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Technical Manual · Thermal Lab

Liquid-to-Chip System Modelling Lab — Methodology & Formulas

Every input, equation, constant, output, and reference behind the LTC steady-state solver. All math is executed by the deterministic engine js/ltc-system-modelling-lab.js (function computeModel) — no back-solved constants, no random values. This is a SIMULATED / educational model; it is not a substitute for site-specific hydraulic or thermal commissioning data.

Solver computeModel (inline) Basis ASHRAE / HX Institute / ISO/IEC 30134 Sliders 5 primary Outputs 12+ Status SIMULATED — educational
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01 Purpose & engineering basis

The lab sizes and balances a liquid-to-chip AI campus: coolant flow and pump power, CDUs, the heat rejection for the liquid loop, the CRAHs, chilled water, chillers and towers for the heat liquid cooling does not capture, the cooling of UPS and transformer losses, and the PUE, WUE, CUE, energy, water and cost that follow.

Since v3.17.0 every physical number comes from the workbench’s shared plant engine, js/ltc-plant.js, through js/ltc-lab-plant.js. The engine is a steady-state energy balance that closes: electricity in equals heat out on every path, asserted to within 0.5 % on 202 test plants (it closes to about 10⁻¹⁴). The lab’s design scores, risk index and confidence remain its own screening layer. The same plant is the one every LTC Workbench page reads, so a change here moves the Tier simulator, ASHRAE, ISO, TIA and NFPA tools, and the reverse.

02 Inputs

Three tiers. Most readers touch only the first. Everything else is auto: derived, or a stated default, until changed.

TierInputsDefault
DesignIT load · liquid capture · TCS supply (return follows at ΔT 10 K) · plant configuration (4 presets) · CDU feed single/dual · redundancy100 MW · 85 % · 35 °C · dry coolers + water-cooled chillers · single · N+1
SiteClimate (illustrative tropical / temperate / arid bins, or bins pasted from the site’s EPW) · grid emission factor · renewable share · heat reuse · electricity and water tariffstropical · 0.72 kg/kWh · 0 % · 0 % · 0.10 /kWh · 1.5 /m³
Advanced55 engine inputs: unit sizes, approaches, heads and efficiencies, chiller COP and staging, electrical losses, hall geometry, thermal massesstated in LTCPlant.DEFAULTS; ASSUMED values are typical design values, not a vendor selection

The lab’s own panel still carries its 61 controls under Advanced · auto; the six primary sliders and the site fields write the shared plant on every run. A plant chosen on another workbench page is read first, so the lab’s defaults never overwrite it.

03 Calculation methodology

One operating point = IT at a utilisation, ambient dry and wet bulb. The design day sizes the plant; the year is the same plant run over the climate bins.

Liquid path

liquid = IT × captureṁ_TCS = liquid / (cp · ΔT_TCS), P_pump = ρ · g · H · V̇ / η (pump work returns as heat)CDUs per hall = ⌈hall liquid duty / CDU unit⌉ + N_spare; FWS supply = TCS supply − CDU approachcooler leaving = max(FWS supply, sink + min approach); sink = dry bulb · pre-cooled air (adiabatic) · wet bulb (fluid cooler, tower)trim share = (cooler leaving − FWS supply) / ΔT_FWS — the trim chiller cools the restCooler count: duty ÷ (rated unit × LMTD_actual / LMTD_rating), taken at the condition that loads the coolers most across the design day and the bins.

Air path — the heat liquid cooling does not capture

air load = IT × (1 − capture) + CDU skin loss + cord and PDU lossesfan heat closes on itself: Q_CRAH = Q₀ / (1 − SFP / (ρ·cp·ΔT_air))CRAHs per hall = ⌈hall air load / CRAH unit⌉ + N_spare; CHW flow = load / (cp · ΔT_CHW)chiller load = CRAHs + electrical rooms + CHW pump heat; COP = rated × part-load factor(PLR) × lift ratioPart-load factor from published VSD points (100 % 1.000, 80 % 1.140, 50 % 1.441), flat below 30 % PLR. Lift ratio = (T_cond,rated − T_evap)/(T_cond − T_evap).

Electrical chain and metering points (ISO/IEC 30134-2)

M3 = IT input ← cords ← M2 = PDU output ← PDU ← M1 = UPS output (+ CDU pumps on UPS)UPS in = M1 / η_UPS; LV distribution, transformers upstream; M0 = facility inputCord and PDU losses land in the hall air (the CRAHs carry them); UPS, LV and transformer losses in the electrical rooms, cooled on chilled water.

