Heating Ventilating and Air Conditioning: Analysis and Design
Heating Ventilating and Air Conditioning: Analysis and Design
6th Edition
ISBN: 9780471470151
Author: Faye C. McQuiston, Jeffrey D. Spitler, Jerald D. Parker
Publisher: Wiley, John & Sons, Incorporated
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Chapter 3, Problem 3.27P

The design cooling load for a zone in a building is 250,000 Btu/hr (73 kW), of which 200,000 Btu/hr (59 kW is sensible cooling load. The space is to be maintained at 75 F (24 C) dry bulb temperature and 50 percent relative humidity. Locate the space condition line on Charts 1a and 1b and draw the condition line.

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Humid air flows in a duct at atmospheric pressure. The dry bulb   temperature and humidity ratio  are  80℉ and ω=0.011 (lbm water)/(lbm dry air) Add the point on the attached chart and complete the other properties of this humid air in the table below:
ASHRAE standard 55, Thermal Environmental Conditions for Human Occupancy, notes that for thermal comfort purposes, the indoor temperature should range from approximately 67ºF to 82°F (19.4ºC to 27.8ºC), and systems designed to control humidity must be able to maintain a dew-point temperature of 16.8°C (62.2°F). ASHRAE standard 62.1, Ventilation and Acceptable Indoor Air Quality, recommends that relative humidity in occupied spaces be controlled to less than 65% to reduce the likelihood of conditions that can lead to microbial growth. Determine the minimum allowable indoor temperature that will ensure a humidity control system designed according to ASHRAE standard 55 will also satisfy the humidity requirements of standard 62.1
Use the concept of evaporative cooling to explain how air’s relative humidity is measured using a sling psychrometer

Chapter 3 Solutions

Heating Ventilating and Air Conditioning: Analysis and Design

Ch. 3 - The environmental conditions in a room are to be...Ch. 3 - Air enters a cooling coil at the rate of 5000 cfm...Ch. 3 - Air flowing in a duct has dry and wet bulb...Ch. 3 - Air is humidified with the dry bulb temperature...Ch. 3 - Air at 38 C db and 20 C wb is humidified...Ch. 3 - Two thousand cfm (1.0 m3/s) of air at an initial...Ch. 3 - Air at 40 F (5 C) db and 35 F (2 C) wb is mixed...Ch. 3 - Rework Problem 3-25, using Chart 1a, with the...Ch. 3 - The design cooling load for a zone in a building...Ch. 3 - Assume that the air in Problem 3-22 is supplied to...Ch. 3 - The sensible heat loss from a space is 500,000...Ch. 3 - Air enters a refrigeration coil at 90 Fdb and 75...Ch. 3 - A building has a total heating load of 200,000...Ch. 3 - Reconsider Problem 3-36 for an elevation of 5000...Ch. 3 - The system of Problem 3-34 has a supply air fan...Ch. 3 - An evaporative cooling system is to be used to...Ch. 3 - A cooling system is being designed for use at high...Ch. 3 - Consider a space heating system designed as shown...Ch. 3 - A variable-air-volume VAV cooling system is a type...Ch. 3 - Rework Problem 3-43 for an elevation of 5000 feet...Ch. 3 - The design condition for a space is 77 F (25 C) db...Ch. 3 - Rework Problem 3-45 for an elevation of 5000 feet...Ch. 3 - It is necessary to cool and dehumidify air from 80...Ch. 3 - Conditions in one zone of a dual-duct conditioning...Ch. 3 - Rework Problem 3-48 for an elevation of 5000 ft...Ch. 3 - A water coil in Problem 3-48 cools return air to...Ch. 3 - A multizone air handler provides air to several...Ch. 3 - Under normal operating conditions a zone has a...Ch. 3 - An interior zone of a large building is designed...Ch. 3 - Outdoor air is mixed with room return air to...Ch. 3 - Consider an enclosed swimming pool. The pool area...Ch. 3 - One particular zone served by a multizone air...Ch. 3 - A research building requires 100 percent outdoor...Ch. 3 - A space requires cooling in the amount of 120,000...

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