"Un projet n'est jamais trop grand s'il est bien conçu."— André Citroën
"La difficulté attire l'homme de caractère, car c'est en l'étreignant qu'il se réalise."— Charles de Gaulle