TCE DSIGN GUIDE.pdf

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SECTION:TITLE

DESIGN GUIDE FOR HVAC SYSTEM

FOR GREEN BUILDINGS SHEET i OF iv

REV. NO. R0

ISSUE INITIALS SIGN. INITIALS SIGN. INITIALS SIGN. INITIALS SIGN.

PPD. BY RST Sd

R0

CHD. BY PRJ Sd

APD. BY GSK Sd

DATE 24.06.2010

FILE NAME: F020R4.DOC TCE FORM NO. 020 R4

DESIGN GUIDE FOR HVAC SYSTEM

FOR GREEN BUILDINGS

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SECTION: CONTENTS DESIGN GUIDE FOR HVAC SYSTEM

FOR GREEN BUILDINGS

SHEET ii OF iv OF 4

TCE FORM NO. 120 R3 FILE NAME: F120R3.DOC

ISSUE R0 CONTENTS SL. NO. TITLE SH. NO. 1.0 INTRODUCTION 1 2.0 SCOPE 1 3.0 DESIGN REQUIREMENTS 1 4.0 REFERENCES 16 APPENDICES APPENDIX NO. TITLE SH. NO.

1 REFRIGERANT IMPACT CALCULATION 17

2 A BUILDING ENVELOPE REQUIREMENTS AS PER ECBC-2007 19

2 B BUILDING ENVELOPE REQUIREMENTS AS PER ASHRAE

90.1.2007 20

3 ASSEMBLY U FACTORS & SHGC FOR UNLABELED

VERTICAL FENESTRATION & SKYLIGHTS 21

4 EQUIPMENT EFFICIENCIES AS PER ECBC-2007 22

5 EQUIPMENT EFFICIENCIES AS PER ASHRAE 90.1.2007 23

5 A AIR CONDITIONERS & CONDENSING UNITS 23

5 B WATER CHILLING PACKAGES 25

5 C PACKAGE UNITS 26

5 D HEAT REJECTION EQUIPMENTS 28

5 E NON-STANDARD CENTRIFUGAL CHILLERS UPTO 150 TR 29

5 F NON-STANDARD CENTRIFUGAL CHILLERS FROM 151 TR

TO 300 TR 30

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6 PSYCHROMETRIC CHART (FREE COOLING SYSTEM) 32

7 FAN POWER LIMITATION PRESSURE DROP ADJUSTMENT 33

8 DUCT INSULATION 34

9 PIPING INSULATION 35

10 MINIMUM DUCT SEAL LEVEL 36

11 OUTDOOR AIR FLOW CALCULATION 37

12 A MINIMUM VENTILATION RATES 38

12 B MINIMUM EXHAUST RATES 40

12 C ZONE AIR DISTRIBUTION EFFECTIVENESS 41

12 D SYSTEM VENTILATION EFFICIENCY 42

13 MINIMUM SEPARATION DISTANCE 43

14 LIGHTING POWER DENSITIES 44

15 VOC LIMITS 47

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ISSUE R0 REVISION STATUS REVISION NO. DATE DESCRIPTION R0 24.06.2010 First issue

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R0 TCE FORM NO. 120 R3 FILE NAME: F120R3.DOC

1.0 INTRODUCTION

The built environment has a profound impact on our natural environment, economy, health, and productivity. Breakthroughs in building science, technology, and operations are now available to designers, builders, operators, and owners who want to build green and maximize both economic and environmental performance.

The green building movement offers an unprecedented opportunity to respond to the most important challenges of our time, including global climate change, dependence on non sustainable and expensive sources of energy, and threats to human health.

Green building is the practice of increasing the efficiency with which buildings

use resources -- energy, water, and materials — while reducing building

impacts on human health and the environment during the building's lifecycle.

2.0 SCOPE

This document gives guidelines for design of HVAC system for Green Buildings.

3.0 DESIGN REQUIREMENTS

Following requirements should be met for the HVAC system for Green Buildings to acquire various prerequisites & credits as per LEED (Leadership in Energy and Environmental Design) rating system:

3.1 REFRIGERANTS

3.1.1 Minimum requirement: Zero use of CFC based refrigerants in new building HVAC & R systems. In case of renovations or using existing HVAC & R equipments, identify existing equipments that uses CFC refrigerants & schedule for replacement of these refrigerants.

3.1.2 As per Indian Green Building Council (IGBC)-LEED rating system, equipment that do not contain HCFCs should be used for getting additional credits. Whereas as per LEED-USGBC HVAC&R equipment must comply with the following formula, which sets a maximum threshold for the combined contributions to ozone depletion and global warming potential:

LCGWP + LCODP x 105 100

Where

LCODP = [ODPr x (Lr x Life +Mr) x Rc] / Life

LCGWP = [GWPr x (Lr x Life + Mr) x Rc] / Life

LCODP : Lifecycle Ozone Depletion Potential (lb CFC 11/Ton-Year)

LCGWP : Lifecycle Direct Global Warming Potential (lb CO2/Ton-Year)

GWPr : Global Warming Potential of Refrigerant (0 to 12,000 lb

CO2/lbr)

ODPr : Ozone Depletion Potential of Refrigerant (0 to 0.2 lb CFC

11/lbr)

Lr : Refrigerant Leakage Rate (0.5% to 2.0%; default of 2%

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Mr : End-of-life Refrigerant Loss (2% to 10%; default of 10%

unless otherwise demonstrated)

Rc : Refrigerant Charge (0.5 to 5.0 lbs of refrigerant per ton of

gross ARI rated cooling capacity)

Life : Equipment Life (10 years; default based on equipment type, unless otherwise demonstrated)

In case of multiple type of equipment average of all equipment must be calculated using following formula :

(LCGWP + LCODP x 105 ) x Qunit 100

QTotal

Where

Qunit : ARI rated cooling capacity of individual refrigeration / HVAC

unit (TR)

QTotal : Total ARI rated cooling capacity of all refrigeration / HVAC

unit (TR)

Sample Calculation for the same is shown in APPENDIX 1.

3.1.3 Select HVAC&R equipment with reduced refrigerant charge and increased equipment life. Maintain equipment to prevent leakage of refrigerant to the atmosphere.

3.2 BUILDING ENVELOPE

3.2.1 The exterior building envelope shall be designed with either Residential or

Non-residential requirements in APPENDIX 2, Building Envelope

Requirements, (excerpts from American Society of Heating, Refrigerating and Air-Conditioning Engineers (ASHRAE) 90.1.2007 & Energy Conservation Building Code (ECBC)). As per green building requirements stringent requirements of the above (ASHRAE or ECBC) shall be followed.

For all opaque surfaces, compliance to standard shall be demonstrated by either Minimum rated R values of insulation or Maximum U factor.

3.2.2 The total vertical fenestration area shall be less than 40% (as per ASHRAE 90.1.2007) of the gross wall area. In ECBC vertical fenestration area limit is up to 60% of the gross wall area. The total skylight area shall be less than 5% of the gross roof area as per ASHRAE 90.1.2007 and ECBC.

