Automotive Headliner Sound Transmission Loss Predictor
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Doubling the mass buys six decibels. Splitting the same mass into two skins with foam between them buys far more — everywhere except at the resonance it creates.
Sound Transmission Loss
—dB
Attenuation through the full stack at the chosen frequency
Loss Breakdown
Total Surface Mass
—kg/m²
Mass-Law Contribution
—dB
Mass-Air-Mass Resonance
—Hz
Double-Wall Gain
—dB
Energy Transmitted
—%
The double-wall gain is applied as a clean 18 dB per octave above resonance, which real panels never quite achieve and which ignores the dip at the resonance itself — right at that frequency the assembly performs worse than its mass alone, and this model does not show that trough. Coincidence at high frequency is also absent, so the numbers above roughly 2 kHz on a stiff substrate are optimistic. Mass law is a diffuse-field infinite-panel result; a real headliner is a small, curved, edge-bonded panel and flanking through the pillars usually governs the cabin anyway.
Using this calculator
About the Automotive Headliner Sound Transmission Loss Predictor
The formula
This is the expression the tool evaluates. Every term is named underneath, with the unit it must be supplied in.
Each input feeds the expression evaluated in the browser; the symbol table below names every term and its unit.
Symbols used above
Symbol
Stands for
Unit
fabricMass
Facing Fabric Mass
g/m²
substrateMass
Substrate Mass
g/m²
foamThickness
Foam Core Thickness
mm
foamDensity
Foam Density
kg/m³
foamModulus
Foam Dynamic Modulus
kPa
frequency
Frequency of Interest
Hz
transmissionLoss
Sound Transmission Loss
dB
surfaceMass
Total Surface Mass
kg/m²
massLawLoss
Mass-Law Contribution
dB
resonanceFrequency
Mass-Air-Mass Resonance
Hz
doubleWallGain
Double-Wall Gain
dB
transmittedEnergy
Energy Transmitted
%
How the result is derived
Step by step, from the values you type to the figure on screen.
The 6 inputs are read from the form on every keystroke: Facing Fabric Mass, Substrate Mass, Foam Core Thickness, Foam Density, Foam Dynamic Modulus and Frequency of Interest.
Each value is checked against the accepted range in the input table below. A value outside its range stops the calculation rather than producing a misleading figure — the results blank out and a message appears.
The validated values are substituted into the expression above, which resolves Sound Transmission Loss together with every supporting figure in one pass — no value is carried over from a previous entry.
The supporting outputs — Total Surface Mass, Mass-Law Contribution, Mass-Air-Mass Resonance, Double-Wall Gain and Energy Transmitted — come from the same pass, so they always describe the same case as the headline figure.
Results are rounded for display only. The full-precision value is used throughout the chain, so reading a rounded intermediate figure back into the tool by hand can shift the last digit.
What each input means
Where to read each value on the floor, the unit it must be in, and the range the tool accepts.
Input
Unit
Accepted range
Default
What it means
Facing Fabric Mass
g/m²
40 to 2000 g/m²
250
Substrate Mass
g/m²
100 to 6000 g/m²
900
Foam Core Thickness
mm
1 to 60 mm
12
Foam Density
kg/m³
8 to 200 kg/m³
30
Foam Dynamic Modulus
kPa
5 to 1000 kPa
60
Through-thickness stiffness of the core; sets the resonance.
Frequency of Interest
Hz
50 to 8000 Hz
1000
What the tool returns
The headline figure and every supporting value it is built from.
Output
Unit
What it tells you
Sound Transmission Loss (headline result)
dB
Attenuation through the full stack at the chosen frequency
Total Surface Mass
kg/m²
Mass-Law Contribution
dB
Mass-Air-Mass Resonance
Hz
Double-Wall Gain
dB
Energy Transmitted
%
Worked example
Given
Facing Fabric Mass
250 g/m²
Substrate Mass
900 g/m²
Foam Core Thickness
12 mm
Foam Density
30 kg/m³
Foam Dynamic Modulus
60 kPa
Frequency of Interest
1000 Hz
The tool loads with this case already solved — the Sound Transmission Loss shown above is its answer. Change one value and the difference from this baseline is the sensitivity of the result to that variable.
How to use it
Work through the input groups in order — Layer Stack and Acoustic Conditions. The defaults are a realistic case, so you can change one value at a time and watch what moves.
