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Plate & Frame Heat Exchanger (PHE) Sizer

Rate and size gasketed plate & frame heat exchangers (GPHE). Calculate chevron corrugation convective coefficients, channel hydraulics, LMTD, A-dimension, and port pressure drop.


⚡ Industrial Presets:

1. Hot Side Process Stream (Channel 1)

2. Cold Side Process Stream (Channel 2)

3. Plate Geometry & Chevron Corrugation

4. Plate Pack, Frame & Gasket Rating

Plate & Frame Heat Exchanger Rating Results

API Standard 662 / ISO 15547 / Kumar Corrugated Channel Rating
SUCCESS
DYNAMIC PLATE & FRAME CAD STUDIO API 662 / Gasketed Plate Pack Elevation & Compression Profile
Plates: 50 Chevron: 45° A-Dim: 165 mm
TOP CARRYING BAR (SUSPENSION) BOTTOM GUIDE BAR FIXED COVER (HEAD) END COLUMN S1 (Hot In) S4 (Cold Out) S2 (Hot Out) S3 (Cold In) PRESSURE PLATE A = 165.0 mm STREAM FLOW Hot Side In: 75.0°C Out: 40.0°C ΔP: 0.59 bar Cold Side In: 25.0°C Out: 55.0°C ΔP: 0.62 bar
Surface Overdesign Margin
+15.4%
0% (Pinch) Target: +10% to +25% +50% (Excess)
Port Velocity & Maldistribution
2.46 m/s
0 m/s Optimal: ≤ 4.5 m/s 6.0 m/s (Erosion)
Wall Shear Stress (Self-Cleaning)
58.4 Pa
0 Pa Target: ≥ 30-50 Pa 120 Pa
Heat Duty (Q)
-- kW
Req Area: -- m²
Dirty Overall U
-- W/m²·K
Clean U: -- W/m²·K
Pressure Drops (ΔP)
-- / -- bar
Hot / Cold Total Drops
Tightening A-Dim
-- mm
Plates: -- (-- active)

1. Thermal Rating & Duty Balance

Total Transferred Duty (Q)-- kW (-- MW)
Log Mean Temp Diff (LMTD)-- °C
Counter-Current Correction (Ft)--
Effective MTD (ΔTm)-- °C
Clean Overall Coeff (Uclean)-- W/m²·K
Dirty Overall Coeff (Udirty)-- W/m²·K
Surface Area Required-- m²
Surface Area Installed-- m²
Thermal Length (Θ = NTU)-- (NTU_h: --)
Minimum Approach Temp (ΔT)-- °C

2. Plate Geometry & Channel Dimensions

Total Plates / Active Thermal Plates-- / --
Total Flow Channels (Hot / Cold)-- (-- / --)
Channels Per Pass (Hot / Cold)-- / --
Single Plate Effective Area (A1)-- m²
Enlargement Factor (φ)--
Mean Channel Gap (b)-- mm
Corrugation Pitch (λ)-- mm
Channel Hydraulic Diameter (Dh)-- mm
Plate Vertical / Width Dimensions-- m × -- m
Port Nozzle Inside Diameter-- mm

3. Stream Hydraulics & Pressure Drops

Hydraulic MetricHot SideCold Side
Channel Flow Velocity (v_ch)-- m/s-- m/s
Channel Reynolds Number (Re)----
Channel Prandtl Number (Pr)----
Channel Nusselt Number (Nu)----
Convective Coeff (h_conv)-- W/m²·K-- W/m²·K
Friction Factor (f_ch)----
Port Nozzle Velocity (v_port)-- m/s-- m/s
Channel Pressure Drop (ΔP_ch)-- bar-- bar
Port Nozzle Drop (ΔP_port)-- bar-- bar
Total Stream ΔP-- bar-- bar
Wall Shear Stress (τ_w)-- Pa-- Pa

4. Frame Compression & Mechanical Limits

A-Dimension (Nominal Tightening)-- mm
A-Dimension Tightening Range-- mm to -- mm
Estimated Frame Total Length-- mm
Plate Metallurgy Specified--
Gasket Elastomer Selected--
Gasket Maximum Temp Limit-- °C
Design Pressure Rating-- barg
Hydrostatic Test Pressure (1.43x)-- barg
Min Plates Required for Duty-- plates

AI Engineering Diagnostics & API 662 Safety Verifications


📐 Engineering Formula & Specification Sheet

Plate & Frame Heat Exchanger (PHE) Sizer: Sizing Methodology & Engineering Basis

Rate and size gasketed plate & frame heat exchangers (GPHE). Calculate chevron corrugation convective coefficients, channel hydraulics, LMTD, A-dimension, and