3.2.3 Design building envelope so that space conditions are maintained within the range specified in ASHRAE standard 55-2004, Thermal comfort Conditions for Human Occupancy. Documentation shall be as under (Excerpts from ASHRAE standard 55-2004, Section 6.1.1)

(i) The design criteria of the system in terms of indoor temperature, humidity, including any tolerance based on stated design outdoor ambient conditions and total indoor loads should be stated.

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(ii) The system input or output capacities necessary to attain the design indoor conditions at design outdoor ambient conditions should be stated along with system supplied and installed capacities.

(iii) The limitations of the system to control the environment of the zone(s) should be stated.

(iv) The overall space supplied by the system should be shown in a plan view layout, with all individual zones within it identified. All terminal units should be shown with type and flow.

(v) Items affecting indoor comfort (such as decor, significant structural items) should be shown. Notes should be provided to identify areas and location within space relative to grilles, diffuser, sensors which should not be obstructed.

(vi) Areas within any zone that lie outside the comfort area, where people should not be permanently located, should be identified.

(vii) Location of all occupant adjustable controls should be identified and each should be provided with a legend describing which zone(s) and function it controls, how it is to be adjusted, the range of effect it can have and recommended setting for various times of day, season or occupancy load. (viii) A block diagram control schematic should be provided with sensors,

controls and actuators identified for each zone.

(ix) The general maintenance, operation and performance of the building systems should be state, followed by more specific comments on maintenance and operation of automatic controls and manually adjustable controls and the response of the system to each. Where necessary, specific seasonal settings of manual controls should be stated and major system changeovers that are required to be performed by a professional service agency should be identified.

(x) Specific limits in the adjustment of manual controls should be stated. Recommendations for seasonal settings on these controls should be stated. A maintenance and inspection schedule for all thermal environmental related systems should be provided.

(xi) Assumed electrical load for lighting and equipment in occupied spaces (including diversity considerations) used in HVAC load calculations should be documented along with any other significant thermal and moisture loads assumed in HVAC load calculations and any other assumptions based upon which HVAC and control design is based. 3.2.4 Fenestration and Doors

Where fenestration and doors are used in the building envelope, it shall comply with following requirements:

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3.2.4.1 The U factor, SHGC & air leakage rate shall be determined by a laboratory accredited by a nationally recognized accreditation organization such as National Fenestration Rating Council (NFRC).

3.2.4.2 U factors & SHGC for the overall fenestration product shall be determined in accordance with ISO 15099 as per ECBC or NFRC 100 & NFRC 200 respectively as per ASHRAE 90.1.2007. Or alternatively U factors & SHGC from APPENDIX 3, Assembly U factors & SHGC for unlabeled vertical fenestration & skylights, are acceptable.

3.2.4.3 U factors for unlabeled opaque doors shall be as under

(a) Un-insulated single layer metal swinging or non-swinging doors, including single layer un-insulated access hatches : 1.45 Btu/hr ft2 °f

(b) Un-insulated double layer metal swinging or non-swinging doors, including

double layer un-insulated access hatches : 0.75 Btu/hr ft2 °f

(c) Insulated metal swinging doors including fire rated doors, insulated access hatches : 0.50 Btu/hr ft2 °f

(d) Wood doors , minimum nominal thickness of 1.75” including panel doors

with minimum panel thickness of 1.125” , solid core flush doors, & hollow core flush doors :0.50 Btu/hr ft2 °f

(e) Any other wood door : 0.60 Btu/hr ft2 °f

3.2.4.4 The U factor & the air leakage rate shall be identified on a permanent nameplate installed on the product by the manufacturer.

3.2.5 Air Leakage Rates

3.2.5.1 All openings in the building envelope such as joints around doors & fenestrations, corners, utility services penetrations, openings shall be sealed, gasketed or weather stripped to minimise air leakage.

3.2.5.2 Air leakage shall not exceed 1 cfm/ft2 for glazed swinging entrance doors & 0.4 cfm/ft2 for all other products.

3.2.6 Insulation

Where insulation is used in the building envelope it shall comply with following requirements:

3.2.6.1 The rated R value of the insulation shall be clearly identified by the manufacturer on each piece of building envelope insulation

3.2.6.2 Insulation material shall be installed as per manufacturer’s recommendation, in substantial contact with inside surface & in such a manner so as to achieve the rated R value of the insulation.

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3.2.6.3 Roof insulation shall not be installed on a suspended ceiling with removable ceiling panels.

3.2.6.4 Loose fill insulation shall not be used in attic roof spaces when slope of the ceiling is more than 3:12

3.2.6.5 Insulation material in ground contact shall have water absorption rate no greater than 3%when tested in accordance with ASTM C272

3.2.6.6 Flexible bat insulation installed in floor cavities shall be supported in a permanent manner by supports no greater than 24” on centre.

3.2.6.7 Any equipment, fixtures shall not be recessed in such a manner as to affect the insulation thickness.

3.2.6.8 Exterior insulation shall be covered with protective material to prevent damage from moisture, sunlight, wind, maintenance.

3.2.6.9 Insulation shall extend over the full component area to the required rated R value of insulation.

3.3 HVAC EQUIPMENTS

3.3.1 Equipment Efficiencies

3.3.1.1 HVAC equipments shall have minimum performance as per APPENDIX 4, Minimum Equipment Efficiency requirements as per ECBC-2007 or APPENDIX 5, Minimum Efficiency requirements as per Ashrae 90.1.2007, whichever is stringent, at specified rating conditions when tested in accordance with specified test procedure. Where multiple rating conditions or performance requirements are provided, the equipment shall satisfy all rated conditions. APPENDIX details are as under :

APPENDIX 4 Minimum Efficiency Requirement As per ECBC

APPENDIX 5 Minimum Efficiency Requirement as

per ASHRAE 90.1.2007 as under

APPENDIX 5 A Air Conditioners & Condensing Units

APPENDIX 5 B Water Chilling Packages

APPENDIX 5 C Package Units

APPENDIX 5 D Heat Rejection Equipments

Water cooled Centrifugal Chillers that are not designed for operation at ARI standard 550/590 test conditions shall have performance requirements (full load COP & NPLV) as per following APPENDICES:

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APPENDIX 5 F 150 TR Chiller Capacity < 300 TR

APPENDIX 5 G Chiller Capacity 300 TR

The table values are applicable over the following full load design range :

Leaving Chilled water temperature :40°F to 48°F

Entering Condenser water temperature :75°F to 85°F

Condenser water temperature rise :5°F to 15°F

3.3.1.2 Equipment efficiencies information provided by the manufacturer shall be verified by certified programme & data furnished by manufacturer

3.3.1.3 Equipments shall carry a permanent label installed by manufacturer stating that the equipment complies with the requirements of ASHRAE standard 90.1 3.3.2 Air and Water Economizers

3.3.2.1 Each individual cooling fan system that has a design supply capacity over 2500 cfm and a total mechanical cooling capacity over 6.3 TR shall include either air side or water side economizer(as per para 5.3.1 of ECBC). Projects in Hot dry and Warm humid climate zones are exempt and individual ceiling mounted fan systems (<6500 cfm) are exempt.

