TRIBHUVAN UNIVERSITY INSTITUTE OF ENGINEERING PURWANCHAL CAMPUS, DHARAN A REPORT ON COOLING LOAD CALCULATION AND DUCT DESIGN OF DHARAN BUS TERMINAL PROJECT MEMBERS: SHREERAM SUBEDI(PUR076BME089) NEWTON POKHAREL(PUR076BME056) PARBESH KHADKA(PUR076BME067) SAILESH KUMAR SAH(PUR076BME078) RAJ KUMAR B.K.(PUR076BME070) SUBMITTED TO DEPARTMENT OF MECHANICAL ENGINEERING DHARAN, NEPAL SUPERVISED BY ER. KESHAV KUMAR ACHARYA MAY 3, 2024 ACKNOWLEDGEMENT The success of this project required a lot of guidance and assistance from many people and we are extremely fortunate to have obtained that guidance all along for the completion of our final year project work. Whatever we have achieved is the result of such guidance and assistance and we would not forget to thank them. Firstly, we would like to thank Institute of Engineering for including the final year project as a part of our curriculum. I would like to extend my heartfelt gratitude to Mr. Roshan Ghimire, the Head of Department of Mechanical Engineering at Purwanchal Campus, for his invaluable support throughout the completion of this project. His dedication to fostering a conducive academic environment has been truly inspiring. We extend our sincere gratitude to our supervisor, Er. Keshav Acharya Sir, for his invaluable guidance, unwavering support, and insightful feedback throughout the duration of this project. His expertise in the field of HVAC engineering has been instrumental in shaping our understanding and approach towards cooling load calculation and duct design. We would also like to express our heartfelt thanks to the site engineer Saroj Kumar Yadav for providing us with essential site data, sharing his practical insights, and facilitating our understanding of the terminal's unique requirements and constraints. His cooperation and assistance have been indispensable in ensuring the relevance and applicability of our solutions. We acknowledge the support of our campus family and group members for their encouragement and understanding during the course of project completion. 1 ABSTRACT This report presents a comprehensive analysis of cooling load calculation and duct design for the bus park terminal, focusing on the application of the Cooling Load Temperature Difference (CLTD) method for load estimation and the Equal Friction method for duct design. The study aims to optimize the thermal comfort and energy efficiency of the terminal while ensuring effective air distribution throughout the space. The cooling load calculation utilizes the CLTD method, considering various factors such as solar radiation, internal heat gains, and outdoor weather conditions to estimate the sensible heat gain within the terminal. By employing this method, we determine the peak cooling load requirements for different zones within the terminal, facilitating the selection of appropriately sized HVAC equipment. Furthermore, the duct design process employs the Equal Friction method to determine the duct sizes and layouts necessary to distribute conditioned air efficiently throughout the terminal. By maintaining consistent air velocity and pressure drop along the duct network, this method ensures uniform airflow to all occupied spaces, optimizing thermal comfort and minimizing energy consumption. This report provides detailed recommendations for the cooling load calculation and duct design of the bus park terminal. These recommendations aim to enhance the overall performance and sustainability of the terminal's HVAC system, contributing to a comfortable and energy-efficient environment for passengers and staff alike. 2 Table of Contents ACKNOWLEDGEMENT ......................................................................................................... 1 ABSTRACT ............................................................................................................................... 2 Acronyms and Abbreviations ..................................................................................................... 7 1. INTRODUCTION: ............................................................................................................. 8 1.1 2. 1.1.1 Based on Application: .......................................................................................... 8 1.1.2 Based on Air Conditioning Unit and Distribution System: ............................... 10 1.1.3 Based on Working Fluid Used: .......................................................................... 12 1.2 Simple Vapour Compression Refrigeration System .................................................. 13 1.3 Thermal Comfort: ...................................................................................................... 15 1.4 Problem Statement .................................................................................................... 15 1.5 Scope of Work ........................................................................................................... 15 1.6 General Objective:..................................................................................................... 15 1.7 Specific Objectives:................................................................................................... 16 Literature Review ............................................................................................................. 17 2.1 Psychrometrics .......................................................................................................... 17 2.1.1 Basic Properties of Moist Air:............................................................................ 17 2.1.2 Psychrometric Processes: ................................................................................... 17 2.1.3 Psychrometric Chart: ......................................................................................... 18 2.1.4 Applications in HVAC Design: .......................................................................... 19 2.2 3. Classification of HVAC System: ................................................................................. 8 Cooling Load Temperature Difference (CLTD) Method .......................................... 19 2.2.1 Identification of Building Components: ............................................................ 19 2.2.2 Determination of R and U values: ..................................................................... 19 2.2.3 Determination of wall and roof numbers: .......................................................... 20 2.2.4 Determination of CLTD Values: ........................................................................ 20 2.2.5 Calculation of Cooling Load:............................................................................. 21 2.2.6 Determination of Solar Heat Gain Factor/Coefficient: ...................................... 22 2.2.7 Consideration of Internal Gains: ........................................................................ 22 Theoretical Considerations ............................................................................................... 23 3.1 Indoor Air Quality ..................................................................................................... 23 3.2 Outdoor Air Quality .................................................................................................. 24 3.3 Bypass Factor ............................................................................................................ 24 3.4 Room Sensible heat. .................................................................................................. 25 3.4.1 Solar gain –glass ................................................................................................ 25 3 3.4.2 Solar and transmission gain through wall and roofs .......................................... 25 3.4.3 Transmission gain .............................................................................................. 25 3.4.4 Infiltration and by-passed air ............................................................................. 25 3.4.5 Internal heat ....................................................................................................... 25 3.5 4. 5. ROOM LATENT HEAT............................................................................................ 25 Methodology..................................................................................................................... 27 4.1 Site selection ............................................................................................................. 27 4.2 Data collection........................................................................................................... 27 4.3 U value calculations .................................................................................................. 29 4.4 Cooling load .............................................................................................................. 30 4.4.1 For glass, ............................................................................................................ 30 4.4.2 For walls............................................................................................................. 30 4.4.3 For roof .............................................................................................................. 33 4.5 System selection ........................................................................................................ 35 4.6 Duct sizes .................................................................................................................. 35 CONCLUSION ................................................................................................................ 39 References ............................................................................................................................ 40 Appendices ............................................................................................................................... 41 Appendix A: Climate Data ................................................................................................... 41 Appendix B: Cooling Loads ................................................................................................. 42 4 List of tables Table 1. Area conversion.......................................................................................................... 28 Table 2. Solar Heat Gain Through Glass ................................................................................. 30 Table 3. CLTD LM correction ................................................................................................. 31 Table 4. wall types, mass evenly distributed............................................................................ 32 Table 5. wall numbers .............................................................................................................. 33 Table 6. roof number. ............................................................................................................... 34 Table 7. Roof type .................................................................................................................... 34 Table 8. Room loads ................................................................................................................ 35 Table 9. Circular equivalent of Rectangular Duct ................................................................... 37 Table 10. branch duct sizes ...................................................................................................... 