Source: https://guthlabs.ai/docs/instruments/brayton-cycle-efficiency-calculator/
instrument / verified-clean
# Brayton Cycle Efficiency Calculator
The current ledger marks this instrument verified clean within the source-bound verification corpus.
Status: **VERIFIED_CLEAN**Lifecycle: **verified-clean**
## Inspectable records
[01**Overview**Purpose and lifecycle]()[02**Mechanism**Method and assumptions]()[03**Implementation**Binding and validation]()[04**Qualification**Evidence and errata]()
## Ledger state
The current ledger marks this instrument verified clean within the source-bound verification corpus.
**Area**: Thermodynamics, Fluids & Aero
**Tranche**: tranche-4
**Evidence ID**: t4-024
**Ledger rows**: 1
No ledger note is attached.
## Review findings
The base simple-cycle efficiency formula is standard, but the specification is incomplete for its claimed outputs and does not define the regenerative efficiency adjustment. Verdict remains NEEDS_REVIEW until the missing work equations, regeneration model, temperature units, input constraints, and zero-denominator behavior are explicitly specified.
### Formula and scope findings
- The base formula η=1−1/rp^((γ−1)/γ) is correct only for an ideal simple Brayton cycle with constant γ, isentropic compression and expansion, and no pressure losses.
- No formula is provided for compressor-exit temperature, turbine-exit temperature, compressor work, turbine work, net specific work, or back-work ratio, even though those outputs are claimed.
- The regenerative adjustment is unspecified: effectiveness ε alone does not define η without the regenerator temperature relations and heat-input definition.
- A standard regeneration model must specify T2r=T2+ε(T4−T2), T4r=T4−ε(T4−T2), and η=(wt−wc)/qin, with qin=Cp(T3−T2r).
- Regeneration is physically useful only when T4>T2; otherwise the regenerator should be bypassed or ε should be treated as zero.
- The listed formula does not use turbine/compressor inlet temperatures or Cp, so it cannot by itself produce specific work or back-work ratio.
### Unit assumptions
- Temperatures are absolute temperatures in kelvin for all thermodynamic formulas; Celsius or Fahrenheit values must be converted before multiplication or division.
- Pressure ratio rp is dimensionless and means compressor outlet absolute pressure divided by compressor inlet absolute pressure.
- γ is dimensionless and assumed constant, with γ>1; the examples use γ=1.4 for air.
- Cp is assumed constant and expressed in kJ/(kg·K); the examples use Cp=1.005 kJ/(kg·K), so work outputs are in kJ/kg.
- The test vectors use the standard ideal-cycle relations T2=T1·rp^((γ−1)/γ), T4=T3/rp^((γ−1)/γ), wc=Cp(T2−T1), wt=Cp(T3−T4), and wnet=wt−wc.
- For regenerated cases, the standard no-pressure-loss regenerator model and ε between 0 and 1 are assumed.
## Boundary hardening
### Recorded hazards
- Division by zero occurs for back-work ratio when turbine work is zero, including the rp=1 boundary case.
- The exponent requires γ>1; γ=1 causes a degenerate zero-efficiency result, and γ≤1 is not a valid ordinary ideal-gas Brayton-cycle input.
- rp must be positive; rp=0 is invalid and negative pressure ratios are nonphysical.
- Regenerator effectiveness should be constrained to 0≤ε≤1.
- The regenerator formula requires a specified operating condition such as T4>T2; applying regeneration when T4≤T2 can produce nonphysical heat flow or misleading efficiency.
- If T3≤T2, the heat-addition denominator is zero or negative and efficiency is undefined or nonphysical.
- Celsius inputs used directly instead of kelvin produce incorrect temperatures and work values.
- Cp must be supplied or given a clearly documented default; changing Cp changes specific work but not the ideal simple-cycle efficiency.
## Errata and corrections
No applied erratum is attached to this unique-name record.
## Inspectable example
4 review vectors are recorded. One source-bound sample is shown below.
````
{
"inputs": {
"rp": 4,
"gamma": 1.4,
"T1_K": 288,
"T3_K": 1400,
"Cp_kJ_per_kgK": 1.005,
"regeneration": false
},
"expected_outputs": {
"eta": 0.32705,
"specific_work_kJ_per_kg": 319.497,
"back_work_ratio": 0.30569
},
"working": "a=(γ−1)/γ=0.4/1.4=2/7. F=rp^a=4^(2/7)=1.485994. T2=T1·F=288·1.485994=427.966 K. T4=T3/F=1400/1.485994=942.130 K. wc=Cp(T2−T1)=1.005·(427.966−288)=1.005·139.966=140.666 kJ/kg. wt=Cp(T3−T4)=1.005·(1400−942.130)=1.005·457.870=460.163 kJ/kg. wnet=wt−wc=460.163−140.666=319.497 kJ/kg. η=1−1/F=1−1/1.485994=0.32705. Back-work ratio=wc/wt=140.666/460.163=0.30569."
}
````
## Related workflows
[Engine Cycle Comparatorturbine]()
## Sources and evidence
These pointers bind the page to evidence. They do not grant authority or collapse verification into deployment.
- `VERIFIED_LEDGER.json · VERIFIED_CLEAN`
- `evidence-tranche4/tranche4-results.json`