3.3.2.2 Free Cooling: When the enthalpy of the outside air is less than the enthalpy of the mixing air (outside air + return air), conditioning the outside air is more energy efficient than conditioning mixing air. Air economizer can be used to implement the scheme. Air economizer consists of modulating outdoor air damper, return air damper, exhaust air dampers and control system to operate them. Operating characteristic of the economizer system is illustrated below for different conditions (Case I, Case II & Case III). Also refer attached psychrometric chart, APPENDIX 6.

Case I - When the enthalpy of outside air (hos) is higher than the

mixing air enthalpy (hmc), hos > hmc

(i) The outdoor air damper is opened to a minimum position,

taking minimum outdoor air required for ventilation.

(ii) Return air damper is fully open and exhaust air damper is

opened to a minimum position.

(iii) Refrigeration plant is working to cool the mixing air to the supply air temperature.

Case II - When the enthalpy of outside air is equal to or lower than

the mixing air enthalpy but more than the supply air enthalpy (hsa), hsa

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(i) The outdoor air damper and exhaust air damper both are fully

open.

(ii) Return air damper is closed.

(iii) Refrigeration plant is working to cool the outdoor air to the supply air temperature.

Case III - When the enthalpy of outside air is lower than the supply air enthalpy, hos ≤ hsa

(i) The outdoor air damper and Return air damper both are

modulated to achieve the supply air temperature.

(ii) Exhaust air damper is also modulated.

(iii) Refrigeration plant is switched off

Careful analysis is required for designing & implementing the above scheme considering outside conditions throughout the year.

3.3.3 Each HVAC system having a total fan system motor nameplate hp exceeding 5 hp shall meet the following :

3.3.3.1 Each HVAC system at fan system design conditions shall not exceed the allowable fan system motor nameplate hp (Option 1) or fan system bhp (Option 2) as shown below

Limit Constant Volume Variable Volume

Option1 Allowable hp ≤ CFM*0.0011 hp ≤ CFM*0.0015

nameplate Motor HP

Option2 Allowable bhp ≤ CFM*0.00094+A bhp ≤ CFM*0.0013+A

fan system BHP

where CFM is the maximum design supply air flow rate to conditioned spaces served by the system in cfm and A is the sum of (PD x CFM (through each device) / 4131). PD shall be as given in the APPENDIX 7

3.3.3.2 The selected fan motor shall be no larger than the first available motor size greater than the bhp.

3.3.3.3 Individual VAV fans with motors 10 hp or larger shall meet one of the following requirement

(a) The fan shall be driven by a mechanical or electrical variable speed

drive

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(c) The fan shall have other controls and devices that will result in fan motor

demand of no more than 30% of design wattage at 50% of design air volume when static pressure set point equals one third of the total design static pressure based on manufacturers certified fan data.

3.3.4 HVAC hydronic systems having a total pump power exceeding 10 hp shall meet following provisions

3.3.4.1 HVAC pumping systems that include control valves designed to modulate or step open and close as a function of load shall be designed for variable fluid flow and shall be capable of reducing pump flow rates to 50% or less of the design flow rate. Individual pumps serving variable flow systems having a pump head in excess of 100 ft and motor exceeding 50 hp shall have controls and/or devices (such as variable speed control) that will result in pump motor demand of no more than 30% of design wattage at 50% of design water flow. The devices shall be controlled as a function of desired flow or to maintain a minimum required differential pressure. Differential pressure shall be measured at or near the most remote heat exchanger requiring the greatest differential pressure.

3.3.4.2 When a chilled water plant includes more than one chiller, provisions shall be made so that the flow in the respective chiller can be automatically stopped when a chiller is shut down.

3.3.5 Each fan of heat rejection equipment (whose energy usage is not included in equipment efficiency tables listed in Sr. No. 3.3.1.1) of motor rating 7.5 hp or larger shall have the capability to operate at 2/3rd of full speed or less and shall have speed controls to control the leaving fluid or condensing temperature or pressure of the heat rejection equipment.

3.3.6 Individual fan systems that have both a design supply air capacity of 5000 cfm or greater and have a minimum outdoor air supply of 70% or greater of the design supply air quantity shall have an energy recovery system with at least 50% recovery effectiveness (i.e. Change in enthalpy of the outdoor air supply equal to 50% of the difference between the outdoor air and return air at design conditions).

3.3.7 Kitchen exhaust hoods larger than 5000 cfm shall be provided with makeup air sized for at least 50% of exhaust air volume.

3.3.8 Building with fume hood systems having a total exhaust rate greater than 15000 cfm shall include at least one of the following features

3.3.8.1 VAV hood exhaust and room supply systems capable of reducing exhaust and makeup air volume to 50% or less of design values

3.3.8.2 Direct make up air supply equal to at least 75% of the exhaust rate, cooler to no cooler than 3°F above room set point and heated no warmer than 2°F below room set point, no humidification added, no simultaneous heating and cooling used for dehumidification control.

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3.3.8.3 Heat recovery system to precondition makeup air from fume hood exhaust in accordance with Sr. No. 3.3.6

3.3.9 Controls

3.3.9.1 Design the HVAC system (heating & cooling both) to provide individual comfort controls to allow adjustments to suit individual needs. Also provide comfort controls for all shared multi-occupant spaces to enable adjustments that meet group needs. Conditions of thermal comfort shall be as described in ASHRAE standard 55-2004.

3.3.9.2 Controls for metering the energy used shall be included in the design.

3.3.9.3 Temperature range or dead band for controls shall be 5°F except for special applications

3.3.9.4 When HVAC systems are not intended to operate continuously , HVAC system shall be designed with controls (i) that shall start and stop the system under different time schedule , (ii) an occupant sensor that is capable of shutting the system off when no occupant is sensed for a period of 30 minutes, (iii) a manually operated timer capable of bring adjusted to operate the system for upto two hours, (iv) an interlock with the security system that shuts the system off when the security system is activated.

3.3.9.5 Individual HVAC systems having capacity in excess of 10000 cfm shall have the optimum start control, the control algorithm as a minimum shall be a function of difference between space temperature and occupant set point and amount of time prior to scheduled occupancy.

3.3.9.6 HVAC systems serving zones that may operate non simultaneously shall be divided into isolated areas. Zones shall be grouped so that no individual zone exceeds 25000 ft2 of conditioned floor area. Controls shall be provided for automatic shutting off the system in particular zone when system is not in use.

3.3.9.7 Stair and shaft vents shall be equipped with motorized dampers that are capable of being automatically closed during normal building operation & are interlocked to open when required by fire and smoke detection system. All outdoor supply air and exhaust air systems shall be equipped with motorised dampers that will automatically shut down when the spaces served are not in use.