38 5 List of figures Figure 1. Commercial HVAC System ....................................................................................... 9 Figure 2. Residential HVAC System ......................................................................................... 9 Figure 3.Industrial HVAC System ........................................................................................... 10 Figure 4.Centralized System .................................................................................................... 11 Figure 5. Decentralized System ............................................................................................... 11 Figure 6. Air Based HVAC system .......................................................................................... 12 Figure 7. Water Based HVAC System ..................................................................................... 13 Figure 8. Simple Vapour Compression Refrigeration System ................................................. 14 Figure 9. Thermal Comfort ...................................................................................................... 15 Figure 10. Psychrometric Chart ............................................................................................... 18 Figure 11. First Floor plan ....................................................................................................... 27 Figure 12. Friction Loss in inches of water per 100 feet of duct ............................................. 36 Figure 13. duct sizer by McQuay............................................................................................. 37 6 Acronyms and Abbreviations Acronyms and Abbreviations Full forms Heating, Ventilation and Air Conditioning Vapour Compression Refrigeration System Variable Air Volume Cooling Load Temperature Difference Daily Range Apparatus Dew Point Cubic Feet per Minute HVAC VCRS VAV CLTD DR ADP CFM LM DBT WBT RH BTU ASHRAE Latitude Month Correction Dry Bulb Temperature Wet Bulb Temperature Relative Humidity British Thermal Unit American Society OF Heating, Refrigeration and Air Conditioning Engineers 7 1. INTRODUCTION: Dharan, a bustling town in eastern Nepal, has seen substantial growth in recent years. The increased commercial and transportation activities have necessitated the construction of a modern bus terminal to accommodate the growing needs of the area. The New Bus Terminal of Dharan is going to be built to address these needs with new facilities for all the civilians along with HVAC system for the enhancement of the comfort of transporters, Staffs, Workers, etc. The HVAC system is the must because of the geographical location of Dharan city which lies in the “Inner-Terai Region of Eastern Nepal”. The city is the main junction for Hilly and Himalayan districts of Eastern Nepal. Similarly, the city is the main hub of education too, where the students from almost all over the districts of Nepal come here for their educational enhancement. Moreover, the city is also the main hub of business so many people are coming and staying here for employment as well as business purposes. So here occurs higher mobility of people and transport vehicles. But, here is no well facilitated bus terminal still so far. This study explores the cooling load calculations and duct design for the new Dharan Bus Terminal, with a focus on energy efficiency and occupant comfort. 1.1 Classification of HVAC System: HVAC stands for Heating, Ventilation and Air Conditioning. The system typically refers to the system of providing heating, cooling and ventilation within the residentials and commercial buildings. The system is becoming an indispensable need for modern era because of rising the serious issues of global warming globally. The main components of HVAC are Heating, Ventilation and Air Conditioning. The need of HVAC is for Comfort enhancement, Humidity Controlment, Energy Efficient and Air Quality Maintenance. HVAC systems can be classified into different types based on several criteria, such as application, unit and distribution system, and working fluid used. These classifications help in determining the most suitable system for specific needs. 1.1.1 Based on Application: HVAC systems can be categorized by their primary use: Commercial HVAC System: A commercial HVAC (Heating, Ventilation, and Air Conditioning) system is designed to provide comfort and air quality in commercial spaces such as offices, malls, hospitals, and transportation hubs like bus terminals. These systems are typically larger and more complex than residential HVAC systems. These systems need to provide the comfort and safety of a high volume of people and operate continuously throughout the day. 8 Figure 1. Commercial HVAC System Residential HVAC Systems: A Residential HVAC (Heating, Ventilation, and Air Conditioning) system is designed to provide comfort and air quality in residential spaces such as in homes and apartments. These systems are typically smaller in scales and limited to individual homes. These system need to provide the comfort and safety of a small volume of people and operate continuously throughout the day. Figure 2. Residential HVAC System 9 Industrial HVAC Systems: A Industrial HVAC (Heating, Ventilation, and Air Conditioning) system is designed to provide comfort and air quality in industrial spaces such as in manufacturing plants, warehouses, data centres, and other production facilities. These systems are generally more robust and complex than residential or commercial HVAC systems. These systems have the unique environmental conditions and operational requirements in industrial settings. Figure 3.Industrial HVAC System 1.1.2 Based on Air Conditioning Unit and Distribution System: HVAC systems can also be categorized by their unit type and distribution method: Centralized Systems: A centralized HVAC (Heating, Ventilation, and Air Conditioning) system is a comprehensive system designed to provide heating, cooling, and ventilation to an entire building or structure from a single, centralized location. This system is commonly found in larger buildings like offices, malls, hospitals, and industrial facilities. The components of centralized system are Heating Equipment, Cooling Equipment, Ventilation System, Thermostat Controls, Ductwork, Air Filters and Purifiers, and Humidification and Dehumidification Systems. 10 Figure 4.Centralized System Decentralized Systems: A Decentralized HVAC (Heating, Ventilation, and Air Conditioning) system is a comprehensive system designed to provide heating, cooling, and ventilation to an entire building or structure from a separate areas or locations. It's commonly found in smaller buildings, multi-family residences, hotels, and some office buildings. Figure 5. Decentralized System 11 1.1.3 Based on Working Fluid Used: Another classification is based on the type of fluid used for heating or cooling: Air-based Systems: An air-based HVAC system is a type of heating, ventilation, and air conditioning system that uses air as the primary medium for distributing thermal energy (heating or cooling) and providing ventilation throughout a building or structure. These systems use ductwork, air handlers, and fans to circulate conditioned air to different areas or rooms. The Components of an Air-Based HVAC System are Air Handling Unit, Ductwork, Heating Equipment, Cooling Equipment, Ventilation System, and Thermostats. Figure 6. Air Based HVAC system 12 Water-based Systems: An water-based HVAC system is a type of heating, ventilation, and air conditioning system that uses water as the primary medium for distributing thermal energy (heating or cooling) and providing ventilation throughout a building or structure. These systems are common in both residential and commercial applications and can be used for various types of heating and cooling needs. These systems typically use pipes to transport heated or cooled water to different parts of the building. Figure 7. Water Based HVAC System 1.2 Simple Vapour Compression Refrigeration System A vapour compression refrigeration system is and improved type of air refrigeration system in which a suitable working substance termed as refrigerant is used. The refrigerant generally used are ammonia (NH3), carbon dioxide (CO2), Sulphur dioxide (SO2). Mechanism of a Simple Vapour Compression Refrigeration System Figure below shows the schematic diagram of a simple vapour compression refrigeration system. It consists of the following five essential parts. 1. Compressor: The low pressure and temperature vapour refrigerant from evaporator is drawn into the compressor through the inlet or suction valve, where 13 it is compressed to a high pressure and temperature. This high pressure and temperature vapour refrigerant is discharged into the condenser through the delivery valve. 2. Condenser: The condenser or cooler consists of coils of pipe in which the high pressure and temperature vapour refrigerant is cooled and condensed. The refrigerant, while passing through the condenser, gives up its latent heat to the surrounding condensing medium which is normally air or water. 3. Receiver: The condensed liquid refrigerant from the condenser is stored in a vessel known as receiver from where it is supplied to the evaporator through the expansion valve or refrigeration. 4. Expansion valve: It is also called throttle valve or refrigerant control valve. The function of the expansion valve is to allow the liquid refrigerant under high pressure and temperature. Some of the liquid refrigerant evaporates as it passes through expansion valve, but the greater portion is vaporized in the evaporator at the low pressure and temperature. 5. Evaporator: An evaporator consists of coils of pipe in which the liquid vapour refrigerant at low pressure and temperature is evaporated and changed into vapour refrigerant at low pressure and temperature. In evaporating, the liquid vapour refrigerant absorbs its latent heat of vaporization from the medium which is to be cooled. Figure 8. Simple Vapour Compression Refrigeration System 14 1.3 Thermal Comfort: Thermal comfort refers to the state in which individuals feel comfortable regarding temperature, humidity, and air movement. It is influenced by factors like air temperature, humidity, airflow, and personal activity levels. The goal of the HVAC system in the Dharan Bus Terminal is to maintain thermal comfort despite changing external weather conditions and high occupancy. Figure 9. Thermal Comfort 1.4 Problem Statement The main problem to be addressed is the design of an HVAC system that can handle the cooling load requirements of the Dharan Bus Terminal. This involves accurately calculating the cooling load, considering factors such as occupancy, equipment, lighting, and solar gains, and designing a duct system that effectively distributes conditioned air throughout the terminal. 1.5 Scope of Work The scope of work for this study includes: Calculating the cooling load for the Dharan Bus Terminal based on various factors. Designing an efficient duct system to ensure optimal distribution of conditioned air. Considering energy efficiency and sustainability in the design process. 1.6 General Objective: The general objective of this study is to design an HVAC system that provides effective cooling and maintains thermal comfort in the Dharan Bus Terminal while optimizing energy efficiency and sustainability. 