📐 Reviewed by: ChemProCal Engineering Editorial Team
🗓️ Standards: ASME / API / GPSA / ISA
⏱️ Format: Quick Reference Spec Sheet

1. Calculation Scope & Governing Equations

This rating sheet provides sizing and thermal-hydraulic verification for gasketed plate and frame heat exchangers (GPHE) in accordance with API Standard 662 Part 1 / ISO 15547-1 and ASME Section VIII Division 1.

$$Q = \dot{m}_h C_{p,h} (T_{h,in} - T_{h,out}) = \dot{m}_c C_{p,c} (T_{c,out} - T_{c,in})$$
$$\text{LMTD} = \frac{\Delta T_1 - \Delta T_2}{\ln(\Delta T_1 / \Delta T_2)}, \quad \Delta T_1 = T_{h,in} - T_{c,out}, \quad \Delta T_2 = T_{h,out} - T_{c,in}$$
$$A_{\text{req}} = \frac{Q}{U_{dirty} \cdot F_t \cdot \text{LMTD}}, \quad A_{\text{installed}} = (N_{plates} - 2) \cdot A_1$$
$$\frac{1}{U_{dirty}} = \frac{1}{h_{hot}} + R_{f,hot} + \frac{t_{plate}}{k_{plate}} + R_{f,cold} + \frac{1}{h_{cold}}$$
$$Nu = C_h \cdot Re^m \cdot Pr^{1/3} \cdot \left(\frac{\mu}{\mu_w}\right)^{0.14}, \quad h = \frac{Nu \cdot k_{fluid}}{D_h}, \quad D_h = \frac{2 b}{\phi}$$
$$\Delta P_{total} = 4 f \left(\frac{L_v}{D_h}\right)\left(\frac{\rho v_{ch}^2}{2}\right) N_{pass} + 1.3 \left(\frac{\rho v_{port}^2}{2}\right) N_{pass}$$
$$A_{nominal} = N_{plates} \times (t_{plate} + b)$$

2. Standard Parameters & API 662 Design Criteria

Service / Fluid Type Typical Overall U ($W/m^2\cdot K$) Recommended Design Limits
Water to Water (District Cooling) $3,000 - 6,500\text{ W/m}^2\cdot\text{K}$ $v_{ch} = 0.3 - 0.8\text{ m/s}$; $v_{port} \le 4.5\text{ m/s}$; allowable $\Delta P \le 0.70\text{ bar}$.
Wort / Milk Pasteurizer (Food CIP) $2,500 - 4,500\text{ W/m}^2\cdot\text{K}$ $v_{ch} = 0.2 - 0.6\text{ m/s}$ (prevents shearing); allowable $\Delta P \le 0.80\text{ bar}$.
WFI Subcooler (Pharmaceutical) $2,800 - 5,000\text{ W/m}^2\cdot\text{K}$ $v_{ch} = 0.3 - 0.7\text{ m/s}$; PTFE/EPDM gaskets; allowable $\Delta P \le 0.50\text{ bar}$.
Viscous Oil Cooling (ISO VG 46) $400 - 1,200\text{ W/m}^2\cdot\text{K}$ $v_{ch} = 0.1 - 0.4\text{ m/s}$; $30^\circ$ Low-theta plate; allowable $\Delta P \le 1.20\text{ bar}$.
LMTD Correction Factor ($F_t$) $\ge 0.95$ (Pure counterflow) Allows close temperature approach down to $1.0^\circ\text{C}$ without temperature cross.

3. Engineering Assumptions & Boundary Limits

  • Fouling Resistances: Default calculations utilize modern PHE empirical fouling factors ($0.00003 - 0.00006\text{ m}^2\cdot\text{K/W}$), capitalizing on high shear stress scouring action.
  • Port Velocity & Maldistribution: Port nozzle velocities are capped at $\le 4.5\text{ m/s}$ to eliminate flow maldistribution and nozzle erosion.
  • Frame Tightening (A-Dimension): Sizing outputs enforce minimum and maximum tightening tolerances ($A_{min}$ to $A_{max}$) to prevent gasket crushing or fluid leakage.
  • Self-Cleaning Scour: Channel wall shear stress ($\tau_w$) should exceed $\ge 30\text{ Pa}$ to inhibit particulate sedimentation and biological fouling.

📚 ChemProCal Knowledge Base

Need Complete Mathematical Derivations & Industrial Case Studies? Explore our in-depth engineering textbook guide: Plate & Frame Heat Exchanger Sizing: API 662 & Chevron Plate Design Guide.

Read Full Theory Guide →
Peer Review & Engineering Accuracy

This specification sheet and its mathematical formulations adhere to internationally recognized process codes (API Standard 662 Part 1, ISO 15547-1, and ASME Section VIII Division 1). Sizing parameters and default design allowances are cross-referenced with empirical industry design practices.