3.3.9.8 Outdoor air supply & exhaust dampers shall have a maximum leakage rate not more than 4 cfm / ft2 @ 1” SP for motorized dampers & no leakage at 1” SP for non motorized damper. However damper smaller than 24” in either dimension may have leakage of 40 cfm/ft2

3.3.10 Insulation

3.3.10.1 All supply & return ductwork insulation shall be in accordance with APPENDIX 8, Duct Insulation

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3.3.10.2 All piping insulation shall be in accordance with APPENDIX 9, Piping Insulation

3.3.10.3 Insulation exposed to weather shall be protected by aluminium, sheet metal, painted canvas or plastic cover.

3.3.11 Ductwork and plenum shall be sealed in accordance with APPENDIX 10, Minimum Duct Seal Level

3.3.12 Ductwork that is designed to operate at static pressures in excess of 3” w.c. shall be leak tested for 25% of the installed duct area. The maximum permitted leakage shall be

Lmax = CL x P0.65 where

Lmax =Maximum permissible leakage , cfm / 100 ft2 duct surface area

CL =Duct leakage class, cfm / 100 ft2 at 1” W.C.

6 for rectangular sheet metal / fibrous & round flexible ducts 3 for round/flat oval sheet metal / fibrous glass duct

P =test pressure (design duct pressure)

3.3.13 Completion Requirements

Following construction documents shall be provided to building owner or representative within 90 days of acceptance of the system:

(a) As built drawings

(b) Operation & Maintenance Manual

(c) Air & Water balancing reports

3.3.14 HVAC Electrical equipment & cabling

(a) All Motors shall have a minimum acceptable nominal full load motor efficiency not less than IS 12615 standard for energy efficient motors (b) Feeder conductors shall be sized for a maximum voltage drop of 2% at

design load. Branch circuit conductors shall be sized for a maximum voltage drop of 3% at design load

3.4 VENTILATION FOR ACCEPTABLE INDOOR AIR QUALITY

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3.4.1.1 Outdoor air quality shall be evaluated for the project site prior to completion of ventilation system design for checking the outdoor air contamination levels. A survey of the building site & its immediate surroundings shall be conducted during hours the building is expected to be normally occupied to identify local contaminants from surrounding facilities. The observations of the survey shall be documented (as per ASHRAE 62.1.2004) & discussed with the building owner or their representatives.

3.4.1.2 If the outdoor air is judged to be unacceptable in accordance with ASHRAE 62.1.2004, ventilation system that provides outdoor air through a supply fan shall comply with the following :

(a) Air filters having MERV of 6 or higher shall be provided

(b) Air cleaning devices having minimum volumetric ozone removal efficiency of 40% for ozone shall be provided when outdoor ozone levels are expected to exceed 0.16 ppm. Air cleaning devices for ozone are not required when outdoor air intake results in 1.5 ACPH or less

3.4.2 Mechanical Ventilation

3.4.2.1 As a minimum requirement for green buildings, mechanical ventilation systems shall be designed using the Ventilation Rate Procedure (VRP) or the applicable local code whichever is more stringent. Refer APPENDIX 11, for Ventilation Rate Procedure details. Further additional credit points can be acquired by increasing the ventilation rates to all occupied spaces by at least 30% above minimum rates required by ASHRAE standard 62.1.2004. Minimum ventilation rates are given in APPENDIX 12 A. One example is given in APPENDIX 16.

3.4.2.2 Various tables required for calculation in ventilation rate procedure are given as under :

APPENDIX 12 A - Minimum Ventilation Rates for Breathing Zone

APPENDIX 12 B - Minimum Exhaust Rates

APPENDIX 12 C - Zone Air Distribution Effectiveness

APPENDIX 12 D - System Ventilation Efficiency

3.4.2.3 Demand control ventilation (DCV) is required for spaces larger than 500 ft2 and with design occupancy for ventilation of greater than 40 people per 1000 ft2 of floor area and served by systems with either an air side economizer or automatic modulating control of the outside air damper or both.

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DCV is a system that adjusts the amount of outside air based on the number of occupants and the ventilation demands that those occupants create. DCV

systems uses CO2-based sensors, which measure the buildup of CO2 from

the occupants present and control the outside air flow. In this system CO2

sensors monitor CO2 levels in the air inside a building or occupied areas, and

an air-handling system uses this data from the sensors to regulate the amount of ventilation air admitted.

3.4.2.4 Use heat recovery, where appropriate, to minimize the additional energy consumption associated with higher ventilation rates.

3.4.2.5 Indoor Air Quality (IAQ) procedure can be used as an alternative to VRP (described at Sr. No. 3.4.2.1) as per Ashrae standard 62.1. IAQ procedure allows credit to be taken for controls that remove contaminant. It is also used where the design is intended to attain specific target contaminant concentrations or levels of acceptability of perceived indoor air quality. Air purification equipment are used in the HVAC systems enabling a reduction in ventilation air flow rates from the levels required by VRP.

3.4.2.6 Use of controlled injection of ozone can help reduce the quantity of fresh air. Ozone is a powerful oxidant, which removes odour, Volatile Organic Compounds (VOC) and even fungi by oxidation. This reduces the oxygen requirement in the form of ventilation and air is mainly required for diluting

CO2. With ozone generators, ozone is injected into the central air conditioning

system (ducts) & concentration is controlled by sensors activated by excessive VOC concentrations & turned off by excess ozone concentration sensors. Ozone concentration is required to be kept below harmful limit (0.05 ppm as per Ashrae).

3.4.3 Natural Ventilation

3.4.3.1 Naturally ventilated spaces shall be permanently open to and within 8 m of operable wall or roof openings to the outdoors. Openable area shall be minimum of 4% of the net occupiable floor area.

3.4.3.2 An engineered natural ventilation system when approved by the authority having jurisdiction need not meet the above requirement

3.4.3.3 Credits may be acquired by designing natural ventilation system to meet recommendations set forth in the Chartered Institution of Building Services Engineers (CIBSE) Application manual 10:2005, follow flow diagram process shown in figure 2.8 of CIBSE Application Manual 10 OR

3.4.3.4 Follow 8 design steps, as under, described in Carbon Trust Good Practice Guide 237

(a) Develop design requirements (b) Plan air flow paths

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(d) Determine ventilation requirement (e) Estimate external driving pressures (f) Select types of ventilation devices (g) Size ventilation devices

(h) Analyze the design

OR Use public domain software such as NIST’s CONTAM, Multizone

modelling software, along with LoopDA, Natural ventilation sizing tool, to analytically predict room by room airflows.