15 1.7 Specific Objectives: The specific objectives of this study are: Cooling Load Calculation for Dharan bus terminal. Design a duct system that provides even distribution of conditioned air. 16 2. Literature Review The design of air conditioning systems for buildings is a crucial aspect of architectural and engineering planning, aiming to provide occupants with comfortable indoor environments while minimizing energy consumption and environmental impact. This literature review explores theoretical frameworks, methodologies, and best practices in air conditioning system design for buildings. 2.1 Psychrometrics Psychrometrics deals with the properties of moist air and its behaviour under various conditions. Key parameters include dry-bulb temperature, wet-bulb temperature, relative humidity, dew point temperature, and enthalpy. Understanding psychrometric properties is essential for analysing the air conditioning process, determining air properties at different system points (such as entering and leaving air conditions), and designing air handling units, ductwork, and distribution systems. Here's a detailed exploration of psychrometrics and its significance in HVAC design: 2.1.1 Basic Properties of Moist Air: Dry-Bulb Temperature (DBT): This is the temperature of the air measured with a standard thermometer. It indicates the sensible heat content of the air and is commonly used to represent air temperature in weather reports and HVAC calculations. Wet-Bulb Temperature (WBT): The wet-bulb temperature is the lowest temperature that can be reached by evaporating water into the air at constant pressure. It represents a combination of sensible and latent heat and is used to determine the adiabatic saturation temperature and calculate psychrometric properties. Relative Humidity (RH): Relative humidity is the ratio of the actual water vapor pressure in the air to the saturation vapor pressure at the same temperature, expressed as a percentage. It indicates the moisture content of the air relative to its capacity to hold moisture at that temperature. Dew Point Temperature: The dew point temperature is the temperature at which the air becomes saturated with moisture and condensation begins to form. It represents the temperature at which the air must be cooled at constant pressure to reach saturation. 2.1.2 Psychrometric Processes: Sensible Heating/Cooling: Sensible heating or cooling refers to changes in dry-bulb temperature without a change in moisture content. It involves adding or removing 17 sensible heat from the air through processes such as heating coils or cooling coils in HVAC systems. Latent Heating/Cooling: Latent heating or cooling involves changes in moisture content without a change in dry-bulb temperature. It occurs when moisture is added to or removed from the air through processes such as humidification or dehumidification. Mixing and Dilution: Mixing two air streams with different psychrometric properties results in a new air state with intermediate characteristics. Dilution refers to reducing the concentration of contaminants in the air by mixing it with a cleaner air stream. 2.1.3 Psychrometric Chart: Psychrometric charts are graphical representations of the psychrometric properties of air. They plot dry-bulb temperature, wet-bulb temperature, relative humidity, dew point temperature, specific volume, enthalpy, and other parameters on a set of axes. Psychrometric charts are valuable tools for HVAC engineers and designers as they allow for quick and accurate determination of air properties, calculation of heating and cooling loads, selection of air conditioning equipment, and analysis of air conditioning processes. Figure 10. Psychrometric Chart 18 2.1.4 Applications in HVAC Design: Psychrometrics is used extensively in HVAC design to determine design conditions, calculate heating and cooling loads, size equipment such as air handling units and cooling coils, and select appropriate air distribution strategies. Understanding psychrometric properties enables designers to create comfortable indoor environments by controlling temperature, humidity, and air quality effectively. Psychrometric analysis also facilitates energy-efficient design by optimizing system performance, minimizing energy consumption, and ensuring occupant comfort. 2.2 Cooling Load Temperature Difference (CLTD) Method The Cooling Load Temperature Difference (CLTD) method is a widely recognized and utilized technique in the field of HVAC engineering for estimating cooling loads in buildings. Developed by Carrier Corporation, this method offers a simplified yet accurate approach to calculate the heat gains and losses within a building's envelope. By leveraging CLTD values for different building components, engineers can efficiently design air conditioning systems tailored to specific environmental conditions, such as those found in the Dharan Bus Terminal. The CLTD method relies on the concept of temperature differences between indoor and outdoor conditions to estimate the cooling load of a building. The methodology involves several key steps: 2.2.1 Identification of Building Components: The first step in applying the CLTD method is to identify and categorize the various components of the building envelope, including walls, roofs, windows, and floors. 2.2.2 Determination of R and U values: Determining R-values (thermal resistance) and U-values (thermal transmittance) is crucial in assessing the thermal performance of building materials and assemblies. Here's how you can determine these values: 2.2.2.1 R-Value (Thermal Resistance): 19 R-value represents the ability of a material to resist heat flow. It is calculated by dividing the thickness of the material by its thermal conductivity. The formula for Rvalue is: 𝑻𝒉𝒊𝒄𝒌𝒏𝒆𝒔𝒔 𝑅��= 𝑻𝒉𝒆𝒓𝒎𝒂𝒍�𝒄𝒐𝒏𝒅𝒖𝒄𝒕𝒊𝒗𝒊𝒕𝒚 Thickness: Measure the thickness of the material in inches or meters. Thermal Conductivity: Obtain the thermal conductivity of the material from reliable sources such as material datasheets, manufacturers' specifications, or engineering handbooks. Thermal conductivity values are typically expressed in units such as BTU/(hr·ft²·°F) or W/(m·K). For composite materials or assemblies with multiple layers, the total R-value is calculated by summing the R-values of each layer: 𝑅�total = 𝑅�1 + 𝑅�2 + …. + 𝑅�𝑛� 2.2.2.2 U-Value (Thermal Transmittance): U-value represents the rate of heat transfer through a material or assembly. It is the reciprocal of the total thermal resistance (R-value) of the material or assembly. The formula for U-value is: 𝑈��=�𝑹 𝟏 𝒕𝒐𝒕𝒂𝒍 2.2.3 Determination of wall and roof numbers: Wall numbers and roof numbers are coefficients used to represent the thermal characteristics of walls and roofs, respectively. These are coefficients assigned to different types of walls based on their construction materials, thickness, and insulation. These coefficients take into account factors such as thermal conductivity, convective heat transfer coefficients, and radiative properties of the materials used in construction. 2.2.4 Determination of CLTD Values: To determine the Cooling Load Temperature Difference (CLTD) using wall and roof numbers, engineers typically refer to ASHRAE (American Society of Heating, Refrigerating and Air-Conditioning Engineers) tables designed for different latitudes. These tables provide standard values for wall and roof numbers based on empirical data and climatic conditions specific to different regions. Here's how the determination process generally works: 20 2.2.4.1 Identify Location and Climate Zone: The first step is to identify the location of the building and determine its climate zone based on factors such as latitude, altitude, and prevailing weather patterns. ASHRAE divides regions into different climate zones, each with its own set of standard design conditions. 2.2.4.2 Consult ASHRAE Tables: We refer to ASHRAE publications, such as the ASHRAE Handbook of Fundamentals, which contain tables providing standard wall and roof numbers for various climate zones. These tables typically include data for different latitudes, allowing for accurate estimation of cooling loads based on locationspecific conditions. 2.2.4.3 Select Wall and Roof Numbers: Based on the identified climate zone and latitude, we select the appropriate wall and roof numbers from the ASHRAE tables. These numbers represent the temperature differences across walls and roofs for given outdoor and indoor design conditions. 2.2.4.4 Calculate CLTD: Once the wall and roof numbers are determined, engineers use them along with other parameters such as outdoor design temperature, indoor design temperature, and solar heat gain to calculate the Cooling Load Temperature Difference (CLTD). The CLTD represents the temperature difference between the indoor and outdoor environments that the cooling system must overcome to maintain comfort conditions inside the building. 2.2.5 Calculation of Cooling Load: Once the CLTD values for each component are determined, the cooling load for each space or zone within the building can be calculated by summing the heat gains or losses associated with the respective components. Corrected CLTD = CLTDcorrected = CLTD + LM + (78 - tr) + (ta - 85) where, LM= Latitude Month Correction tr = room temperature, F ta= average outside temperature on a design day, F 𝐷𝑅 ta = to – 2 where, to= outside design dry bulb temperature, F DR = Daily Range 21 Cooling Load = U * A * CLTDcorrected where, A = Area of surface from which heat transfer occurs 2.2.6 Determination of Solar Heat Gain Factor/Coefficient: This represents the fraction of solar radiation admitted through a window, both directly transmitted and absorbed and subsequently released inward. Manufacturers provide SHGC values for different types of windows. Multiply the window area by the SHGC to determine the amount of solar heat gain through the windows. Heat Gain from Window = SHGC * Area of Window Note that solar heat gain factor differs with the direction of window facing. 