Annual figures

PUE_annual = Σ facility·h / Σ IT·h over the climate bins at mean utilisationWUE = make-up water / IT energy; make-up = evaporation × C/(C−1), evaporation = latent heat / h_fgCUE = (M0 − renewable) × grid factor / M3 (market-based simplification)Never a fixed fraction of the design-day PUE: the bins carry the ambient that sets trim hours, chiller lift and fan energy.

04 Constants & data sources

STANDARD: water cp 4.186 kJ/kg·K, ρ 997 kg/m³; air cp 1.006 kJ/kg·K, ρ 1.18 kg/m³; h_fg 2,430 kJ/kg; 1 RT = 3.517 kW. ASSUMED (each editable under Advanced): CDU 2,000 kW, CRAH 250 kW, chiller 4,000 kW_th at rated COP 6.5, SFP 1.2 kW per m³/s, TCS head 25 m at η 0.70, FWS head 30 m at η 0.75, UPS 97 %, transformer 99 %, cord 0.5 %, PDU 1.5 %, LV 0.5 %, tower cycles 4, cooler minimum approaches dry 4 K / adiabatic 1.5 K / fluid 2 K / tower 3 K. The climate bins are illustrative; replace them with bins built from the site’s EPW file.

05 Outputs

OutputDerivationNote
PUE (annual / design)Σ facility·h / Σ IT·h; design-day facility / ITThe lab’s headline PUE is annual; the design day sizes the plant
PUE categories 1/2/3M0 / M1, M0 / M2, M0 / M3Same facility, three numbers: state the category
Flow, pump power, CDUsTCS loopPump power = TCS + FWS pumps
System COPIT / all cooling powerPumps, fans, chillers, trim, towers
WUE, water, CUE, CO₂Over the binsSite layer sets grid factor and renewable share
Energy, water cost, net OPEXM0 × tariff, water × tariff − reuse creditTariffs from the site layer
Scores, risk, confidenceLab screening modelScreening, not a compliance finding

06 Worked example

Defaults: 100 MW IT in 5 halls, capture 85 %, TCS 35/45 °C, dry coolers + water-cooled chillers, tropical bins (design 35 °C dry bulb / 28 °C wet bulb), utilisation 85 %. Every number is what the engine returns; tools/test-ltc-plant.mjs recomputes the first ones by hand.

  1. Liquid heat: 100,000 × 0.85 = 85,000 kW; TCS ΔT 10 K → 85,000 / (4.186 × 10) = 2,030.6 kg/s = 2,036.7 L/s
  2. TCS pumps: 997 × 9.81 × 25 × 2.0367 / 1000 / 0.70 = 711 kW; CDU duty 85,711 kW → 10 CDUs per hall (9 + 1)
  3. Facility water 32/42 °C at 2,033 L/s. At 35 °C the dry coolers leave 39 °C: the trim chiller carries 70 % on the design day and runs 3,160 h a year; 65 coolers including the spare, sized for the cooler hours
  4. Air path: 15,000 kW IT + 857 kW CDU skin + 500 kW cords + 1,530 kW PDUs, fan heat closed at 8.42 % → 3,907 kW per hall, 17 CRAHs (16 + 1)
  5. Chillers: CRAHs + 5,005 kW electrical rooms + CHW pumps = 25,327 kW; 8 machines at 79 % load, COP 6.81
  6. Losses: UPS 3,178 kW, LV 530 kW, transformers 1,298 kW; mechanical (MCC) 22,004 kW; facility 129,750 kW
  7. PUE 1.298 design-day, 1.189 annual; categories 1/2/3 = 1.157 / 1.183 / 1.189 (M0 885,295 · M1 765,016 · M2 748,323 · M3 744,600 MWh)
  8. WUE 0.67 L/kWh (499,745 m³/yr, the trim chiller’s condenser towers); CUE 0.856 kgCO₂/kWh at 0.72 kg/kWh; energy balance closes to 1.2 × 10⁻¹⁴
SIMULATED result: educational estimates from stated equations and stated assumptions, not site-validated measurements. A real study uses vendor selections and an 8,760-hour simulation on the site’s weather file.

A Legacy screening model (comparison only)

Shown only when Legacy screening model is ticked under Run Model. This was the lab’s engine until v3.17.0: one deterministic pass with heuristic multipliers (density stress, control index, future factor) that no component can be traced to, and no separate air, chilled-water or electrical-room path. Kept for comparison; its equations follow, as they are in computeModelLegacy.

