HVAC Systems Encyclopedia

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Commercial Kitchen Ventilation & Exhaust Hood Design

Commercial Kitchen Ventilation & Exhaust Hood Design

Commercial kitchen ventilation systems capture heat, smoke, steam, grease, and odors from cooking equipment while providing makeup air to replace exhaust. This guide covers hood types, exhaust rate calculations, makeup air strategies, grease control, and demand-controlled ventilation per ASHRAE, NFPA 96, and IMC requirements.

Hood Classification and Requirements

Type I (Grease) Hoods

Definition: Hoods for cooking equipment producing grease-laden vapors

Appliances requiring Type I hoods:

  • Charbroilers and grills
  • Fryers (open deep-fat fryers)
  • Ranges (gas or electric with open flame or high heat)
  • Ovens used for high-temperature cooking (> 400°F)
  • Woks and stir-fry equipment
  • Griddles (solid top cooking surfaces > 400°F)

Construction requirements (UL 710, NFPA 96):

  • Material: 16-20 gauge stainless steel or 18 gauge carbon steel
  • Grease filters: Baffle or mesh type, UL 1046 listed
  • Slope: Bottom and sides slope toward grease collection (2% minimum)
  • Grease gutters: Continuous perimeter gutter, drain to external receptacle
  • Access panels: For cleaning ductwork, fans

Fire suppression: Required per NFPA 96

  • Wet chemical or dry chemical system
  • Automatic activation (fusible links at 350-500°F)
  • Manual pull stations
  • Fuel shutoff interlocked with suppression system

Type II (Heat and Steam) Hoods

Definition: Hoods for equipment producing heat and moisture but minimal grease

Appliances requiring Type II hoods:

  • Steam kettles and steamers
  • Dishwashers
  • Low-temperature ovens (< 400°F)
  • Pasta cookers and rethermalizers

Construction:

  • Lighter gauge material acceptable (20-22 gauge)
  • No grease filters required (optional condensate filters)
  • Fire suppression not required

Exhaust Airflow Rates

Exhaust CFM per linear foot of hood:

Appliance DutyHood TypeLight DutyMedium DutyHeavy DutyExtra-Heavy Duty
Wall canopyType I200 CFM/ft300 CFM/ft400 CFM/ft550 CFM/ft
Single islandType I300 CFM/ft400 CFM/ft500 CFM/ft600 CFM/ft
Double islandType I250 CFM/ft350 CFM/ft450 CFM/ft550 CFM/ft
Backshelf/Pass-overType I150 CFM/ft250 CFM/ft300 CFM/ft400 CFM/ft
EyebrowType I250 CFM/ft350 CFM/ft450 CFM/ft

Appliance duty classification:

  • Light duty: Electric ovens, steam kettles, small ranges
  • Medium duty: Gas ranges, fryers, griddles (standard output)
  • Heavy duty: Charbroilers, wok ranges, high-Btu equipment
  • Extra-heavy duty: Solid-fuel (charcoal, wood), mesquite grills

Hood area method (alternative):

$$CFM = A_{hood} \times V_{capture}$$

Where:

  • $A_{hood}$ = hood face opening area (ft²)
  • $V_{capture}$ = capture velocity (100-150 fpm typical)

Factors Affecting Exhaust Rate

Hood geometry:

  • Wall-mounted canopy: One side open (lowest exhaust rate)
  • Single island: All four sides open (highest exhaust rate)
  • Proximity hood (backshelf): Close to appliance (reduced rate)

Appliance heat output:

  • Higher Btu/hr → more thermal plume → higher exhaust required

Hood overhang:

  • Minimum 6" overhang beyond appliance footprint (all sides)
  • Larger overhang improves capture, may reduce exhaust rate

Worked Example 1: Type I Hood Exhaust Calculation

Given:

  • Wall-mounted canopy hood
  • Hood length: 12 ft
  • Appliances: Two charbroilers (heavy-duty), three gas ranges (medium-duty)
  • Cooking line overhang: 9" beyond appliances

Find: Required exhaust airflow

Solution:

Method 1: ASHRAE table (per linear foot)

Heavy-duty wall canopy: 400 CFM/ft

$$CFM_{exhaust} = 12 \times 400 = 4,800 \text{ CFM}$$

Method 2: Weighted by appliance duty

Charbroilers occupy 6 ft (heavy-duty): $6 \times 400 = 2,400$ CFM

Ranges occupy 6 ft (medium-duty): $6 \times 300 = 1,800$ CFM

$$CFM_{total} = 2,400 + 1,800 = 4,200 \text{ CFM}$$

Method 3: Hood face area

Hood depth: 4 ft (typical wall canopy) Hood height above appliances: 3 ft Face opening: $12 \times 3 = 36$ ft² (conservative, uses full height) Capture velocity: 100 fpm

$$CFM = 36 \times 100 = 3,600 \text{ CFM}$$

Design selection: Use Method 1 (most conservative): 4,800 CFM

Add 10% safety factor: $4,800 \times 1.10 = 5,280$ CFM

Answer: 5,280 CFM exhaust (select 5,500 CFM fan)