2.2.7 Consideration of Internal Gains: In addition to the heat transfer through the building envelope, internal heat gains from occupants, lighting, equipment, and other sources must be accounted for in the cooling load calculation. Applications and Advantages The CLTD method offers several advantages over more complex cooling load calculation techniques, making it particularly suitable for practical applications: i. ii. iii. iv. Simplicity: The CLTD method provides a straightforward and easy-to-implement approach for estimating cooling loads, making it accessible to designers and engineers with varying levels of expertise. Versatility: CLTD values are available for a wide range of building components and configurations, allowing for the estimation of cooling loads in diverse architectural settings. Accuracy: Despite its simplicity, the CLTD method yields reasonably accurate results when applied correctly, especially for projects with typical building envelopes and operating conditions. Time and Cost Efficiency: By streamlining the calculation process, the CLTD method helps save time and resources during the design phase of HVAC projects, without sacrificing accuracy or reliability 22 3. Theoretical Considerations 3.1 Indoor Air Quality Indoor air quality (IAQ) refers to the condition of the air inside buildings and structures, encompassing various factors that affect occupant health, comfort, and well-being. It is influenced by the presence of pollutants such as dust, allergens, volatile organic compounds (VOCs), and gases, as well as factors like humidity levels, ventilation rates, and airflow patterns. Poor IAQ can lead to a range of health issues, including respiratory problems, allergies, fatigue, and headaches. Therefore, ensuring good IAQ is essential for creating a healthy and comfortable indoor environment. Here are some key factors to consider: i. Ventilation Rate: Proper ventilation is crucial for maintaining IAQ by diluting indoor pollutants with fresh outdoor air. The HVAC system should be designed to provide adequate ventilation rates based on occupancy, building size, and the type of activities conducted within the space. For this project we have considered ACH (Air Change per Hour) to be 1. ii. Filtration: High-efficiency air filters should be integrated into the HVAC system to capture airborne particles such as dust, pollen, mold spores, and other allergens. Filters are rated based on their Minimum Efficiency Reporting Value (MERV), with higher MERV ratings indicating better filtration capabilities. iii. Airborne Contaminant Control: In environments where there are specific airborne contaminants of concern, such as volatile organic compounds (VOCs), gases, or pathogens, specialized filtration or purification systems may be necessary. This could include activated carbon filters for VOC removal or UVGI (Ultraviolet Germicidal Irradiation) systems to disinfect air. iv. Humidity Control: Maintaining appropriate humidity levels is essential for IAQ. Excess humidity can lead to mold growth and microbial proliferation, while low humidity levels can cause discomfort and respiratory issues. The HVAC system should incorporate humidification and dehumidification components to regulate indoor humidity levels within the recommended range (usually between 30% to 60%). For our project, the desired relative humidity is taken to be 50%. v. Indoor Air Temperature: Indoor temperature is a critical factor for occupant comfort and well-being, impacting productivity and health. Effective HVAC systems regulate indoor temperatures, providing warmth in cold weather and cooling during hot seasons. Optimal temperature control enhances comfort, reduces energy costs, and promotes a healthier indoor environment. Advanced temperature monitoring and control technologies help maintain consistent 23 temperatures, ensuring a pleasant atmosphere for occupants year-round. For this project, the desired DBT is considered to be 71.6 oF. 3.2Outdoor Air Quality Outdoor air quality refers to the condition of air outside our air-conditioned space or we can also say that the out-door air quality refers to the condition of suction air. The outdoor air quality of Dharan, sourced from the Office of Hydrology and Meteorology (Eastern Regional Climate Office), Dharan, reflects a complex interplay of natural and anthropogenic factors. Dharan, located in eastern Nepal, experiences varying air quality influenced by factors such as industrial activities, vehicular emissions, biomass burning, and geographical features. Considerations for the outside air quality is given below: i. Maximum Outdoor Temperature: As per past three years data provided by Office of Hydrology and Meteorology (Eastern Regional Climate Office), Dharan, the maximum temperature was 39.3 oC on 06/07/2023 . This temperature is taken as the outside design dry bulb temperature (to). ii. Daily Range: Daily range refers to difference between maximum outdoor temperature and minimum outdoor temperature in a given day. We have taken minimum temperature of 06/07/2023 because the maximum temperature of three years occurred on this day. The minimum temperature that day was 26.8 oC, which makes the daily range 12.5. iii. Relative Humidity: For the sake of calculations, we have considered relative humidity as 70%. 3.3 Bypass Factor Bypass factor is a ratio that represents the portion of air which passes through the conditioning apparatus completely unaltered. It is the inability of a coil to cool or heat the air to its temperature. The bypass factor is calculated as the difference between the evaporator coil temperature and outlet air temperature as compared to the inlet. A coil with low bypass factor has better performance. The bypass factor is represented by 𝐵𝑃𝐹 = 𝑇𝑖𝑛𝑡 − 𝑇𝑓 𝑇𝑖𝑛𝑡 − 𝑇𝑖 Or 𝐵𝑦𝑝𝑎𝑠𝑠�𝐹𝑎𝑐𝑡𝑜𝑟 = 𝐼𝑛𝑡𝑒𝑟𝑚𝑒𝑑𝑖𝑎𝑡𝑒�𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 − 𝐹𝑖𝑛𝑎𝑙�𝑇𝑒𝑚𝑝𝑟𝑒𝑎𝑡𝑢𝑟𝑒 𝐼𝑛𝑡𝑒𝑟𝑚𝑒𝑑𝑖𝑎𝑡𝑒�𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 − 𝐼𝑛𝑖𝑡𝑖𝑎𝑙�𝑇𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒 24 Here, the intermediate temperature refers to the coil surface temperature. We have considered the bypass factor as 0.3 as it is the industry standard for various air handling units, and it is generally used by HVAC engineers when sufficient data about the evaporator coil isn’t known. 3.4 Room Sensible heat. Sensible heat is the heat energy which is responsible for changing the air temperature in room. The factors that are responsible for the sensible heat are as follows: 3.4.1 Solar gain –glass Glass solar gain is the amount of solar radiation that enters a building through it glass. Here, the glass is ordinary type, transparent and no coating or shading is there. So, the transmission coefficient U is taken as 1. 3.4.2 Solar and transmission gain through wall and roofs The wall and the roof, which is directly in contact with the sunlight, is responsible for the sensible heat. All the parameters for the CLTD is taken for 24° N latitude for the time ranging from the 8:00 AM to 3:00 PM. 3.4.3 Transmission gain Transmission gain is small in context of this building, so it is neglected. 3.4.4 Infiltration and by-passed air Infiltration: Infiltration refers to the Leakage of outdoor air into the building through gaps. The infiltration is considered to be 0 to 10% of air change per minute of room which contributes to the sensible heat. Outside air: According to the ventilation standard, the fresh air introduced in the room, it's about 5 CFM per person and 0.33 CFM per square feet of room area, which increases the sensible heat, the Fresh air in the room is introduced through AHU. 3.4.5 Internal heat The sources of internal load contributing to the sensible heat are as follows: People: The sensible heat raise per person is taken to be 285 BTU per hour per person, which is taken from the data book at 70 Fahrenheit indoor temperature. Lighting: Lighting also contribute to the increase in the sensible heat. For lighting it is taken as 1watt/ square fit. Equipment: There is no standard to know the equipment load for causing the sensible heat. It is calculated on the basis of number of people and according to the purpose of the room. 3.5 ROOM LATENT HEAT Latent heat is the heat energy that is responsible for changing the moisture contain in the room. 25 1)People: The Latent heat value for the people is taken as 165 BTU per hour per person from the data table at 70 Fahrenheit indoor temperature. 2)Infiltration and outside air: The infiltration an outside air also increases in the latent heat. The humidity ratio for the infiltration and outside air is taken as 165 grain per pound. 26 4. Methodology 4.1 Site selection The new about to be completed Dharan bus terminal was selected which is located at 26.79oN latitude was selected for our project. The Dharan bus terminal is of 3 floors i.e. underground, ground and first floor. Cooling load and duct designing of only first floor was to be calculated. 4.2 Data collection step 1: The hard copy of map of Dharan bus terminal with dimensions, climate data, humidity data of Dharan was collected. The map then was drawn in the AutoCAD 2023 (student version) software as given below: Figure 11. First Floor plan step 2: All rooms were numbered and the room which needs to be conditioned were highlighted. The area of highlighted room was converted into ft2. 27 Wall facing West East North South Area ft Area ft Area ft Area ft Area Room Number 51.11496 549.997 1 47.3075 509.0287 45.77588 492.5485 0 2 24.12683 259.6046 0 8.59155 92.44508 3 0 0 0 4 0 0 0 5 0 0 0 6 0 0 0 7 0 0 0 8 0 0 0 9 0 0 0 10 0 0 0 11 0 0 17.21993 185.2864 12 0 0 13 13.8365 148.8807 0 0 10.40287 111.9349 14 13.81757 148.6771 0 0 24.22947 260.7091 0 15 0 0 0 0 16 0 0 0 0 17 0 0 13.19312 141.9579 0 18 0 0 11.7316 126.232 0 19 0 0 9.73328 104.7301 0 20 0 0 0 0 21 0 0 0 0 22 0 0 0 0 23 0 0 0 0 24 0 0 0 0 25 0 0 0 0 26 0 0 0 0 27 0 0 8.588375 92.41092 0 28 0 0 12.74064 137.0893 0 29 0 0 13.7922 148.4041 0 30 0 0 12.9159 138.9751 0 31 0 0 13.7922 148.4041 0 32 0 0 12.9159 138.9751 0 33 0 0 13.7922 148.4041 0 34 0 0 12.74064 137.0893 0 35 0 0 13.7922 148.4041 0 36 0 0 12.21486 131.4319 0 37 0 0 13.7922 148.4041 0 38 0 0 12.74064 137.0893 0 39 0 0 29.88945 321.6105 18.45818 198.61 40 Area Glass window facing North Area ft East ft 5.2578 56.57393 5.60832 60.34552 0 0 0 0 3.5052 37.71595 5.78358 62.23132 0 0 0 0 0 0 0 2.10312 22.62957 3.15468 33.94436 2.10312 22.62957 2.97942 32.05856 2.10312 22.62957 2.97942 32.05856 2.10312 22.62957 3.15468 33.94436 2.10312 22.62957 3.68046 39.60175 2.10312 22.62957 3.15468 33.94436 8.41248 90.51828 Roof West Area ft Area 232.5 19.2786 207.4377 54.51 14.0208 150.8638 0 20.08125 0 23.1 0 17.675 0 0 17.0205 8.442 0 24.745 0 0 20.8425 20.3 0 0 18.375975 0 7.11165 0 22.276008 0 15.107838 0 34.933876 0 12.10774 0 13.0375 0 25.53495 0 29.49045 15.99 0 0 22.907394 0 21.40155 0 17.148744 0 33.028866 0 20.47329 0 19.9404 0 10.444644 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 0 15.630625 69.225 0 ft 2501.7 586.5276 216.07425 248.556 190.183 183.14058 90.83592 266.2562 224.2653 218.428 197.725491 76.521354 239.6898461 162.5603369 375.8885058 130.2792824 140.2835 274.756062 317.317242 172.0524 246.4835594 230.280678 184.5204854 355.3905982 220.2926004 214.558704 112.3843694 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 168.185525 28 South ft 0 3.32994 35.83015 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 0 75.4319 7.0104 Table 1. Area conversion 4.3 U value calculations 𝑅= 1 1 𝐿 + + ℎ0 ℎ𝑖 𝑘 Where, R= thermal resistance h0=4.613, Convective heat transfer coefficient on the outside surface hi=2.134, Convective heat transfer coefficient on the inside surface L= width of a material in feet k= thermal conductivity of a material 1 𝑈=𝑅 For wall, It was observed that the dimension of brick was 10 inch and plaster(light concrete) was 2 inch. K value of brick and plaster are 0.42 and 0.1 respectively. Now we find equivalent R for wall 𝑅= 1 4.613 + 1 2.134 +( 0.8333 0.42 + 0.167 0.1 ) ∴ 𝑅 = 4.336 𝑈= 1 = 0.2306 4.336 For roof, The dimension of roof was 5-inch, material was heavy concrete and k value of concrete is 0.1 𝑅= 1 1 0.4167 + + 4.613 2.134 0.1 ∴ 𝑅 = 4.8517 29 𝑈= 1 = 0.206 4.8517 4.4 Cooling load The cooling load between 8am-4pm is calculated here. Cooling load Q=U*A*∇𝑇 Where, A= area of a room in ft2 ∇𝑇(𝐶𝐿𝑇𝐷)=corrected temperature difference For corrected temperature difference from glass 4.4.1 For glass, For ordinary glass with no shading factor U value is 1. Table 2. Solar Heat Gain Through Glass CLTDE=1640F CLTDw=1450F CLTDN=140F CLTDS=300F 4.4.2 For walls (corrCLTD)north= CLTD + LM + (78 - tr) + (ta - 85) 30 = 19+1+(78-71.6) +(91.49-85) =32.890F (corrCLTD)south= 18-6+(78-71.6) +(91.49-85) = 24.89 0F (corrCLTD)east = 39+0+(78-71.6) +(91.49-85) = 51.890F (corrCLTD)west = 20+0+(78-71.6) +(91.49-85) = 32.890F Table 3. CLTD LM correction 31 Table 4. wall types, mass evenly distributed 32 Table 5. wall numbers 4.4.3 For roof corrCLTD=CLTD + (78 - tr) + (ta - 85) Our R value of roof falls between 0-5. So from table below our roof is of type 5 33 Table 7. Roof type Table 6. roof number. And maximum CLTD of roof type 5 from 10am-3pm is 74 from following table Now 34 corrCLTD=47 + (78 – 71.6) + (91.49 - 85) 0 = 86.89 F Using E20 Form sheet Cooling load with respect to room were calculated which is given below in tabular form Room Tonnes 3 2.1 13 3.24 14 2.58 15 4.2 16 1 17 1.33 18 2.18 20 2.71 28 1.82 29 2.06 30 1.85 31 1.99 32 1.85 33 1.99 34 1.85 34 2.02 36 1.04 37 2.11 38 1.85 39 2.02 total 41.79 Table 8. Room loads The total load that needed to be conditioned was found to be 41.79 tonnes of refrigeration. 