3.4.4 Smoking rooms designed to contain, capture & remove environmental tobacco smoke (ETS) from the building must be directly exhausted to the outdoors, away from air intakes and building entry paths with no recirculation of ETS containing air. Exhaust shall be sufficient to create negative pressure differential with the surrounding spaces of at least an average of 0.02” of

water gauge & minimum of 0.004” of water gauge when doors to smoking

rooms are closed. Corridors common to ETS & ETS free areas shall be supplied with outdoor air at the rate of 0.1 cfm/ft2. Differential pressure generally used is 0.05” WC.

3.4.5 Sufficiently exhaust each space where hazardous gases or chemicals may be present or used to create negative pressure with respect to adjacent spaces when the doors to the room are closed. Exhaust rate must be at least 0.5 cfm / ft2 with no air recirculation. The pressure differential with the surrounding spaces must be at least an average of 0.02” & minimum of 0.004” when doors to the rooms are closed. Filters having MERV of 13 or higher must be provided for mechanically ventilated buildings. This requirement is used to acquire credit points and is not a mandatory requirement.

3.4.6 Minimum outdoor air intake shall be greater than the design maximum exhaust airflow when the mechanical air-conditioning are dehumidifying. 3.4.7 ASHRAE Standard 62.1 includes a design requirement intended to limit

relative humidity in zones. To comply with this, designers must analyze the performance of the proposed air conditioning system at relatively severe latent load conditions, namely, with outdoor air at dehumidification design condition (design dew point and mean coincident dry-bulb temperature) and with no zone sensible-heat gain due to solar load. This analysis tests the dehumidification capability of the HVAC system configuration and control. It must show that zone relative humidity does not exceed 65% RH at these conditions. Some systems in some buildings in some climates can meet this requirement without direct humidity control, e.g., VAV systems that supply cool, dry primary air at all conditions. Other systems, however, such as traditional single-zone constant volume systems, supply warmer, moister air at part-sensible load and cannot maintain 65% RH or less without some enhancement. To comply with Standard 62.1, these systems must be reconfigured, to limit relative humidity indirectly, or using a zone humidistat and local reheat.

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3.4.8 Location of outdoor air intakes shall be such that the shortest distance from the intake to any specific potential outdoor contaminant source shall be equal to or greater than the separation distance listed in APPENDIX 13, Minimum Separation distance

3.4.9 Outdoor air intakes that are part of the mechanical ventilation system shall be designed to manage Rain entrainment, Rain intrusion, Snow entrainment in accordance with the ASHRAE standard 62.1.2004

3.4.10 Air shall be classified and its recirculation shall be limited in accordance with the following :

(a) Class 1 air : Air with low contaminant concentration, low irritation intensity and inoffensive odour, may be recirculated or transferred to any space. (b) Class 2 : Air with moderate contaminant concentration, mild irritation

intensity and mild offensive odour, may be recirculated within the space of

origin or transferred or recirculated to other class 2 or class 3 or class 4 spaces utilized for similar purpose.

(c) Class 3 : Air with significant contaminant concentration, irritation intensity and offensive odour, may be recirculated within the space of origin. Shall

not be transferred or recirculated to any other space.

(d) Class 4 : Air with highly objectionable fumes or gases & at harmful concentrations, Shall not be transferred or recirculated to any other space

nor recirculated within space of origin.

Classification of air leaving each space shall be in accordance with APPENDIX 12 A, Minimum Ventilation Rates for Breathing Zone

3.4.11 Mechanical ventilation systems shall include controls, manual or automatic, that enable fan system to operate whenever the spaces served are occupied. The system shall be designed to maintain the minimum outdoor airflow under any load condition.

3.4.12 The system may be designed to reset the design outdoor air intake flow as operating conditions change, these conditions include but are not limited to : 3.4.12.1Variation in occupancy or ventilation rate or CO2 levels (DCV as described at

Sr. No. 3.4.2.3) in one or more individual zones.

3.4.12.2 A higher fraction of outdoor air in the supply due to intake of additional

outdoor air for free cooling or exhaust air make up.

3.4.12.3 All air stream surfaces in equipments and ducts shall be designed and constructed in accordance with ASHRAE standard 62.1.2004, Resistance to mould growth & erosion

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Lighting power densities must not exceed the densities for the classified zone given in ANNEXURE 12, Lighting Power Densities

3.6 LOW EMITTING MATERIALS

3.6.1 Specifications shall clearly state the VOC limits as given in ANNEXURE 13, VOC Limits, for coatings, adhesives & paints that may be used in construction / installation of HVAC system. All adhesives and sealants must comply with South Coast Air Quality Management District Rule 1168

3.7 BUILDING PERFORMANCE

As a minimum requirement for Green building, at least one of the following requirements shall be met.

3.7.1 LEED India requires establishing the minimum level of energy efficiency for the base building and systems and requires the building project to comply with mandatory provisions and prescriptive provisions of ASHRAE standard 90.1.2004 which are described above in earlier sections. Project should also comply with the final version of ECBC.

Whereas as per LEED (USGBC) rating system it is required to demonstrate a 10% improvement in the proposed building performance rating for new buildings, or a 5% improvement in major renovations to existing buildings, compared with the baseline building performance rating. Baseline building performance rating is calculated according to the building performance rating method of ASHRAE Standard 90.1-2007 using a computer simulation model for the whole building project. Ashrae Standard 90.1-2007 requires that the energy analysis done for the building performance rating method include all energy costs associated with the building project.

OR

3.7.2 Comply with the prescriptive measures of ASHRAE Advanced Energy Design Guide for Small Office Buildings 2004 / Small Retail Buildings 2006 / Small Warehouses & Self Storage Building 2008 or Core Performance Guide

3.7.3 Further, additional credits may be acquired by improving the performance of the proposed building (Ref 3.7.1). Credits are available up to 42% (48% as per LEED USGBC) improvement in performance of proposed building. This can be achieved by whole building energy simulation (using the Building Performance Rating Method in Appendix G of the ASHRAE standard 90.1) or prescriptive compliance path described in 3.7.2 above.

3.8 Green building design requirements also encourages use of onsite renewable

energy such as Solar, Wind, Geothermal, Bio mass & Bio gas strategies. However this is not a mandatory requirement at present and is used to acquire additional credit points for Green building certification.