Makeup Air Systems

Makeup Air Requirements

Purpose: Replace exhaust air to prevent building negative pressure

Makeup air quantity:

$$CFM_{makeup} = CFM_{exhaust} - CFM_{transfer}$$

Where $CFM_{transfer}$ = air from adjacent spaces (dining room, etc.)

Typical design: 80-100% makeup air (20% maximum transfer air from dining/non-kitchen spaces)

Code requirements (IMC Section 508):

  • Makeup air required when exhaust > 400 CFM
  • Makeup air shall be within 10% of exhaust rate

Makeup Air Delivery Methods

1. Direct supply to hood (short-circuit):

  • Air curtain at hood front
  • Supply air velocities: 300-500 fpm
  • Temperature: 10-15°F below room temperature (avoid thermal shock to cooks)

Advantages:

  • Reduces conditioned makeup air energy (less tempering required)
  • Prevents draft on cooking line

Disadvantages:

  • Can interfere with capture if velocity too high
  • Requires careful design (ASHRAE 154P testing)

2. General dilution (away from hood):

  • Supply air diffusers around perimeter of kitchen
  • Low velocity (< 500 fpm at outlets)
  • Provides general ventilation and pressurization

3. Combination:

  • 50-70% direct to hood (short-circuit)
  • 30-50% general dilution

Makeup Air Temperature

Heating requirement:

$$Q_{heating} = 1.08 \times CFM_{makeup} \times (T_{supply} - T_{outdoor})$$

Winter design example:

  • Outdoor air: 0°F
  • Supply air target: 60°F (10°F below kitchen ambient)
  • Makeup air: 5,000 CFM

$$Q = 1.08 \times 5,000 \times (60 - 0) = 324,000 \text{ Btu/hr} = 27 \text{ tons heating}$$

Heating methods:

  • Gas-fired makeup air unit (direct-fired or indirect)
  • Electric resistance (expensive to operate)
  • Heat recovery from exhaust (grease accumulation concern)
  • Radiant heaters at cooking line (supplemental comfort heating)

Summer cooling:

  • Typically no mechanical cooling of makeup air (expensive)
  • Evaporative cooling in dry climates (Arizona, New Mexico)
  • Relies on short-circuit strategy (reduce sensible load)

Grease Control and Fire Safety

Grease Extraction

Grease-laden vapor capture efficiency:

Filter TypeGrease Removal EfficiencyApplication
Baffle filters (UL 1046)70-90%Standard (most Type I hoods)
Mesh filters50-70%Light-duty applications
Water-wash systems90-98%High-volume (casinos, stadiums)
Electrostatic precipitators (ESP)85-95%Retrofit, odor control

Baffle filter design:

  • Staggered baffles create centrifugal force (grease droplets separated)
  • Removable for cleaning (commercial dishwasher weekly minimum)

Ductwork Design

NFPA 96 requirements:

Material:

  • 16 gauge carbon steel (continuous welded seams)
  • 18 gauge stainless steel (Type 304)

Slope:

  • Minimum 1/4" per foot horizontal run
  • Drain toward hood (grease flows back to collection)

Access panels:

  • Maximum 12 ft spacing horizontally
  • Every floor penetration
  • Changes in direction

Clearances to combustibles:

  • 18" minimum (unprotected duct)
  • 6" with listed clearance reduction system
  • Zero clearance with factory-built grease duct enclosure

No dampers permitted in grease exhaust ductwork (fire/grease accumulation hazard)

Exhaust Fan Selection

Upblast centrifugal roof exhaust fan:

  • Grease-rated (UL 762 listing)
  • Belt-drive (allows speed adjustment, easier motor replacement)
  • Drain connection at fan base (grease collection)
  • Hinged roof curb (fan removal for cleaning)

Fan materials:

  • Aluminum or coated steel wheel (grease-resistant)
  • Stainless steel preferred for high-volume or acidic exhaust

Typical fan static pressure: 1.0-2.0" w.g. (ductwork + grease filters)

Demand-Controlled Kitchen Ventilation (DCKV)

Operating Principle

Variable exhaust based on cooking activity:

  • Optical sensors (detect smoke/steam plume)
  • Temperature sensors (measure hood plenum temperature)
  • Modulate exhaust fan speed (VFD)
  • Modulate makeup air in proportion