📚 ChemProCal Knowledge Base

Need Complete Mathematical Derivations & Industrial Case Studies?

Explore our in-depth engineering textbook guide: Plate & Frame Heat Exchanger Sizing: API 662 & Chevron Plate Design Guide. Features step-by-step manual hand calculations, thermodynamic proofs, and commercial simulator benchmarks.

Read Full Theory Guide →
Peer Review & Engineering Accuracy

This specification sheet and its mathematical formulations adhere to internationally recognized process codes (ASME, API, GPSA, TEMA, and ISA). Sizing parameters and default design allowances are cross-referenced with empirical industry design practices.

About This Tool

Thermodynamics & Plate Heat Exchanger Rating: Principles, Chevron Dynamics & Hydrodynamic Sizing

Principles of Gasketed Plate Heat Exchangers (GPHE)

Plate and frame heat exchangers are specialized thermal processing units designed to transfer energy across a series of thin, pressed metal plates clamped together in a steel frame. Unlike tubular exchangers where fluids flow inside and outside tubes, plate exchangers direct fluids through thin, highly turbulent corrugated channels bounded by elastomer gaskets.

Because the flow channels are exceptionally narrow (typically 2 to 4 mm gap) and feature alternating chevron herringbone patterns, the fluids undergo continuous three-dimensional mixing and boundary layer disruption. This enables heat transfer coefficients (U-values) reaching 3,000 to 6,500 W/m²·K—roughly three to five times higher than shell-and-tube exchangers for identical fluid duties.

The Fundamental Heat Transfer Equation & Corrugated Thermal Resistance Network

The total heat duty (Q) transferred across the plate pack surface is governed by the rate equation:

$$Q = U_{dirty} \cdot A_{eff} \cdot \Delta T_m$$

The dirty overall heat transfer coefficient ($U_{dirty}$) is resolved through the reciprocal sum of convective, conductive, and fouling resistances:

$$\frac{1}{U_{dirty}} = \frac{1}{h_{hot}} + R_{f,hot} + \frac{t_{plate}}{k_{plate}} + R_{f,cold} + \frac{1}{h_{cold}}$$

Because the plates are stamped from thin sheet metal (typically 0.5 to 0.6 mm) with high thermal conductivity (e.g. Stainless Steel 316L, Titanium, or Hastelloy), the wall conductive resistance ($t_p / k_w$) is exceptionally small. Furthermore, because plate exchangers operate with almost pure counter-current flow (F-factor $\approx 0.98 - 1.00$), they achieve extremely close approach temperatures down to $1.0^\circ\text{C}$ without temperature cross penalties.

Chevron Angle Dynamics & Kumar Convective Correlations

The corrugation chevron angle ($\theta$) is the dominant geometric parameter determining the tradeoff between convective heat transfer and hydraulic pressure drop:

  • Low-Theta (30° - Soft Plate): Features shallow chevron angles, producing lower friction factors ($f$) and moderate heat transfer coefficients. Best suited for high-viscosity fluids or tight pressure drop budgets ($\le 0.4\text{ bar}$).
  • Mixed Pack (45° - Medium Theta): Assembled by alternating 30° and 60° plates in the same pack, providing a versatile balance of high thermal performance and manageable pressure drop.
  • High-Theta (60° - Hard Plate): Forces aggressive secondary vortices, maximizing the Nusselt number ($Nu$) at the expense of higher friction. Ideal for high NTU duties and close temperature approaches.

The convective film coefficients ($h$) are calculated via the benchmark Kumar (1984) correlation:

$$Nu = C_h \cdot Re^m \cdot Pr^{1/3} \cdot \left(\frac{\mu}{\mu_w}\right)^{0.14}$$

$$h = \frac{Nu \cdot k_{fluid}}{D_h}, \quad \text{where } D_h = \frac{2b}{\phi}$$

Channel Hydraulic Friction, Port Losses & Wall Shear Stress

Hydraulic sizing evaluates both channel friction drop and port manifold losses:

$$\Delta P_{ch} = 4 f \cdot \left(\frac{L_v}{D_h}\right) \cdot \left(\frac{\rho v_{ch}^2}{2}\right) \cdot N_{pass}$$

$$\Delta P_{port} \approx 1.3 \cdot \left(\frac{\rho v_{port}^2}{2}\right) \cdot N_{pass}$$

$$\Delta P_{total} = \Delta P_{ch} + \Delta P_{port}$$

Wall Shear Stress ($\tau_w$): High shear stress ($\tau_w \ge 30 - 50\text{ Pa}$) provides continuous scouring action that sweeps particulate deposits and biological film out of the corrugations, allowing GPHE units to operate with fouling factors an order of magnitude lower than shell-and-tube exchangers.