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4.0 REFERENCES

4.1 LEED 2009 for New Construction and Major Renovations

4.2 Reference Guide for New Construction and Major Renovations (LEED-India

NC) Version 1.0

4.3 ASHRAE Standard 90.1.2007, Energy Standard for Buildings except Low

Rise Residential Buildings

4.4 ASHRAE Standard 62.1.2004, Ventilation for Acceptable Indoor Air Quality

4.5 Energy Conservation Building Code 2007

4.6 ASHRAE Standard 55-2004, Thermal comfort Conditions for Human

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APPENDIX 1

REFRIGERANT IMPACT CALCULATION

Sample calculation for arriving at the refrigerant impact is given here. Assumptions made for the calculation are as under

Total no. of systems in complete project :3 (System-1,2 and 3)

Refrigerant for Systems :R-134a for System-1, 2 and 3

CALCULATION TABLE

Description of system System-1 System-2 System-3 Total

Refrigerant R-134a R-134a R-134a

System Capacity TR 1000 1400 1400 3800 GWPr 1320 1320 1320 ODPr 0 0 0 Rc lb 3300 3990 3990 Life years 23 23 23 Lr % 2 2 2 Mr % 10 10 10 LCGWP 106059 128235 128235 LCODP 0 0.00 0.00 LCGWP + LCODP x 105 106059 128235 128235 362529 Total impact 95.4 Where

LCODP = [ODPr x (Lr x Life +Mr) x Rc] / Life

LCGWP = [GWPr x (Lr x Life + Mr) x Rc] / Life

LCODP : Lifecycle Ozone Depletion Potential (lb CFC 11/Ton-Year)

LCGWP : Lifecycle Direct Global Warming Potential (lb CO2/Ton-Year)

GWPr : Global Warming Potential of Refrigerant (0 to 12,000 lb

CO2/lbr). Values taken from Refrigerant Reference Guide,

National Refrigerants

ODPr : Ozone Depletion Potential of Refrigerant (0 to 0.2 lb CFC

11/lbr). Values taken from Refrigerant Reference Guide, National Refrigerants

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Lr : Refrigerant Leakage Rate (0.5% to 2.0%; default of 2%

Mr : End-of-life Refrigerant Loss (2% to 10%; default of 10%

Rc : Refrigerant Charge (0.5 to 5.0 lbs of refrigerant per ton of

gross ARI rated cooling capacity). Values taken from equipment Manufacturer.

Life : Equipment Life, Values taken from

equipment Manufacturer

Total impact (LCGWP + LCODP x 105 ) x Qunit 100

QTotal

Conclusion

1.0 Project satisfies minimum requirement of zero use of CFC refrigerant as

specified in Sr. No. 3.1.1

2.0 Project will get the additional credit as it satisfies the requirement of total impact less than 100.

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APPENDIX 2 A

BUILDING ENVELOPE REQUIREMENTS AS PER ECBC 2007

Walls & Roofs Climate

Zones*

Assembly Insulation Assembly Insulation

Max U Min R Value Max Min R Value

Btu/hr ft2 °f hr ft2 °f / Btu Btu/hr ft2 °f hr ft2 °f / Btu

Roofs

Composite 0.0460 R-19.8 0.0715 R-11.9

Hot & Dry 0.0460 R-19.8 0.0715 R-11.9

Warm & Humid 0.0460 R-19.8 0.0715 R-11.9

Moderate 0.0715 R-11.9 0.0715 R-11.9

Cold 0.0460 R-19.8 0.0715 R-11.9

Walls

Composite 0.0775 R-11.9 0.0775 R-11.9

Hot & Dry 0.0775 R-11.9 0.0775 R-11.9

Warm & Humid 0.0775 R-11.9 0.0775 R-11.9

Moderate 0.0759 R-10.2 0.0699 R-11.4 Cold 0.0650 R-12.5 0.0620 R-13.3 Fenestrations Climate Maximum Zones* U Factor WWR 40% 40%=WWR 60% Btu/hr ft2 °f Vertical Fenestration Composite 0.58 0.25 0.20

Hot & Dry 0.58 0.25 0.20

Warm & Humid 0.58 0.25 0.20

Moderate 1.22 0.40 0.30

Cold 0.58 0.51 0.51

Skylights

Climate With Curb W/o Curb 0 to 2% SRR 2.1 to 5% SRR

Zones* Btu/hr ft2 °f Btu/hr ft2 °f

Composite 1.98 1.36 0.40 0.25

Hot & Dry 1.98 1.36 0.40 0.25

Warm & Humid 1.98 1.36 0.40 0.25

Moderate 1.98 1.36 0.61 0.40

Cold 1.98 1.36 0.61 0.4

*Climate Zones as per ECBC , Climate Zone Map of India

Definitions :

WWR : Window to Wall Ratio, SRR : Skylight Roof Ratio

Maximum SHGC

Maximum SHGC Maximum U Factor

24 Hour use buildings Daytime use buildings

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APPENDIX 2 B

BUILDING ENVELOPE REQUIREMENTS* AS PER ASHRAE 90.1.2007

Opaque

Elements Assembly Insulation Assembly Insulation

Max U Min R Value Max Min R Value

Btu/hr ft2 °f hr ft2 °f / Btu Btu/hr ft2 °f hr ft2 °f / Btu Roofs

Insulation above deck 0.063 R-15 0.048 R-20

Metal Building 0.065 R-19 0.065 R-19

Attic & Other 0.034 R-30 0.027 R-38

Walls, Above grade

Mass 0.58 NR 0.151 R-5.7

Metal Building 0.113 R-13 0.113 R-13

Steel framed 0.124 R-13 0.124 R-13

Wood framed or other 0.089 R-13 0.089 R-13

Walls, Below grade C-1.14 NR C-1.14 NR

Floors

Mass 0.322 NR 0.322 NR

Steel Joist 0.35 NR 0.35 NR

Wood framed & other 0.282 NR 0.282 NR

Fenestration 0 to 40% of wall

Normal framing 1.2 1.2

Metal framing 1.2 1.2

(Curtainwall/Storefront)

*For Climate Zone 1 (A,B) & Prescriptive Building Envelope Option

Notes : (1) Either above U values can be specified / used or alternatively U values for pre-calculated assemblies can be used from APPENDIX A

of ASHRAE 90.1.2007. (2) For Min. R value, specifications listed in APPENDIX A shall be used to determine compliance. For Max. U value , the values for typical construction assemblies listed in APPENDIX A shall be used to determine compliance. (3) Component U factors for other assemblies (not listed in APPENDIX A) can be determined in accordance with Section A9 of ASHRAE 90.1.2007

Definitions :

mass wall : a wall with heat capacity exceeding (1) 7 Btu/ft2_{°F or (2) 5 Btu/ft}2_{°F, provided that the wall has a material unit weight not greater}

than 120 lb/ft3

metal building wall : a wall whose structure consists of metal spanning members supprted by steel structural members (i.e., does not include spandrel glass or metal panels in curtain wall systems)

steel framed wall : a wall with a cavity (insulated or otherwise) whose exterior surfaces are separated by steel framing members (i.e. typical steel stud walls & curtain walls system)

wood framed & other walls : all other wall types, including wood stud walls.