4.5 System selection VAV system for a cooling load of 41.79 tonnes in a building aligns well with goals of energy conservation, comfort optimization, and operational flexibility, making it a suitable and beneficial choice. 4.6 Duct sizes To determine the duct size we determine CFM, velocity of air, head loss and fill these values in friction loss chart hence determine equivalent duct diameter CFM calculation: 35 𝐸𝑓𝑓𝑒𝑐𝑡𝑖𝑣𝑒�𝑟𝑜𝑜𝑚�𝑠𝑒𝑛𝑠𝑖𝑏𝑙𝑒�ℎ𝑒𝑎𝑡 CFM=(𝑖𝑛𝑑𝑜𝑜𝑟�𝑡𝑒𝑚𝑝𝑒𝑟𝑎𝑡𝑢𝑟𝑒−𝐴𝐷𝑃)∗1.08 Let’s take room 3 and determine the size of duct 12288 CFM=(71.6−46)∗1.08 ∴ 𝐶𝐹𝑀 = 634.95� ft3/m Head loss= 0.08 in water/100 ft duct Now using friction loss chart Figure 12. Friction Loss in inches of water per 100 feet of duct We have determined the size of duct using equal friction method Duct diameter=12.5in Velocity=750 fpm 36 Equivalent rectangular dimension=12*11 Table 9. Circular equivalent of Rectangular Duct We crossed checked these values using duct sizer software by McQuay which were similar to our result obtained from above chart. Figure 13. duct sizer by McQuay 37 Duct sizes of branch line with respect to room were calculated as above which is given below in tabular form: Room 3 13 14 15 16 17 18 20 28 29 30 31 32 33 34 34 36 37 38 39 total Head loss 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 0.08 CFM 640 440 1150 1600 300 320 510 1160 620 800 680 780 680 790 680 830 680 890 680 820 15050 CFM/Tonnes 304.7619048 135.8024691 445.7364341 380.952381 300 240.6015038 233.9449541 428.0442804 340.6593407 388.3495146 367.5675676 391.959799 367.5675676 396.9849246 367.5675676 410.8910891 653.8461538 421.8009479 367.5675676 405.9405941 Table 10. branch duct sizes note: duct diameter should be in even number for easier installation. 38 velocity(fpm ) branch duct size (circular) branch duct size (rectangular) 777 708 899 975 643 653 535 900 772 822 789 816 789 819 789 829 789 844 789 827 12.3 10.7 15.3 17.3 9.3 9.5 11.3 15.4 12.1 13.4 12.6 13.2 12.6 13.3 12.6 13.5 12.6 13.9 12.6 13.5 12 x 12 10 x 10 14 x 14 16 x 16 8 x 10 8 x 10 10 x 12 14 x14 8 x 16 14 x 12 12 x 12 12 x 12 12 x 12 12 x 12 12 x 12 12 x 14 12 x 12 12 x 14 12 x 12 12 x 14 5. CONCLUSION The cooling load calculation and duct design for the Dharan Bus Park Terminal have been carefully analysed and created to ensure optimal efficiency and comfort within the terminal space. The cooling load of the Dharan Bus Park terminal is about 41.79 Tonne. According to the obtained tonnage and design of terminal of bus park, central air conditioning system is selected. Equal friction method is used for design of duct. 39 References ASHRAE Handbook - Fundamentals. Atlanta: American Society of Heating, Refrigerating and Air-Conditioning Engineers, Inc., 2021. Carrier, W. H. "Simplified Design Procedure for Cooling and Heating Load Estimation." American Society of Heating, Refrigerating and Air-Conditioning Engineers Transactions 61 (1955): 91-104. McQuiston, Faye C., Parker, Jerald D., and Spitler, Jeffrey D. Heating, Ventilating, and Air Conditioning: Analysis and Design. Hoboken, NJ: John Wiley & Sons, Inc., 2017. C. K. Rajput, “A Text Book of Refrigeration and Air Conditioning”, S. K Kataria & Sons publication, New Delhi, India. S. C. Arora & S. Domkundwar, “A Course in Refrigeration and Air Conditioning”, Dhanpar Rai & Sons Publication, New Delhi, India. Andrew D. Althouse, Carl H. Thrnouist, and Alfred F. Bracciano, “Modern Refrigeration and Air Conditioning”, Galgotia Publication, New Delhi, India. Carrier Air Conditioning Company, “Handbook of Air Conditioning System Design”. C. P. Arora, “Refrigeration and Air Conditioning”, Tata McGraw Hill, India., 40 Appendices Appendix A: Climate Data Time 06/07/2023 05/12/2023 05/10/2023 06/08/2023 05/11/2023 05/09/2023 06/04/2023 03/17/2022 05/14/2023 06/03/2023 06/06/2023 05/13/2023 03/18/2022 05/08/2023 06/02/2023 04/26/2021 05/24/2021 04/15/2023 05/31/2023 06/01/2023 06/05/2023 06/11/2023 04/17/2023 03/19/2022 04/11/2021 Manual Daily Maximum Air Temperature 39.3 38.9 38.8 38.8 38.6 38.3 38.3 37.7 37.6 37.5 37.5 37.4 37.2 37.2 37.1 37 37 37 37 37 37 36.9 36.8 36.7 36.5 41 Manual Relative Humidity 60.59 59.45 61.14 62.1 72.48 60.67 63.23 95.67 51.83 73.53 59.47 63.01 99.21 66.71 58.27 82.93 73.65 74.11 62.12 61.75 71.55 97.26 76.33 98.51 66.31 Appendix B: Cooling Loads PROJECT U Watts INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FIRST FLOOR room no 3 216.07 10.42 2,250.59 Summer WB (°F) RH (%) 92.44 70.00 59.58 50.00 32.86 20.00 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 = = 10.00 71.30 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = 37.51 By Pass Factor (BF) Contact Factor (CF = 1 - BF) = 2,250.59 x CFM Infiltration CFM Ventilation 5.00 No 0.33 Sqft 2.00 216.07 1.00 x1/60 Btu/Hour Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) CFM Cu.ft x x x x 1.00 = x = 1.00 501.62 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 = = = = Swinging Revolving Doors (People) Open Doors Crack (feet) CFM cfm/door cfm/door cfm/door cfm/ft x x x x x x x x x x x x x x x x x x 32.89 51.89 24.89 32.89 634.95 L/s 0.76 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 = 298.43 = x x x x x x x x x Dehumidified Rise = TR 46.00 F F F F F F F F F 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 2.10 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) 86.89 0.00 0.00 0.00 0.00 0.00 0.00 2.00 = 701.14 0.00 0.00 0.00 0.00 0.00 1,968.92 0.00 3,869.39 x x x x x x x x x 0.00 Gr/Lb x 0.68 0.00 Gr/Lb x BFx0.68 2,808.00 Btu/Hour Per Person 825.00 3,633.00 181.65 3,814.65 16,103.17 TR 17.92 x x x x 1.08 1.08 CF x 1.08 1,868.54 Notes: 2.10 = = F F F F x x x 3.00 4.00 = = 25.40 T.Diff 169.30 169.30 165.00 F(TD) x 1.00 Indicated ADP (F) Selected ADP (F) x x x x 30.40 30.40 Btu/Hour Per Person W/SqFt x Watts x 0.00 800.80 x x 285.00 1.00 200.00 30.40 Gr/Lb 1,425.00 736.80 682.00 0.00 10,685.67 1,602.85 12,288.52 169.30 TMBH TKW TSMBH TSKW CF x 0.68 6,552.00 8,420.54 24,523.71 1 - 3% 735.71 25,259.42 25.26 7.33 14,157.06 4,105.55 2.10 2.5 - 5% 5-15% 3.41 3.41 x x x OUTSIDE AIR HEAT CFM x x x x 81.30 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Solar Gain - Glass Area Glass - N 35.83 SqFt Glass - NE SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight SqFt Solar & Transmission Gain - Walls & Roof Wall - N 92.45 SqFt Wall - NE SqFt Wall - E SqFt Wall - SE 0.00 SqFt Wall - S SqFt Wall - SW 0.00 SqFt Wall - W 259.60 SqFt Wall - NW SqFt Roof 216.07 SqFt Transmission Gain - Except Walls & Roof All Glass 0.00 SqFt Partition 0.00 SqFt Ceiling SqFt Floor 0.00 SqFt INFILTRATION AND BY PASSED AIR Infiltration CFM Outside Air 81.30 CFM Internal Heat People 5.00 Nos. Lighting 216.07 SqFt Equipments 1.00 Power kW/Hp Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT Infiltration 0.00 CFM Outside Air 81.30 CFM People 5.00 Nos. Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT Sensible CFM x 81.30 Factor Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 42 Btu/Hour Swinging Revolving Doors (People) Open Doors Crack (feet) Indicated ADP (F) Selected ADP (F) (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 2,497.57 x CFM Infiltration x x x x Dehumidified Rise = x = 1.00 1.00 15.00 239.69 1.00 x1/60 = = = = = = = = = = = = 29.12 30.00 0.62 0.00 0.00 0.00 0.00 0.00 41.63 75.00 79.10 0.30 0.70 HR (Gr/Lb) 229.50 60.20 169.30 cfm/door cfm/door cfm/door cfm/ft = 3.24 202.67 TR L/s CFM = 431.22 = TR = 3.24 = FIRST FLOOR room13 239.69 10.42 2,497.57 Summer WB (°F) RH (%) 92.44 70.00 59.58 50.00 32.86 20.00 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) CFM Cu.ft Watts 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) DB (°F) 102.00 71.60 30.40 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ x x x x x x x x x 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 4,275.00 1,226.01 4,774.00 0.00 11,792.81 1,768.92 13,561.74 2.00 By Pass Factor (BF) Contact Factor (CF = 1 - BF) x x x x x x x x x 0.30 0.50 0.00 0.00 0.00 0.00 Gr/Lb x 0.68 0.00 Gr/Lb x BFx0.68 5,322.13 Btu/Hour Per Person 2,475.00 7,797.13 2.5 - 5% 389.86 8,186.99 21,748.73 3.00 4.00 CFM Ventilation 5.00 No 0.33 Sqft F F F F F F F F F 0.27 U Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET 0.00 0.00 30.40 25.40 x x x x 1.08 0.00 1.08 1,517.80 CF x 1.08 3,541.53 1.00 F F F F T.Diff x x 285.00 1.50 70.00 x 3.41 3.41 169.30 169.30 165.00 F(TD) x Btu/Hour Per Person W/SqFt x Watts x 30.40 Gr/Lb TMBH TKW TSMBH TSKW 5-15% 169.30 CF x 0.68 12,418.31 15,959.84 37,708.57 1 - 3% 1,131.26 38,839.83 38.84 11.26 17,103.27 4,959.95 3.24 30.40 30.40 Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 0.00 0.00 x x x x x x x x x x x x x x x x x x 25.40 0.00 x x x x x x x x x OUTSIDE AIR HEAT CFM x x x x 154.10 PROJECT LOCATION CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Solar Gain - Glass Area Glass - N 0.00 SqFt Glass - NE SqFt Glass - E 0.00 SqFt Glass - SE SqFt Glass - S 0.00 SqFt Glass - SW SqFt Glass - W 0.00 SqFt Glass - NW SqFt Skylight SqFt Solar & Transmission Gain - Walls & Roof Wall - N SqFt Wall - NE SqFt Wall - E SqFt Wall - SE SqFt Wall - S 148.81 SqFt Wall - SW SqFt Wall - W SqFt Wall - NW SqFt Roof 239.69 SqFt Transmission Gain - Except Walls & Roof All Glass 0.00 SqFt Partition 0.00 SqFt Ceiling SqFt Floor 0.00 SqFt INFILTRATION AND BY PASSED AIR Infiltration 0.00 CFM Outside Air 154.10 CFM Internal Heat People 15.00 Nos. Lighting 239.69 SqFt Equipments 20.00 Power kW/Hp Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT Infiltration 0.00 CFM Outside Air 154.10 CFM People 15.00 Nos. Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT Sensible CFM x 154.10 Factor Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 43 PROJECT 24.89 32.89 30.40 25.40 Btu/Hour Watts FIRST FLOOR room no 14 162.56 10.42 1,693.22 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 15.00 53.64 = x = 1.00 = = CFM Ventilation No 5.00 Sqft 0.33 1,693.22 x CFM Infiltration 28.22 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 9,277.48 0.00 0.00 0.00 0.00 0.00 0.00 3.00 162.56 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 x x x x x x x x x = = = = 1.00 cfm/door cfm/door cfm/door cfm/ft x x x x 0.85 Swinging Revolving Doors (People) Open Doors (feet) Crack = 49.00 0.00 0.00 1,339.34 0.00 854.52 0.00 0.00 0.00 2,911.14 = = 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 Dehumidified Rise = = = 2.58 2.58 538.76 TR TR L/s CFM Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = 1,146.30 Indicated ADP (F) Selected ADP (F) F F F F F F F F F 0.00 0.00 0.00 0.00 0.00 0.00 15.82 0.00 5-15% 2.00 3.00 4.00 = x x x x U Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET x x x OUTSIDE AIR HEAT x CFM TMBH TKW TSMBH TSKW 1.00 F F F F Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 32.89 86.89 x x x x x x x x x x x x x x x x x x 25.40 51.89 x x x x 0.00 676.12 T.Diff 855.00 554.33 562.65 0.00 17,030.57 2,554.59 19,585.16 1.08 1.08 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,370.81 x Gr/Lb 825.00 Btu/Hour Per Person 3,195.81 2.5 - 5% 159.79 3,355.60 22,940.76 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,577.62 x x x x 285.00 1.00 55.00 x 68.64 3.41 3.41 x x 169.30 169.30 165.00 F(TD) x x 30.40 Gr/Lb Sensible CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass SqFt Glass - N SqFt Glass - NE 56.57 SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight Solar & Transmission Gain - Walls & Roof SqFt 0.00 Wall - N SqFt Wall - NE 111.93 SqFt Wall - E SqFt 0.00 Wall - SE 148.88 SqFt Wall - S SqFt 0.00 Wall - SW SqFt 0.00 Wall - W SqFt Wall - NW 162.56 SqFt Roof Transmission Gain - Except Walls & Roof SqFt 0.00 All Glass SqFt 0.00 Partition SqFt Ceiling SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR CFM Infiltration 68.64 CFM Outside Air Internal Heat Nos. 3.00 People 162.56 SqFt Lighting 3.00 Equipments kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT CFM 0.00 Infiltration 68.64 CFM Outside Air Nos. 5.