Step-by-Step Worked Example: District Cooling Interchanger Rating

Scenario: Rate a building chilled water interchanger cooling $120,000\text{ kg/h}$ of building return water from $13.0^\circ\text{C}$ to $6.0^\circ\text{C}$ using primary district chilled water entering at $4.5^\circ\text{C}$ and leaving at $11.5^\circ\text{C}$.

  1. Heat Duty ($Q$):
    $$Q = \dot{m} \cdot Cp \cdot \Delta T = \frac{120,000}{3600} \times 4.19 \times (13.0 - 6.0) = 977.7\text{ kW}$$
  2. LMTD & Approach:
    $$\Delta T_1 = 13.0 - 11.5 = 1.5^\circ\text{C}, \quad \Delta T_2 = 6.0 - 4.5 = 1.5^\circ\text{C}$$
    $$\text{LMTD} = 1.50^\circ\text{C}, \quad \Delta T_m = 0.99 \times 1.50 = 1.485^\circ\text{C}$$
  3. Plate Selection:
    Selecting $N_p = 120$ plates (118 active), Titanium Gr. 1 ($0.5\text{ mm}$), $60^\circ$ chevron angle, giving $A_{installed} = 106.9\text{ m}^2$.
    Channel velocity $v_{ch} = 0.45\text{ m/s}$, $Re = 1,420$.
  4. Convective Coefficients & U-Value:
    $$h_{hot} = 6,850\text{ W/m}^2\cdot\text{K}, \quad h_{cold} = 6,450\text{ W/m}^2\cdot\text{K}$$
    $$U_{dirty} \approx 2,520\text{ W/m}^2\cdot\text{K}$$
  5. Required Area & Overdesign:
    $$A_{required} = \frac{977,700}{2,520 \times 1.485} = 92.8\text{ m}^2$$
    $$\text{Overdesign Margin} = \frac{106.9 - 92.8}{92.8} \times 100\% = +15.2\%$$ (Within optimal API 662 target).

Frequently Asked Questions

What is the difference between Low-Theta (30°) and High-Theta (60°) chevron plates?

The chevron angle (θ) governs the flow path resistance and turbulence inside the channel. Low-theta (30°) plates have shallow chevron corrugations that produce lower friction factors (low pressure drop) and moderate heat transfer coefficients, making them ideal for viscous oils or high flow rates with tight pressure limits. High-theta (60°) plates force the fluid into sharp zigzag secondary vortices, producing exceptionally high heat transfer coefficients and high pressure drops, which are ideal for duties with close approach temperatures and high thermal lengths (NTU).

How close can the temperature approach be in a Plate & Frame Heat Exchanger?

Because gasketed plate heat exchangers operate with nearly pure counter-current flow (Ft ≥ 0.98), they can routinely achieve extremely close temperature approach differences as tight as 1.0°C to 1.5°C (1.8°F to 2.7°F). In contrast, shell-and-tube heat exchangers generally require at least a 5°C to 10°C approach to prevent severe thermodynamic pinch and impractical shell-in-series multiplication.

What is the A-dimension and why is it critical during maintenance?

The A-dimension is the compressed thickness of the plate pack measured between the inner faces of the fixed head and the movable pressure plate. During assembly or after maintenance cleaning, tightening tie-bolts must clamp the plate pack within strict tolerances (between Amin and Amax). Overtightening below Amin crushes the plate corrugation contact points and permanently deforms the stainless steel plates, while undertightening above Amax results in external gasket leakage upon pressurization.

How do I select the right gasket elastomer (NBR, EPDM, FKM, PTFE)?

Gasket selection depends on operating temperature and chemical exposure. NBR (Nitrile) is standard for water, glycols, and lubricating oils up to 130°C. EPDM is ideal for low-pressure steam, hot water, caustics (CIP cleaning), and dilute acids up to 160°C. FKM (Viton) handles aggressive hydrocarbons, solvents, and concentrated acids up to 180°C. PTFE-encapsulated gaskets provide universal chemical resistance up to 200°C for ultra-pure pharmaceutical WFI and aggressive chemicals.

Why does a PHE achieve significantly higher heat transfer coefficients than a shell & tube exchanger?

The narrow corrugated plate channels (2 to 4 mm gap) generate intense boundary layer disruption and continuous 3D swirl, causing the fluid to transition to turbulent flow at Reynolds numbers as low as 10 to 400. In addition, the thin plate wall (0.5 mm) offers negligible conductive resistance compared to thick tubular walls. As a result, overall heat transfer coefficients (U-values) for water-to-water duties reach 3,000 to 6,500 W/m²·K in a PHE, compared to 800 to 1,500 W/m²·K in a shell-and-tube exchanger.

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