There is no calculate button. Every figure recalculates as you type or drag, which is what makes this usable for a what-if sweep rather than a single answer.
Read Sound Transmission Loss in the dark results panel — that is the headline figure, expressed in dB.
Check the supporting rows underneath (Total Surface Mass, Mass-Law Contribution, Mass-Air-Mass Resonance, Double-Wall Gain and Energy Transmitted) before acting on the headline — they are where an implausible input usually shows itself first.
Reset to defaults returns every field to the reference case, which is the quickest way to check whether a surprising result came from the tool or from an input you had changed earlier.
Where this is used
Process planning — establishing Sound Transmission Loss before a trial is booked, so machine time and material in Acoustic, Thermal & Metamaterial Textiles are committed against a calculated figure rather than an estimate.
Costing and quotation — Sound Transmission Loss is an input to the cost sheet, and quoting from a worked number rather than a remembered one is what keeps a margin intact.
Troubleshooting — when the floor result drifts from plan, entering the measured values (starting with Facing Fabric Mass) shows how much of the gap in Sound Transmission Loss each variable explains.
Teaching and study — the accepted ranges bracket normal Acoustic, Thermal & Metamaterial Textiles practice, so moving one variable at a time shows the shape of the relationship rather than a single answer.
Assumptions and limits
The double-wall gain is applied as a clean 18 dB per octave above resonance, which real panels never quite achieve and which ignores the dip at the resonance itself — right at that frequency the assembly performs worse than its mass alone, and this model does not show that trough. Coincidence at high frequency is also absent, so the numbers above roughly 2 kHz on a stiff substrate are optimistic. Mass law is a diffuse-field infinite-panel result; a real headliner is a small, curved, edge-bonded panel and flanking through the pillars usually governs the cabin anyway.
Every input is bounded to the range normal practice occupies (Facing Fabric Mass 40 to 2000 g/m², Substrate Mass 100 to 6000 g/m² and Foam Core Thickness 1 to 60 mm, and so on for the rest). Those bounds are guard rails against typing errors, not a claim that the formula fails one unit outside them.
The calculation is deterministic: the same inputs always give the same result. It carries no allowance for machine condition, operator skill, ambient conditions or lot-to-lot material variation unless an input above explicitly represents one.
Nothing is sent anywhere. The maths runs in your browser, so the numbers you type never leave the page.
Questions people ask
What do I need to know before using the Automotive Headliner Sound Transmission Loss Predictor?
Have these to hand: Facing Fabric Mass, Substrate Mass, Foam Core Thickness, Foam Density, Foam Dynamic Modulus and Frequency of Interest. With those entered, the tool returns Sound Transmission Loss immediately.
What exactly is Sound Transmission Loss?
Attenuation through the full stack at the chosen frequency. It is reported in dB. It is derived from Facing Fabric Mass, Substrate Mass, Foam Core Thickness, Foam Density, Foam Dynamic Modulus and Frequency of Interest, and is the figure the rest of the Acoustic, Thermal & Metamaterial Textiles calculation is built around.
Which units does this calculator expect?
Enter Facing Fabric Mass in g/m², Substrate Mass in g/m², Foam Core Thickness in mm, Foam Density in kg/m³, Foam Dynamic Modulus in kPa and Frequency of Interest in Hz. Mixing unit systems is the most common cause of a result that looks an order of magnitude wrong — convert before typing, not after reading.
What are the other figures under the main result?
They are the intermediate quantities the calculation passes through: Total Surface Mass, Mass-Law Contribution, Mass-Air-Mass Resonance, Double-Wall Gain and Energy Transmitted. They are shown because a headline number nobody can trace is a number nobody trusts — checking them against your own expectation is the fastest way to confirm the inputs were read as you intended.
Can I rely on this for a production decision?
The double-wall gain is applied as a clean 18 dB per octave above resonance, which real panels never quite achieve and which ignores the dip at the resonance itself — right at that frequency the assembly performs worse than its mass alone, and this model does not show that trough. Coincidence at high frequency is also absent, so the numbers above roughly 2 kHz on a stiff substrate are optimistic. Mass law is a diffuse-field infinite-panel result; a real headliner is a small, curved, edge-bonded panel and flanking through the pillars usually governs the cabin anyway. Treat the output as an engineering estimate that narrows the trial window, not as a substitute for the trial.