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT 169.30 CFM x 68.64 Factor CF x 0.68 5,531.90 7,109.52 30,050.28 901.51 1 - 3% 30,951.79 30.95 8.98 21,162.78 6,137.21 2.58 Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 44 PROJECT CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 164.00 30.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 15 375.89 10.42 3,915.25 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 65.25 = x = 1.00 10.00 124.04 CFM Ventilation No 5.00 Sqft 0.33 3,915.25 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM 1.00 = 0.00 0.00 9,896.74 0.00 0.00 0.00 0.00 0.00 0.00 x x x x 2.00 375.89 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 Swinging Revolving Doors (People) Open Doors (feet) Crack 0.00 0.00 0.00 0.00 0.00 x x x x x x x x x 32.89 51.89 24.89 32.89 = = = = 0.00 0.00 3,119.61 0.00 0.00 0.00 0.00 0.00 6,731.42 Dehumidified Rise = = = 4.20 4.20 751.97 TR TR L/s CFM cfm/door cfm/door cfm/door cfm/ft 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = 1,599.93 0.81 0.00 0.00 0.00 0.00 0.00 0.00 = x x x x x x x x x 0.00 25.40 48.00 F F F F F F F F F x x x x 214.24 1.08 1.08 1,320.27 = = F F F F x x 5-15% Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) T.Diff 570.00 1,281.78 1,687.95 0.00 24,822.02 3,723.30 28,545.33 2.00 Indicated ADP (F) Selected ADP (F) 30.40 30.40 751.24 0.68 x Gr/Lb BFx0.68 4,629.50 x Gr/Lb 825.00 Btu/Hour Per Person 6,205.74 2.5 - 5% 310.29 6,516.03 35,061.36 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 3,080.63 16.52 285.00 1.00 165.00 x 3.00 4.00 = 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 10,802.18 13,882.81 48,944.17 1 - 3% 1,468.33 50,412.49 50.41 14.62 31,625.96 9,171.53 4.20 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor 134.04 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 60.35 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt 0.00 Wall - N x SqFt Wall - NE x 260.71 SqFt Wall - E x SqFt 0.00 Wall - SE x SqFt 0.00 Wall - S x SqFt 0.00 Wall - SW x SqFt 0.00 Wall - W x SqFt Wall - NW x 375.89 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 6.53 Infiltration x 134.04 CFM Outside Air Internal Heat x Nos. 2.00 People x 375.89 SqFt Lighting 3.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 6.53 Infiltration x 134.04 CFM Outside Air x Nos. 5.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 134.04 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 45 PROJECT Btu/Hour F F F F F F F F F F F F F x x x x x x x x x x x x x x x x x x x x x x 0.00 0.00 0.00 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 2,333.05 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 U Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET 24.89 32.89 30.40 25.40 T.Diff 0.00 423.46 1.08 1.08 3.41 3.41 5-15% 0.00 444.25 1,687.95 0.00 4,888.70 733.31 5,622.01 30.40 x x CF x 1.08 988.06 169.30 Gr/Lb TMBH TKW TSMBH TSKW CF x 0.68 3,464.62 4,452.68 11,633.77 349.01 1 - 3% 11,982.79 11.98 3.48 6,610.07 1,916.92 1.00 F(TD) 0.00 0.68 x 169.30 Gr/Lb BFx0.68 1,484.84 x 169.30 Gr/Lb 0.00 165.00 Btu/Hour Per Person 1,484.84 74.24 2.5 - 5% 1,559.08 7,181.09 285.00 Btu/Hour Per Person x 1.00 W/SqFt x 165.00 Watts x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 86.89 32.89 x x x x x x x x x 25.40 x x x x x x x x x x x x x 30.40 30.40 51.89 x x x x x OUTSIDE AIR HEAT x CFM x x x 42.99 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass SqFt Glass - N SqFt Glass - NE 0.00 SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight Solar & Transmission Gain - Walls & Roof 0.00 SqFt Wall - N SqFt Wall - NE 0.00 SqFt Wall - E 0.00 SqFt Wall - SE 0.00 SqFt Wall - S 0.00 SqFt Wall - SW 0.00 SqFt Wall - W SqFt Wall - NW 130.28 SqFt Roof Transmission Gain - Except Walls & Roof 0.00 SqFt All Glass 0.00 SqFt Partition SqFt Ceiling 0.00 SqFt Floor INFILTRATION AND BY PASSED AIR 0.00 CFM Infiltration 42.99 CFM Outside Air Internal Heat 0.00 Nos. People 130.28 SqFt Lighting 3.00 Equipments kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT 0.00 CFM Infiltration 42.99 CFM Outside Air 0.00 Nos. People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT Sensible CFM x 42.99 Factor Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 Watts 1.00 2.00 3.00 4.00 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FIRST FLOOR room no 16 130.28 10.42 1,356.99 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 = = 0.00 42.99 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = 22.62 By Pass Factor (BF) Contact Factor (CF = 1 - BF) = CFM Ventilation No 5.00 Sqft 0.33 0.00 130.28 1.00 x1/60 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = x = 1.00 0.78 1,356.99 x CFM Infiltration = = = = 46.50 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 17.57 1.00 cfm/door cfm/door cfm/door cfm/ft = = x x x x Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) = Dehumidified Rise 1.00 139.25 TR L/s CFM = 296.28 = TR = 1.00 = Indicated ADP (F) Selected ADP (F) (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 46 PROJECT 56.29 CFM x Btu/Hour F F F F F F F F F x x x x x x x x x x x x x x x x x x x x x x 1.08 1.08 0.00 0.00 0.00 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 79.96 554.47 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 2,512.20 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 U Q= U*A*ΔT F F F F x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 32.89 51.89 24.89 32.89 86.89 30.40 25.40 25.40 T.Diff 3.41 3.41 5-15% 570.00 478.37 1,909.60 0.00 6,104.59 915.69 7,020.28 169.30 Gr/Lb F(TD) x x CF x 1.08 1,293.76 TMBH TKW TSMBH TSKW CF x 0.68 4,536.54 5,830.31 15,532.92 1 - 3% 465.99 15,998.90 16.00 4.64 8,314.04 2,411.07 1.33 30.40 169.30 Gr/Lb x 0.68 280.37 169.30 Gr/Lb x BFx0.68 1,944.23 165.00 Btu/Hour Per Person 330.00 2,554.60 2.5 - 5% 127.73 2,682.33 9,702.61 285.00 Btu/Hour Per Person 1.00 W/SqFt x 70.00 Watts x 30.40 30.40 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Solar Gain - Glass Area Glass - N SqFt x Glass - NE SqFt x Glass - E SqFt x Glass - SE SqFt x Glass - S SqFt x Glass - SW SqFt x Glass - W SqFt x Glass - NW SqFt x Skylight SqFt x Solar & Transmission Gain - Walls & Roof Wall - N SqFt x Wall - NE SqFt x Wall - E 0.00 SqFt x Wall - SE SqFt x Wall - S SqFt x Wall - SW SqFt x Wall - W SqFt x Wall - NW SqFt x Roof 140.28 SqFt x Transmission Gain - Except Walls & Roof All Glass 0.00 SqFt x Partition 0.00 SqFt x Ceiling SqFt x Floor 0.00 SqFt x INFILTRATION AND BY PASSED AIR Infiltration 2.44 CFM x Outside Air 56.29 CFM x Internal Heat People 2.00 Nos. x Lighting 140.28 SqFt x Equipments 8.00 Power kW/Hp x Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT Infiltration 2.44 CFM x Outside Air 56.29 CFM x People 2.00 Nos. x Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT 56.29 CFM x Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 Watts 1.00 2.00 3.00 4.00 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 FIRST FLOOR room no 17 140.28 10.42 1,461.19 Summer WB (°F) RH (%) 92.44 70.00 59.58 50.00 32.86 20.00 = = 10.00 46.29 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = 24.35 By Pass Factor (BF) Contact Factor (CF = 1 - BF) = CFM Ventilation 5.00 No 0.33 Sqft 2.00 140.28 1.00 x1/60 = x = 1.00 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors Crack (feet) 1,461.19 x CFM Infiltration = = = = 0.72 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) CFM Cu.ft cfm/door cfm/door cfm/door cfm/ft = 42.00 1.00 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) = = x x x x Indicated ADP (F) Selected ADP (F) 20.72 Dehumidified Rise = 1.33 147.45 TR TR L/s CFM = 1.33 313.72 = = = (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 47 PROJECT CFM x DHARAN BUS STATION DHARAN,NEPAL Btu/Hour Q= U*A*ΔT F F F F F F F F F F F F F x x x x x x x x x x x x x x x x x x x x x x x x 1.08 1.08 0.00 0.00 0.00 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 0.00 1,698.63 0.00 0.00 0.00 0.00 0.00 4,920.34 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 Sun Gain or Temp. Diff. T.Diff 855.00 936.92 187.55 0.00 9,589.99 1,438.50 11,028.49 U 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 3,476.86 x Gr/Lb 330.00 Btu/Hour Per Person 3,806.86 2.5 - 5% 190.34 3,997.21 15,025.70 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 2,313.63 ΔT 285.00 1.00 55.00 x 25.40 30.40 25.40 86.89 32.89 24.89 51.89 32.89 145.00 30.00 164.00 169.30 169.30 165.00 F(TD) x 5-15% TMBH TKW TSMBH TSKW 0.00 991.55 30.40 Gr/Lb 3.41 3.41 169.30 CF x 0.68 8,112.68 10,426.31 25,452.00 763.56 1 - 3% 26,215.56 26.22 7.60 13,342.12 3,869.21 2.18 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor 100.67 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 141.96 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 274.76 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 100.67 CFM Outside Air Internal Heat x Nos. 3.00 People x 274.76 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 100.67 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 100.67 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 Watts 1.00 2.00 3.00 4.00 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 FIRST FLOOR room no 18 274.76 10.42 2,861.86 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 10.00 90.67 DB (°F) 102.00 71.60 30.40 = = 47.70 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) = = x = 1.00 2.00 274.76 1.00 x1/60 CFM Ventilation No 5.00 Sqft 0.33 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack 2,861.86 x CFM Infiltration = = = = 0.73 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM cfm/door cfm/door cfm/door cfm/ft = 43.00 1.00 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) = = x x x x Indicated ADP (F) Selected ADP (F) 20.02 Dehumidified Rise = 2.18 239.73 TR TR L/s CFM = 2.18 510.07 = = = (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 48 51.89 24.89 32.89 30.40 25.40 Btu/Hour Q= U*A*ΔT Watts Swinging Revolving Doors (People) Open Doors (feet) Crack Indicated ADP (F) Selected ADP (F) (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 1,792.79 x CFM Infiltration x x x x Dehumidified Rise = x = 1.00 1.00 4.00 172.05 1.00 x1/60 = = = = = = = = = = 15.82 49.00 0.84 0.00 0.00 0.00 0.00 0.00 29.88 20.00 56.78 0.30 0.70 HR (Gr/Lb) 229.50 60.20 169.30 cfm/door cfm/door cfm/door cfm/ft = = = = 2.71 2.71 543.79 TR TR L/s CFM = = 1,156.99 = FIRST FLOOR Room 20 172.05 10.42 1,792.79 Summer RH (%) WB (°F) 70.00 92.44 50.00 59.58 20.00 32.86 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY DB (°F) 102.00 71.60 30.40 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ 0.00 0.00 10,205.94 0.00 0.00 0.00 0.00 0.00 0.00 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) U 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 1,253.18 0.00 0.00 0.00 0.00 0.00 3,081.12 By Pass Factor (BF) Contact Factor (CF = 1 - BF) x x x x x x x x x 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 5-15% 2.00 3.00 4.00 CFM Ventilation No 5.00 Sqft 0.33 x x x x x x x x x 0.30 0.50 0.00 0.00 0.00 0.00 Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 30.00 164.00 145.00 32.89 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET x x x x x x x x x F F F F F F F F F 0.27 86.89 x x x x x x x x x x x x x F F F F 25.40 T.Diff x x x x x x x OUTSIDE AIR HEAT x CFM TMBH TKW TSMBH TSKW 1.00 98.10 756.23 1,140.00 586.70 68.20 0.00 17,189.46 2,578.42 19,767.88 1.08 1.08 30.40 30.40 343.99 0.68 x Gr/Lb BFx0.68 2,651.69 x Gr/Lb 660.00 Btu/Hour Per Person 3,655.68 2.5 - 5% 182.78 3,838.46 23,606.35 x x x x CF x 1.08 1,764.53 76.78 3.41 3.41 285.00 1.00 20.00 x Sensible Btu/Hour Per Person x W/SqFt x Watts x x 169.30 169.30 165.00 F(TD) x x 30.40 Gr/Lb x CFM Factor 76.78 PROJECT LOCATION CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass SqFt Glass - N SqFt Glass - NE 62.23 SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight Solar & Transmission Gain - Walls & Roof SqFt Wall - N SqFt Wall - NE 104.73 SqFt Wall - E SqFt Wall - SE SqFt Wall - S SqFt Wall - SW SqFt Wall - W SqFt Wall - NW 172.05 SqFt Roof Transmission Gain - Except Walls & Roof SqFt 0.00 All Glass SqFt 0.00 Partition SqFt Ceiling SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR CFM 2.99 Infiltration 76.78 CFM Outside Air Internal Heat Nos. 4.00 People 172.05 SqFt Lighting 1.00 Equipments kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT CFM 2.99 Infiltration 76.78 CFM Outside Air Nos. 4.