Turndown ratio: 30-100% of design airflow typical

Energy savings:

  • Reduced fan energy: 40-60% (fan power ∝ flow³)
  • Reduced heating/cooling of makeup air: 30-50%
  • Total kitchen HVAC energy savings: 30-40%

Control Strategy

graph TD
    A[Cooking Activity Sensors] --> B{Detect Heat/Smoke?}
    B -->|High Activity| C[100% Exhaust + Makeup]
    B -->|Medium Activity| D[70% Exhaust + Makeup]
    B -->|Low/Idle| E[30-50% Exhaust + Makeup]
    
    F[Manual Override] --> C
    G[Fire Suppression Activation] --> H[Shutdown Fans<br/>Close Makeup Dampers]

Minimum airflow (idle mode):

  • 30-50% of design exhaust
  • Maintains hood capture, prevents grease accumulation
  • Complies with makeup air requirements

Code acceptance:

  • IMC 2021: Allows DCKV with listed controls and sensors
  • Local AHJ approval may be required
  • ASHRAE 154P: Standard method of test for DCKV systems

Worked Example 2: DCKV Energy Savings

Given:

  • Exhaust hood: 6,000 CFM design
  • DCKV idle flow: 40% (2,400 CFM)
  • Operating hours: 16 hr/day (8 hr cooking, 8 hr idle/prep)
  • Winter outdoor temp: 20°F average
  • Makeup air supply: 65°F
  • Fan motor: 7.5 hp at full flow
  • Energy cost: $0.12/kWh, $0.80/therm (natural gas)
  • Heating efficiency: 80%

Find: Annual energy and cost savings

Solution:

Fan energy savings:

Full flow power: 7.5 hp = 5.6 kW

Idle flow power (40% flow): $5.6 \times 0.40^3 = 0.36$ kW

Daily fan energy savings (8 hr idle): $$E_{fan} = (5.6 - 0.36) \times 8 = 41.9 \text{ kWh/day}$$

Annual: $41.9 \times 365 = 15,294$ kWh/yr

Cost: $15,294 \times 0.12 = $1,835/yr

Makeup air heating savings:

Full flow heating (8 hr cooking): $$Q = 1.08 \times 6,000 \times (65-20) = 291,600 \text{ Btu/hr}$$

Idle flow heating (8 hr idle): $$Q_{idle} = 1.08 \times 2,400 \times (65-20) = 116,640 \text{ Btu/hr}$$

Daily heating reduction: $$\Delta Q = (291,600 - 116,640) \times 8 = 1,399,680 \text{ Btu/day}$$

Annual: $1,399,680 \times 365 = 510,893,280$ Btu/yr = 5,109 therms/yr

Accounting for 80% furnace efficiency: $5,109 / 0.80 = 6,386$ therms/yr

Cost: $6,386 \times 0.80 = $5,109/yr

Total annual savings: $$$1,835 + $5,109 = $6,944/yr$$

If DCKV system costs $15,000 installed:

Simple payback: $15,000 / $6,944 = 2.2 years

Answer: $6,944/year savings (2.2 year payback)

Kitchen Air Balance and Pressurization

Negative pressure target: -0.02" to -0.05" w.g. relative to dining areas

Purpose:

  • Prevent cooking odors migrating to dining room
  • Maintain directional airflow (dining → kitchen → exhaust)

Air balance: $$CFM_{exhaust} > CFM_{makeup} + CFM_{transfer}$$

Typical imbalance: 10-20% exhaust exceeds supply (creates negative pressure)

Transfer air from dining:

  • Relief air grilles or undercut doors
  • 100-200 CFM per door opening typical
  • Dining room must have adequate supply air (HVAC oversized for transfer)

Dishwasher Exhaust

Type II hood or dedicated exhaust:

  • Steam exhaust: 75-150 CFM per ft² dishwasher footprint
  • Condensate hood (water-cooled): Captures steam, condenses to drain

Makeup air for dishwasher:

  • Not required if Type II hood exhaust < 400 CFM (IMC exception)
  • Recommended for large commercial dishwashers (prevent backdraft)

Related Technical Guides:

References:

  • ASHRAE Handbook HVAC Applications, Chapter 35: Kitchen Ventilation
  • NFPA 96: Standard for Ventilation Control and Fire Protection of Commercial Cooking Operations
  • IMC (International Mechanical Code), Chapter 5: Exhaust Systems
  • UL 710: Standard for Exhaust Hoods for Commercial Cooking Equipment
  • ASHRAE 154P: Standard Method of Test for Demand-Controlled Kitchen Ventilation
  • Exxo-Air (Resource): Kitchen Ventilation Design Guide