Steady-state energy balance (conceptual)

Q_in = IT_kW (heat dissipated by servers) Q_cooling = liquidCoolingKw + airCoolingKw + fanKw Q_loss = upsLossKw + distLossKw + auxKw (3% IT) totalFacilityKw = IT_kW + Q_cooling + Q_loss (power draw) The solver does not iterate; it computes Q_cooling from the input parameters directly. Steady-state means the system is assumed to be in thermal equilibrium at the stated inputs.SIMULATED · inline computeModel

Supply temperature rise & mass flow

baseDeltaT = returnTemp − supplyTemp deltaT = clamp( baseDeltaT × (0.9 + densityStress × 0.08), 3, 20 ) [°C] liquidKw = itKw × (effectiveCapture / 100) massFlow_kg/s = liquidKw / ( Cp × deltaT ) baseFlow_m³/s = massFlow_kg/s / ρ designFlow_m³/s = baseFlow × redundancyFactor × (1 + hydraulicMargin%) × pipeFactor flowLPM = designFlow_m³/s × 60 000 Cp and ρ from coolant table (water: 4.186 kJ/kg·K, 997 kg/m³). redundancyFactor = 2 for 2N, 1.15 for N+1, 1 for N. densityStress = clamp(designDensity / 70, 0.5, 2.8).ASHRAE Liquid Cooling Guide · inline computeModel

Hydraulic pump power (affinity-law corrected)

pumpHeadEff = pumpHead × pipeFactor × (1 + (densityStress − 1) × 0.22) [m] P_hyd = ρ × g × pumpHeadEff × designFlow_m³/s / 1000 [kW] pumpPowerKw = P_hyd / pumpEff_fraction g = 9.81 m/s². pumpEff_fraction clamped to [0.35, 1]. Fan power (fan affinity law scaling): fanKw = itKw × (fanPower%) × (1 − effectiveCapture/100 × 0.55) × (1 − controlBonus × 0.18) — residual fan demand after liquid-capture and control reductions.HX Institute · pump affinity laws · inline computeModel

HX effectiveness & liquid cooling COP

supplyBonus = clamp( (supplyTemp − 28) × 0.11, −0.45, 1.5 ) economizerFraction = economizerHours / 100 liquidCOP = clamp( (6.1 + climateBias + supplyBonus + economizerFraction × 1.05 + controlBonus) × futureFactor, 3.0, 19 ) airCopEff = clamp( airCOP × (1 + economizerFraction × 0.58 + controlBonus × 0.32) × factor, 1.7, 16 ) liquidCoolingKw = (liquidKw + cduLossKw) / liquidCOP + pumpPowerKw airCoolingKw = airKw / airCopEff Higher liquid supply temperature → higher liquidCOP (warm-water rejection to cooling tower or dry cooler). Economizer availability boosts both liquid and air path effectiveness. HX effectiveness is captured through the liquidCOP / supplyBonus relationship: warmer supply allows higher approach temperature to the rejection side.HX Institute · ASHRAE · inline computeModel

PUE impact (facility + CDU pump)

upsInputKw = itKw / upsEff_fraction upsLossKw = upsInputKw − itKw distLossKw = upsInputKw × (distLoss% / 100) auxKw = itKw × 0.03 totalCoolingKw = liquidCoolingKw + airCoolingKw + fanKw totalFacilityKw = itKw + totalCoolingKw + upsLossKw + distLossKw + auxKw PUE = totalFacilityKw / itKw CDU pump power (pumpPowerKw) is already embedded in liquidCoolingKw. PUE includes UPS and distribution losses, fan load, liquid cooling overhead, and a 3% IT auxiliary allowance.ISO 30134-2 / Green Grid · inline computeModel

System COP

systemCOP = itKw / totalCoolingKw Cooling-side COP only (IT load divided by total cooling power including pump and fans).ASHRAE 90.4 · inline computeModel

WUE and annual energy

WUE = baseWUE × (1 − economizerFraction × 0.43) × (1 − effectiveCapture/100 × 0.32) × (1 − (futureFactor−1) × 0.18) annualKWh = totalFacilityKw × 8 760 annualGWh = annualKWh / 1 000 000 baseWUE is climate-specific. Economizer use and high liquid-capture reduce water consumption. WUE clamped to ≥ 0.04 L/kWh.ISO/IEC 30134-9 / Green Grid · inline computeModel

07 References & standards

08 Assumptions & limitations

Steady state at each operating point; annual figures are hour-weighted over climate bins at a mean utilisation, which captures ambient-driven effects (trim hours, chiller lift, fan energy) but not load dynamics. Fault responses on the workbench (DH01 map, Tier sweep) use a stated first-order thermal-mass model checked against its analytic solution, and the DH01 map is a thermal approximation, not CFD. Unit sizes and efficiencies are typical design values until a vendor selection replaces them; climate bins are illustrative until replaced with the site’s EPW bins.

This manual and the lab are engineering education and pre-design aids. Outputs are labelled SIMULATED; scores are screening, not compliance findings.

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