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT 169.30 CF x 0.68 6,187.27 7,951.80 31,558.15 946.74 1 - 3% 32,504.89 32.50 9.43 21,532.41 6,244.40 2.71 Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 49 PROJECT Btu/Hour Watts INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 FIRST FLOOR room no 28 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 = = 10.00 55.50 DB (°F) 102.00 71.60 30.40 = = 29.20 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 2.00 168.19 1.00 x1/60 1,751.82 x CFM Infiltration x x x x CFM Ventilation No 5.00 Sqft 0.33 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack 1.00 = x = 1.00 0.00 0.00 3,711.24 0.00 0.00 0.00 0.00 0.00 0.00 = = = = 0.79 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 cfm/door cfm/door cfm/door cfm/ft = x x x x x x x x x U Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET 24.89 32.89 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x Dehumidified Rise = = 1.82 287.75 TR TR L/s = 1.82 CFM 0.00 0.00 1,105.76 0.00 0.00 0.00 0.00 0.00 3,011.87 F F F F F F F F F (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 612.23 47.00 570.00 573.51 187.55 0.00 9,900.95 1,485.14 11,386.10 2.00 3.00 4.00 = 17.22 0.00 0.00 0.00 0.00 0.00 0.00 = = 0.00 = x x x x 336.13 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,928.37 2.5 - 5% 146.42 3,074.79 14,460.89 1.00 Indicated ADP (F) Selected ADP (F) F F F F CF x 1.08 1,505.38 30.40 25.40 T.Diff 285.00 1.00 55.00 x 95.86 645.16 1.08 1.08 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 5-15% 169.30 CF x 0.68 5,278.56 6,783.94 21,244.83 637.34 1 - 3% 21,882.17 21.88 6.35 12,891.47 3,738.53 1.82 Btu/Hour Per Person x W/SqFt x Watts x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 86.89 32.89 x x x x x x x x x 25.40 x x x x x x x x x x x x x 30.40 30.40 51.89 x x x x x OUTSIDE AIR HEAT x CFM x x x 65.50 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass SqFt Glass - N SqFt Glass - NE 22.63 SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight Solar & Transmission Gain - Walls & Roof SqFt Wall - N SqFt Wall - NE 92.41 SqFt Wall - E SqFt Wall - SE SqFt Wall - S SqFt Wall - SW SqFt Wall - W SqFt Wall - NW 168.19 SqFt Roof Transmission Gain - Except Walls & Roof SqFt 0.00 All Glass SqFt 0.00 Partition SqFt Ceiling SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR CFM 2.92 Infiltration 65.50 CFM Outside Air Internal Heat Nos. 2.00 People 168.19 SqFt Lighting 1.00 Equipments kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT CFM 2.92 Infiltration 65.50 CFM Outside Air Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT Sensible CFM x 65.50 Factor Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 50 PROJECT 65.50 CFM x U Btu/Hour Q= U*A*ΔT Watts FIRST FLOOR room no 29 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 = = CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration 29.20 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 5,566.82 0.00 0.00 0.00 0.00 0.00 0.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 x x x x x x x x x = = = = 1.00 cfm/door cfm/door cfm/door cfm/ft x x x x 0.82 Swinging Revolving Doors (People) Open Doors (feet) Crack = 48.00 0.00 0.00 1,640.38 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = 2.06 372.35 TR L/s CFM = TR = 2.06 792.24 = = 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x 0.00 0.00 0.00 0.00 0.00 0.00 2.00 Indicated ADP (F) Selected ADP (F) F F F F F F F F F 0.00 CF x 1.08 1,505.38 16.52 x x x x x 3.00 4.00 = F F F F Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 30.00 164.00 145.00 32.89 51.89 24.89 32.89 86.89 30.40 25.40 25.40 T.Diff 95.86 645.16 1.08 1.08 30.40 x 1.00 x x 3.41 3.41 5-15% 570.00 573.51 187.55 0.00 12,291.15 1,843.67 14,134.83 169.30 Gr/Lb TMBH TKW TSMBH TSKW CF x 0.68 5,278.56 6,783.94 23,993.56 719.81 1 - 3% 24,713.36 24.71 7.17 15,640.20 4,535.66 2.06 F(TD) 336.13 0.68 x 169.30 Gr/Lb BFx0.68 2,262.24 x 169.30 Gr/Lb 330.00 165.00 Btu/Hour Per Person 2,928.37 2.5 - 5% 146.42 3,074.79 17,209.62 285.00 Btu/Hour Per Person x 1.00 W/SqFt x 55.00 Watts 30.40 30.40 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 33.94 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 137.09 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x 0.00 SqFt All Glass x 0.00 SqFt Partition x SqFt Ceiling x 0.00 SqFt Floor INFILTRATION AND BY PASSED AIR x 2.92 CFM Infiltration x 65.50 CFM Outside Air Internal Heat x 2.00 Nos. People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x 2.92 CFM Infiltration x 65.50 CFM Outside Air x 2.00 Nos. People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 51 PROJECT 51.89 24.89 32.89 Btu/Hour Q= U*A*ΔT U Watts INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 FIRST FLOOR room no 30 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 92.44 70.00 59.58 50.00 32.86 20.00 = = 10.00 55.50 DB (°F) 102.00 71.60 30.40 = = 29.20 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 2.00 168.19 1.00 x1/60 1,751.82 x CFM Infiltration x x x x CFM Ventilation 5.00 No 0.33 Sqft CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) CFM Cu.ft Swinging Revolving Doors (People) Open Doors Crack (feet) 1.00 = x = 1.00 0.00 0.00 3,711.24 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 0.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 = = = = 0.82 x x x x x x x x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET x x x x x x x x x 32.89 cfm/door cfm/door cfm/door cfm/ft = 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x 86.89 Dehumidified Rise = = 1.85 1.85 317.34 TR TR L/s CFM = 675.18 0.00 0.00 1,775.78 0.00 0.00 0.00 0.00 0.00 3,011.87 F F F F F F F F F x x x x x x x x x 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = 48.00 0.00 0.00 0.00 0.00 0.00 0.00 16.52 0.00 25.40 5-15% 3.00 4.00 2.00 1.00 = = x x x x x x x x x x x TMBH TKW TSMBH TSKW 0.00 645.16 570.00 573.51 187.55 0.00 10,475.11 1,571.27 12,046.38 = F F F F 1.08 1.08 30.40 30.40 Gr/Lb x 0.68 0.00 Gr/Lb x BFx0.68 2,262.24 Btu/Hour Per Person 330.00 2,592.24 2.5 - 5% 129.61 2,721.85 14,768.23 Indicated ADP (F) Selected ADP (F) T.Diff x x x x CF x 1.08 1,505.38 OUTSIDE AIR HEAT CFM x 3.41 3.41 285.00 1.00 55.00 x 65.50 Btu/Hour Per Person W/SqFt x Watts x x x 169.30 169.30 165.00 F(TD) x x 30.40 Gr/Lb Sensible CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Solar Gain - Glass Area Glass - N SqFt Glass - NE SqFt Glass - E 22.63 SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight SqFt Solar & Transmission Gain - Walls & Roof Wall - N SqFt Wall - NE SqFt Wall - E 148.40 SqFt Wall - SE SqFt Wall - S SqFt Wall - SW SqFt Wall - W SqFt Wall - NW SqFt Roof 168.19 SqFt Transmission Gain - Except Walls & Roof All Glass 0.00 SqFt Partition 0.00 SqFt Ceiling SqFt Floor 0.00 SqFt INFILTRATION AND BY PASSED AIR Infiltration 0.00 CFM Outside Air 65.50 CFM Internal Heat People 2.00 Nos. Lighting 168.19 SqFt Equipments 1.00 Power kW/Hp Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT Infiltration 0.00 CFM Outside Air 65.50 CFM People 2.00 Nos. Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT 169.30 CFM x 65.50 Factor CF x 0.68 5,278.56 6,783.94 21,552.17 1 - 3% 646.57 22,198.73 22.20 6.44 13,551.75 3,930.01 1.85 Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 52 PROJECT 65.50 CFM x Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 31 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 5,257.51 0.00 0.00 0.00 0.00 0.00 0.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 x x x x x x x x x = = = = 1.00 cfm/door cfm/door cfm/door cfm/ft x x x x 0.83 Swinging Revolving Doors (People) Open Doors (feet) Crack = 48.00 0.00 0.00 1,662.95 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 1.99 1.99 360.76 TR TR L/s CFM = 767.58 = = 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x 2.00 Indicated ADP (F) Selected ADP (F) F F F F F F F F F 0.00 0.00 0.00 0.00 0.00 0.00 CF x 1.08 1,505.38 16.52 0.00 x 3.00 4.00 = x x x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 30.00 164.00 145.00 32.89 51.89 24.89 32.89 86.89 30.40 25.40 F F F F 1.08 1.08 0.00 645.16 x x 30.40 x 1.00 T.Diff 30.40 30.40 3.41 3.41 570.00 573.51 187.55 0.00 11,908.56 1,786.28 13,694.84 169.30 Gr/Lb TMBH TKW TSMBH TSKW CF x 0.68 5,278.56 6,783.94 23,200.64 696.02 1 - 3% 23,896.65 23.90 6.93 15,200.22 4,408.06 1.99 F(TD) 0.00 0.68 x 169.30 Gr/Lb BFx0.68 2,262.24 x 169.30 Gr/Lb 330.00 165.