Non-Residential Residential

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APPENDIX 3

ASSEMBLY U FACTORS & SHGC FOR UNLABELED VERTICAL FENESTRATION & SKYLIGHTS

(A) FOR VERTICAL FENESTRATION

Frame Glazing

Type Type U Factor SHGC U Factor SHGC

Btu/hr ft2 °f Btu/hr ft2 °f

All frame types Single glazing 1.25 0.82 1.25 0.70

Wood, vinyl or Double glazing 0.60 0.59 0.60 0.42

fibreglass frames

Metal & other frames Double glazing 0.90 0.68 0.90 0.50

Clear Glass Tinted Glass

(B) FOR SKYLIGHTS

To determine the default U factor for unlabeled sloped glazing & skylights without a curb multiply the values in the above APPENDIX 3 by 1.2

To determine the default U factor for unlabeled sloped glazing & skylights on a curb multiply the values in the above APPENDIX 3 by 1.6

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APPENDIX 4

MINIMUM EQUIPMENT EFFICIENCY REQUIREMENT AS PER ECBC 2007

Sr. no. Equipment Class Minimum Minimum Test

COP IPLV Standard

1 Air Cooled Chillers < 530 kW 2.9 3.16 ARI 550 / 590

(<150 TR) 1998

2 Air Cooled Chillers > = 530 kW 3.05 3.32 ARI 550 / 590

(> = 150 TR) 1998

3 Centrifugal Water Cooled Chiller < 530 kW 5.8 6.09 ARI 550 / 590

(<150 TR) 1998

4 Centrifugal Water Cooled Chiller > = 530 kW & <1050 kW 5.8 6.17 ARI 550 / 590

(> = 150 TR & < 300 TR) 1998

5 Centrifugal Water Cooled Chiller >= 1050 kW 6.3 6.61 ARI 550 / 590

(> = 300 TR) 1998

6 Reciprocating Compressors, Water Cooled Chillers all sizes 4.2 5.05 ARI 550 / 590 1998 7 Rotary Screw & Scroll Compressor, Water Cooled Chillers 4.7 5.49 ARI 550 / 590

< 530 kW (< 150 TR) 1998

8 Rotary Screw & Scroll Water Cooled Chiller > = 530 kW 5.4 6.17 ARI 550 / 590 & <1050 kW ( > = 150 TR & < 300 TR) 1998 9 Rotary Screw & Scroll Water Cooled Chiller >= 1050 kW 5.75 6.43 ARI 550 / 590

(> = 300 TR) 1998

Notes: Heating & Cooling equipment not listed here shall comply with Ashrae 90.1 standard. Unitary Air conditioner shall meet IS 1391 Part 1

Split conditioner shall meet IS 1391 Part 2 Packaged air conditioner shall meet IS 8148

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APPENDIX 5 A

EQUIPMENT EFFICIENCIES – AIR CONDITIONERS AND CONDENSING UNITS (ASHRAE 90.1.2007)

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APPENDIX 5 B

EQUIPMENT EFFICIENCIES WATER CHILLING PACKAGES

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APPENDIX 5 C

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APPENDIX 5 D

EQUIPMENT EFFICIENCIES HEAT REJECTION EQUIPMENTS

Equipment Rating Performance Test

Type Conditions Requireda,b Procedure

Propeller or axial 95°F entering water

fan cooling towers 85°F leaving water CTI ATC-105c &

75°F wb outdoor air CTI STD-201d

Centrifugal fan 95°F entering water CTI ATC-105 &

cooling towers 85°F leaving water CTI STD-201

75°F wb outdoor air

Air cooled 125°F condensing temp.

condensers R-22 test fluid ARI 460

190°F entering gas temp 15°F subcooling 95°F entering db a

Cooling tower performance is defined as the maximum flow rating of the tower divided by the fan nameplate rated motor power b

Air cooled condenser performance is defined as the heat rejected from the refrigerant divided by the fan nameplate rated motor power c

Cooling Technology Institute , Acceptance Test Code for Water Cooling Towers d

Cooling Technology Institute , Stndard for Certification of Water Cooling Towers Thermal Performance = 38.2 gpm / hp

= 20 gpm / hp

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APPENDIX 5 E

EQUIPMENT EFFICIENCIES

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APPENDIX 5 F

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APPENDIX 5 G

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APPENDIX 6

PSYCHROMETRIC CHART (FREE COOLING SYSTEM)

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APPENDIX 7

FAN POWER LIMITATION PRESSURE DROP ADJUSTMENT

Device Adjustment

Fully ducted return and/or exhaust air systems 0.5" WC

Return and/or exhaust air flow control devices 0.5" WC

Exhaust filters, scrubbers, or other exhaust Pressure drop (PD) calculated at

treatment fan system design condition

Particulate filtration credit MERV 9 through 12 0.5" WC

Particulate filtration credit MERV 13 through 15 0.9" WC

Particulate filtration credit MERV 16 and greater PD calculated at 2xclean filter PD

and electronically enhanced filter at fan system design condition

Carbon and other gas phase air cleaners Clean filter PD at fan system

design condition

Heat recovery device PD of device at fan system

design condition

Evaporative humidifier / cooler in series with PD of device at fan system

another cooling coil design condition

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APPENDIX 8

DUCT INSULATION

Duct

Location Supply Duct Return Duct Supply Duct Return Duct

hr ft2 °f / Btu hr ft2 °f / Btu hr ft2 °f / Btu hr ft2 °f / Btu

Exterior R-7.9 R-3.4 R-6 R-3.5

Ventilated Attic R-7.9 R-3.4 R-7 R-3.5

Unventilated Attic w/o Roof

Insulation R-7.9 R-3.4 R-8 R-3.5

Unventilated Attic with Roof

Insulation R-3.4 No Requirement R-3.5 No Requirement

Unconditioned Space R-3.4 No Requirement R-3.5 No Requirement Indirectly Conditioned Space No Requirement No Requirement No Requirement No Requirement

Buried R-3.4 No Requirement R-3.5 No Requirement

a

Insulation R value is measured on a horizontal plane in acoordance with ASTM C518 at a mean temperature of 75°F at installed thk.

Required InsulationAs Per ASHRAE 90.1 Required Insulationa As Per ECBC

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APPENDIX 9 PIPING INSULATION

Design Required Insulation

Operating Temperature R-Value

hr ft2 °f / Btu

Temp > = 140°F (Heating Systems) R-4

139°F >= Temp > 104°F (Heating Systems) R-2

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APPENDIX 10

MINIMUM DUCT SEAL LEVEL

Seal Sealing Requirements

Level

A

All transverse joints, longitudinal seams and duct wall penetrations. Pressure sensitive tape shall not be used as primary sealant, unless it has been certified to comply with UL-181A or B by an independent testing laboratory

B

All transverse joints, longitudinal seams. Pressure sensitive tape shall not be used as primary sealant, unless it has been certified to comply with UL-181A or B by an independent testing laboratory

C Transverse joints only

Table 1 - Duct Seal Levels

Duct Return Exhaust

Location Upto 2" w.c. > 2" w.c. Duct Duct

Static Pressure Static Pressure

Outdoor A A A C

Unconditioned Spaces B A B C

Conditioned Spaces C B C B

a

Refer Table-1 for description of seal level

Supply Duct

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APPENDIX 11

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APPENDIX 12 A

MINIMUM VENTILATION RATES

cfm/person cfm/ft2 #1000ft2 cfm/person Cell 5 0.12 25 10 2 Day Room 5 0.06 30 7 1 Guard Stations 5 0.06 15 9 1 Booking/Waiting 7.5 0.06 50 9 2 Daycare(through age 4) 10 0.18 25 17 2 Classrooms(ages 5-8) 10 0.12 25 15 1 Classrooms(age 9 plus) 10 0.12 35 13 1 Lecture Classroom 7.5 0.06 65 8 1