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 16,416.70 5-15% 285.00 Btu/Hour Per Person x 1.00 W/SqFt x 55.00 Watts 25.40 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 32.06 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 138.98 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x 0.00 SqFt All Glass x 0.00 SqFt Partition x SqFt Ceiling x 0.00 SqFt Floor INFILTRATION AND BY PASSED AIR x 0.00 CFM Infiltration x 65.50 CFM Outside Air Internal Heat x 2.00 Nos. People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x 0.00 CFM Infiltration x 65.50 CFM Outside Air x 2.00 Nos. People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 53 PROJECT Btu/Hour Watts INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 FIRST FLOOR room no 32 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 = = 10.00 55.50 DB (°F) 102.00 71.60 30.40 = = 29.20 FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 2.00 168.19 1.00 x1/60 1,751.82 x CFM Infiltration x x x x CFM Ventilation No 5.00 Sqft 0.33 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack 1.00 = x = 1.00 0.00 0.00 3,711.24 0.00 0.00 0.00 0.00 0.00 0.00 = = = = 0.82 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 cfm/door cfm/door cfm/door cfm/ft = x x x x x x x x x U Q= U*A*ΔT Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET 24.89 32.89 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x Dehumidified Rise = = 1.85 317.34 TR TR L/s = 1.85 CFM 0.00 0.00 1,775.78 0.00 0.00 0.00 0.00 0.00 3,011.87 F F F F F F F F F (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: 675.18 48.00 570.00 573.51 187.55 0.00 10,475.11 1,571.27 12,046.38 2.00 3.00 4.00 = 16.52 0.00 0.00 0.00 0.00 0.00 0.00 = = 0.00 = x x x x 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 14,768.23 1.00 Indicated ADP (F) Selected ADP (F) F F F F CF x 1.08 1,505.38 30.40 25.40 T.Diff 285.00 1.00 55.00 x 0.00 645.16 1.08 1.08 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 5-15% 169.30 CF x 0.68 5,278.56 6,783.94 21,552.17 646.57 1 - 3% 22,198.73 22.20 6.44 13,551.75 3,930.01 1.85 Btu/Hour Per Person x W/SqFt x Watts x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 164.00 30.00 145.00 86.89 32.89 x x x x x x x x x 25.40 x x x x x x x x x x x x x 30.40 30.40 51.89 x x x x x OUTSIDE AIR HEAT x CFM x x x 65.50 CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass SqFt Glass - N SqFt Glass - NE 22.63 SqFt Glass - E SqFt Glass - SE SqFt Glass - S SqFt Glass - SW SqFt Glass - W SqFt Glass - NW SqFt Skylight Solar & Transmission Gain - Walls & Roof SqFt Wall - N SqFt Wall - NE 148.40 SqFt Wall - E SqFt Wall - SE SqFt Wall - S SqFt Wall - SW SqFt Wall - W SqFt Wall - NW 168.19 SqFt Roof Transmission Gain - Except Walls & Roof SqFt 0.00 All Glass SqFt 0.00 Partition SqFt Ceiling SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR CFM 0.00 Infiltration 65.50 CFM Outside Air Internal Heat Nos. 2.00 People 168.19 SqFt Lighting 1.00 Equipments kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT CFM 0.00 Infiltration 65.50 CFM Outside Air Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT Sensible CFM x 65.50 Factor Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 54 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 30.00 164.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 33 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 5,257.51 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,662.95 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 1.99 1.99 368.57 TR TR L/s CFM = 784.19 0.83 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 48.50 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 187.55 0.00 11,908.56 1,786.28 13,694.84 2.00 16.17 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 16,416.70 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 55.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 23,200.64 696.02 1 - 3% 23,896.65 23.90 6.93 15,200.22 4,408.06 1.99 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 32.06 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 138.98 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 55 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 30.00 164.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 34 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 3,711.16 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,775.78 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 1.85 1.85 317.33 TR TR L/s CFM = 675.18 0.82 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 48.00 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 187.55 0.00 10,475.03 1,571.25 12,046.28 2.00 16.52 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 14,768.14 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 55.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 21,552.08 646.56 1 - 3% 22,198.64 22.20 6.44 13,551.66 3,929.98 1.85 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 22.63 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 148.40 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 56 PROJECT 65.50 CFM x U Btu/Hour Q= U*A*ΔT Watts FIRST FLOOR room no 35 168.19 10.42 1,751.82 Summer WB (°F) (%) RH 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 = = CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration 29.20 CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 5,566.82 0.00 0.00 0.00 0.00 0.00 0.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 0.00 0.00 0.00 0.00 0.00 x x x x x x x x x = = = = 1.00 cfm/door cfm/door cfm/door cfm/ft x x x x 0.84 Swinging Revolving Doors (People) Open Doors (feet) Crack = 49.00 0.00 0.00 1,640.38 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 2.02 2.02 385.80 TR TR L/s CFM = 820.84 = = 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) x x x x x x x x x 2.00 Indicated ADP (F) Selected ADP (F) F F F F F F F F F 0.00 0.00 0.00 0.00 0.00 0.00 CF x 1.08 1,505.38 15.82 0.00 x 3.00 4.00 = x x x x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 14.00 30.00 164.00 145.00 32.89 51.89 24.89 32.89 86.89 30.40 25.40 F F F F 1.08 1.08 0.00 645.16 x x 30.40 x 1.00 T.Diff 30.40 30.40 3.41 3.41 570.00 573.51 187.55 0.00 12,195.29 1,829.29 14,024.59 169.30 Gr/Lb TMBH TKW TSMBH TSKW CF x 0.68 5,278.56 6,783.94 23,530.38 705.91 1 - 3% 24,236.29 24.24 7.03 15,529.96 4,503.69 2.02 F(TD) 0.00 0.68 x 169.30 Gr/Lb BFx0.68 2,262.24 x 169.30 Gr/Lb 330.00 165.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 16,746.44 5-15% 285.00 Btu/Hour Per Person x 1.00 W/SqFt x 55.00 Watts 25.40 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 33.94 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 137.09 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x 0.00 SqFt All Glass x 0.00 SqFt Partition x SqFt Ceiling x 0.00 SqFt Floor INFILTRATION AND BY PASSED AIR x CFM Infiltration x 65.50 CFM Outside Air Internal Heat x 2.00 Nos. People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x 0.00 CFM Infiltration x 65.50 CFM Outside Air x 2.00 Nos. People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 57 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 30.00 164.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 36 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 3,652.12 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,775.78 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 1.84 1.84 315.55 TR TR L/s CFM = 671.37 0.81 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 48.00 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 187.55 0.00 10,415.99 1,562.40 11,978.39 2.00 16.52 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 14,700.24 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 55.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 21,484.18 644.53 1 - 3% 22,128.70 22.13 6.42 13,483.76 3,910.29 1.84 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 22.27 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 148.40 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 58 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 164.00 30.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 37 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 6,494.40 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,572.67 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 2.11 2.11 414.62 TR TR L/s CFM = 882.16 0.85 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 49.00 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 238.70 0.00 13,106.31 1,965.95 15,072.26 2.00 15.82 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 17,794.11 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 70.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 24,578.05 737.34 1 - 3% 25,315.40 25.32 7.34 16,577.64 4,807.51 2.11 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 39.60 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 131.43 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 59 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 30.00 164.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 38 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 3,711.24 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,775.78 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 1.85 1.85 317.34 TR TR L/s CFM = 675.18 0.82 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 48.00 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 187.55 0.00 10,475.11 1,571.27 12,046.38 2.00 16.52 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 14,768.23 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 55.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 21,552.17 646.57 1 - 3% 22,198.73 22.20 6.44 13,551.75 3,930.01 1.85 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 22.63 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 148.40 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 60 PROJECT 65.50 CFM x Sun Gain or Temp. Diff. DHARAN BUS STATION DHARAN,NEPAL ΔT 164.00 30.00 145.00 Btu/Hour Q= U*A*ΔT U Watts FIRST FLOOR room no 39 168.19 10.42 1,751.82 Summer WB (°F) RH (%) 70.00 92.44 50.00 59.58 20.00 32.86 HR (Gr/Lb) 229.50 60.20 169.30 0.30 0.70 DB (°F) 102.00 71.60 30.40 INPUT VALUES ARE TO BE GIVEN IN BLUE COLOR BOXES ONLY FLOOR SPACE REFERENCE AREA ( SqFt) (WxH) Falce Ceiling Height (Ft) Volume (CuFt) Estimate for Design Conditions Ambient(Out Side) Room (InDoor) Difference Δ = = By Pass Factor (BF) Contact Factor (CF = 1 - BF) 10.00 55.50 = x = 1.00 29.20 CFM Ventilation No 5.00 Sqft 0.33 1,751.82 x CFM Infiltration = = CFM Per Person CFM Per SqFt Air Change Per Hour (CFM) Cu.ft CFM = 0.00 0.00 5,566.82 0.00 0.00 0.00 0.00 0.00 0.00 1.00 2.00 168.19 1.00 x1/60 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 1.00 x x x x 0.00 0.00 0.00 0.00 0.00 Swinging Revolving Doors (People) Open Doors (feet) Crack = = = = x x x x x x x x x 32.89 51.89 24.89 32.89 cfm/door cfm/door cfm/door cfm/ft 0.00 0.00 1,640.38 0.00 0.00 0.00 0.00 0.00 3,011.87 Dehumidified Rise = = 2.02 2.02 385.80 TR TR L/s CFM = 820.84 0.84 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.23 0.21 86.89 30.40 25.40 (Room DB - ADP) x CF DEHUMIDIFIED AIR QUANTITY Effective Room Sensible Heat Dehumidified Rise x 1.08 TOTAL HEAT CAPACITY Grand Total Heat SENSIBLE HEAT CAPACITY Grand Sensible Heat 12,000.00 Notes: = = 0.00 0.00 0.00 0.00 0.00 0.00 49.00 x x x x x x x x x 0.00 25.40 = = F F F F F F F F F x x x x 1.08 1.08 Supply CFM from Machine Effective Room Sensible Heat Factor = Effective Room Sensible Heat/Eff Room Total Heat Apparatus Dew Point (ADP) F F F F x x 5-15% Indicated ADP (F) Selected ADP (F) T.Diff 570.00 573.51 187.55 0.00 12,195.29 1,829.29 14,024.59 2.00 15.82 30.40 30.40 0.00 0.68 x Gr/Lb BFx0.68 2,262.24 x Gr/Lb 330.00 Btu/Hour Per Person 2,592.24 2.5 - 5% 129.61 2,721.85 16,746.44 Btu/Hour Per Person x W/SqFt x Watts CF x 1.08 1,505.38 3.00 4.00 = 285.00 1.00 55.00 x 0.00 645.16 169.30 169.30 165.00 F(TD) x 3.41 3.41 30.40 Gr/Lb TMBH TKW TSMBH TSKW 1.00 169.30 CF x 0.68 5,278.56 6,783.94 23,530.38 705.91 1 - 3% 24,236.29 24.24 7.03 15,529.96 4,503.69 2.02 14.00 Factor (U) HVAC LOAD CALCULATION - E20 FORM SHEET Factor CLIENT CONSULTANT 126.00 Area or Item Quantity ROOM HEAT ROOM SENSIBLE HEAT Area Solar Gain - Glass x SqFt Glass - N x SqFt Glass - NE x 33.94 SqFt Glass - E x SqFt Glass - SE x SqFt Glass - S x SqFt Glass - SW x SqFt Glass - W x SqFt Glass - NW x SqFt Skylight Solar & Transmission Gain - Walls & Roof x SqFt Wall - N x SqFt Wall - NE x 137.09 SqFt Wall - E x SqFt Wall - SE x SqFt Wall - S x SqFt Wall - SW x SqFt Wall - W x SqFt Wall - NW x 168.19 SqFt Roof Transmission Gain - Except Walls & Roof x SqFt 0.00 All Glass x SqFt 0.00 Partition x SqFt Ceiling x SqFt 0.00 Floor INFILTRATION AND BY PASSED AIR x CFM 0.00 Infiltration x 65.50 CFM Outside Air Internal Heat x Nos. 2.00 People x 168.19 SqFt Lighting 1.00 Equipments x kW/Hp Power Sub Total Factor Effective Room Sensible Heat ROOM LATENT HEAT x CFM 0.00 Infiltration x 65.50 CFM Outside Air x Nos. 2.00 People Sub Total Factor Effective Room Latent Heat EFFECTIVE ROOM TOTAL HEAT OUTSIDE AIR HEAT x 65.50 CFM Sensible Latent OUTSIDE AIR TOTAL HEAT GRAND SUB-TOTAL HEAT GRAND TOTAL HEAT TONS=GRAND TOTAL HEAT/12000 61 62