Lecture hall (fixed seats) 7.5 0.06 150 8 1

Art classroom 10 0.18 20 19 2 Science Laboratories 10 0.18 E 25 17 -Wood/Metal shop 10 0.18 20 19 2 Computer Lab 10 0.12 25 15 1 Media Center 10 0.12 A 25 15 1 Music/Theater/Dance 10 0.06 35 12 1 Multi-use assembly 7.5 0.06 100 8 1

Restaurant Dining Rooms 7.5 0.18 70 10 2

Cafeteria/fast food dining 7.5 0.18 100 9 2

Bars, cocktail lounges 7.5 0.18 100 9 2

Conference/Meetings 5 0.06 50 6 1

Corridors - 0.06 - 1

Storage Rooms - 0.12 B - 1

Bedroom/Living Room 5 0.06 10 11 1

Barracks sleeping areas 5 0.06 20 8 1

Lobbies/prefunction 7.5 0.06 30 10 1

Multi-purpose assembly 5 0.06 120 6 1

Office Space 5 0.06 5 17 1

Reception areas 5 0.06 30 7 1

Telephone/Data entry 5 0.06 60 6 1

Main entry lobbies 5 0.06 10 11 1

Bank vaults/Safe deposit 5 0.06 5 17 2

Computer(not printing) 5 0.06 4 20 1 Pharmacy(prep. Area) 5 0.18 10 23 2 Photo Studios 5 0.12 10 17 1 People Outdoor Air Rate Area Outdoor Air Rate

Occupancy Category Notes Air Class

Default Values Occupant Density Combined Outdoor Air Rate Correctional Facilities Educational Facilities

Food and Beverage Service

General

Hotels, Motels, Resorts, Dormitories

Office Buildings

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Shipping/Receiving - 0.12 B - 1

Transportation waiting 7.5 0.06 100 8 1

Warehouses - 0.06 B - 2

Auditorium seating area 5 0.06 150 5 1

Places of religious workshop 5 0.06 120 6 1

Courtrooms 5 0.06 70 6 1 Legislative chambers 5 0.06 50 6 1 Libraries 5 0.12 10 17 1 Lobbies 5 0.06 150 5 1 Museums (Childrens) 7.5 0.12 40 11 1 Museums/gallaries 7.5 0.06 40 9 1

Sales (except as below) 7.5 0.12 15 16 2

Mall common areas 7.5 0.06 40 9 1

Barber shop 7.5 0.06 25 10 2

Beauty and nail salons 20 0.12 25 25 2

Pet shops (animal areas) 7.5 0.18 10 26 2

Supermarket 7.5 0.06 8 15 1

Coin-operated Laundries 7.5 0.06 20 11 2

Sports area(play area) - 0.3 - 1

Gym, stadium (play area) - 0.3 30 2

Spectator areas 7.5 0.06 150 8 1

Swimming (pool and deck) - 0.48 C - 2

Disco/dance floors 20 0.06 100 21 1

Health club/aerobics room 20 0.06 40 22 2

Health club/weight rooms 20 0.06 10 26 2

Bowling alley(seating) 10 0.12 40 13 1

Gambling casinos 7.5 0.18 120 9 1

Game arcaes 7.5 0.18 20 17 1

Stages, studios 10 0.06 D 70 11 1

GENERAL NOTES FOR TABLE 6.1

1 Related Requirements: The rate in this table are based on all other applicable requirements of this standard being met. 2 Smoking: This table applies to non-smoking areas. Rates for smoking permitted spaces must be determined using other

methods. See section 6.2.9 of Ashrae 62.1.2007 for ventilation requirement in smoking areas.

3 Air density: Volumetric airflow rates are based on an air density of 1.2 Kg/m3 which corresponds to dry air at a barometric

pressure of 1 atm (101.3 kPa) and an air temperature of 21 deg C. Rates may be adjusted for actual density but such adjustment is not required for compliance with this standard.

4 Default Occupant Density: The default occupant density shall be used when actual occupant density is not known. 5 Default Combined Outdoor Air Rate (per person): This rate is based on default occupant density.

6 Unlisted Occupancies: If the occupancy category for a proposed space or zone is not listed, the requirement for the listed occupancy category that is most similar in terms of occupant density, activities and building construction shall be used.

7 Healthcare facilities : Rates shall be determined in accordance with Appendix E.

ITEM-SPECIFIC NOTES

A For high school and college libraries, use values shown for public spaces , library.

B Rates may not be sufficient when stored materials include those having potentially harmful emissions.

C Rates does not allow for humidity control. Additional ventilation or dehumidification may be required to remove moisture D Rate does not include special exhaust for stage effects, e.g. dry ice vapors, smoke.

E No class of air has been established for this occupancy category.

Retail

Sports and Entertainment Public Assembly Spaces

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APPENDIX 12 B MINIMUM EXHAUST RATES

Occupancy Category Exhaust Notes Air Class

Air Rate cfm/ft2

Arenas 0.5 B 1

Art Classrooms 0.7 2

Auto repair rooms 1.5 A 2

Barber shops 0.5 2

Beauty & nail Salons 0.6 2

Cells with toilets 1 2

Copy, printing rooms 0.5 2

Darkrooms, Educational Science Labs 1 2

Janitor closets, trash rooms, recycling 1 3

Kitchenettes 0.3 2

Kitchens - Commercial 0.7 2

Locker/dressing rooms 0.25 2

Locker rooms 0.5 2

Paint spray booths -- F 4

Parking garages 0.75 C 2

Pet shops (animal areas) 0.9 2

Refrigerating machinery rooms -- F 3

Residential Kitchens 50 / 100 per unit G 2

Soiled laundry storage rooms 1 F 3

Storage rooms, chemical 1.5 F 4

Toilets - private 25 / 50 per unit E 2

Toilets - public 50 / 70 per unit D 2

Woodwork shop/classroom 0.5 2

Notes : A Stands where engines are run shall have exhaust systems that directly connect to the engine exhaust & prevent escape of fumes

B When combustion equipment is intended to be used on the playing surface additional dilution ventilation and/or source control shall be provided

C Exhaust not required if two or more sides comprise walls that are atleast 50% open to the outside D Rates are per water closet and / or urinal. Provide higher rates where periods of heavy use are expected, such as toilets in theatres, schools , sports facilities etc

E Rates is for toilet room intended to be occupied by one person at a time. For continuous system operation during normal hours of use, the lower rate may be used, otherwise use higher rate. F See other applicable standard for exhaust rate.