Printer Friendly

Designing for comfort: selecting air-distribution outlets.

A great deal of time is spent designing a system, including sizing chillers and air handlers and laying out pumps and controls, but how much time is spent selecting air-distribution devices? In conversations with design engineers, they estimate spending weeks and months laying out chillers, air handlers, controls and ductwork, but estimate they spend only minutes selecting and laying out air-distribution devices. Most of the HVAC consulting engineer's time is spent designing a system to meet the required ventilation rate and space temperature, but occupant discomfort can still occur if the space air velocity is too high.

The tendency of designers is to add more air-distribution devices, spaced closely together, as a margin of safety for a project. Using proper air-distribution device selection methods can greatly improve occupant comfort, and reduce the number of devices. This has the added value of reducing the amount of ductwork required and the associated accessories and labor. These savings can be accomplished by the designer without a significant amount of additional design time.

Cost of Discomfort

A review of existing literature found that the effect of comfort on productivity generally covers ventilation rate and temperature. The literature suggests that the potential annual saving or productivity gain (in 1996 U.S. dollars) can be as much as $20 to $160 billion. (1) The financial costs due to reduced productivity associated with occupants' thermal discomfort are significantly greater than the costs due to the much publicized sick building syndrome.

Mixed Air-Distribution System

One factor that is commonly overlooked in an air-distribution system design is the resulting room air velocities generated by the outlets and the spacing of the outlets. It is fairly common to see outlets spaced too close together and the downward draft that is generated. Also, it is common to see outlets placed too close to an architectural feature that protrudes below the ceiling, resulting in the horizontal jet being forced down into the space and causing drafts for the occupants.

[FIGURE 1 OMITTED]

Several methods described below can be used to avoid high velocity jets and the resulting drafts when selecting outlets for an air-distribution system. These methods can be implemented without adding a significant amount of design time for a project. Designing to control room air motion will lead to higher levels of comfort and a more productive environment.

Defining a Fully Mixed System

ASHRAE Handbook--Fundamentals, Chapter 20, Space Air Diffusion, defines a fully mixed system as the following:

"In mixed-air systems, high-velocity supply jets from air outlets maintain comfort by mixing room air with supply air. This air mixing, heat transfer and resultant velocity reduction should occur outside the occupied zone. Occupant comfort is maintained not directly by motion of air from the outlets, but from secondary air motion that results from mixing in the unoccupied zone. Comfort is maximized when uniform temperature distribution and room air velocities of less than 50 fpm (0.25 m/s) are maintained in the occupied zone."

A fully mixed system ideally maintains a constant temperature gradient from the floor to the top of the occupied zone. Unlike displacement systems or underfloor systems, the fully mixed system maintains a uniform temperature through dilution of the space air with the air supplied into the space (Figure 1).

Typically, a forced air system is designed to meet the following performance parameters: 73[degrees]F to 77[degrees]F (23[degrees]C to 25[degrees]C) with humidity at 25% to 60% and air velocity in the occupied zone of less than 50 fpm (0.25 m/s).

The latest version of ASHRAE Standard 55-2010 allows for elevated air speeds "to be used to increase the maximum operative temperature for acceptability under certain conditions." These temperatures and velocities are shown in the standard's Figure 5.2.3.1. This article covers air outlet selection where the desired temperature range is 73[degrees]F to 77[degrees]F (23[degrees]C to 25[degrees]C).

Effect of Velocity on Comfort

Figure 2 shows the effect of room air velocity on the perception of comfort. The figure also shows the neck region is more sensitive to air motion then the ankle region. As you can see from the graph, in the neck region, the percentage of complaints are significant at and above 50 fpm (0.25 m/s) velocity. In many cases, the perception of a draft is not because of air temperature, but rather the velocity of air around the occupants. This can be demonstrated by the use of a ceiling fan that is turned on to provide cooling, even though the air being circulated is at room temperature.

Outlet Selection

When designing a fully mixed system for comfort, it is important to define the occupied and unoccupied zone for a space. The occupied zone is the space we live and work in. It is typically the volume from the floor up to a height of 6 ft (1.8 m) and 6 in. to 1 ft (152 mm to 305 mm) from the walls. The occupied zone depends on the specific space and use of that space. We can use the unoccupied zone to deliver all the high velocity supply air and do all the mixing.

The tool that can be used by a designer to predict the location of a discharge jet is listed as "throw" in a manufacturer's catalog. The current standard for outlet testing is ASHRAE Standard 70-2006 (RA 2011), Method of Testing the Performance of Air Outlets and Air Inlets, which defines how throw data is obtained and allows the testing of both isothermal and non-isothermal air. Most of the manufacturer's throw data is, in fact, isothermal air. The reason for this is the data is easier to obtain and is repeatable. Non-isothermal air requires a balanced room, which does require a significant amount of time to conduct testing.

[FIGURE 2 OMITTED]

Discharge Jets

Outlets generate a discharge jet. The designer should select the type of outlet and space the outlets so that the maximum velocity in the occupied space does not exceed 50 fpm (0.25 m/s). There are several principles of jet behavior that if used along with the manufacturer's catalog throw data, the designer can better predict the resulting velocities in the occupied zone.

These principles include:

* A free jet expands at approximately 22[degrees]. The expansion of the jet is due to the induction of air around the jet.

* If a jet is directed toward a surface, the jet will want to stay on that surface regardless if the surface is a ceiling, wall or floor.

* At some point, a cooled jet projected along a horizontal ceiling service will separate from the surface and drop downwards. The point where the jet leaves the ceiling is defined as the separation point.

In a mixed air system, the outlet is an "engine" that produces a discharge jet into the unoccupied zone causing air in the occupied zone to be induced into the supply jet. A typical diffuser induces 20 to 30 times the amount of supply air discharged. This rate of induction is how we maintain comfort in a mixed air system. By discharging jets of air into the unoccupied zone, we create air motion and circulation in the occupied zone.

Because of the high rate of induction generated by outlets, the temperature of the supply jet reaches near space temperature within a very short distance from the outlet. Most of the exchange of load from the supply air to the room air occurs within several feet from the outlet.

The outlets should be spaced to ensure that the entire occupied zone has some induction and air motion to avoid stagnant areas. Placing returns in stagnant areas will not create air motion to pull room air to the return.

Selection by Noise Criteria

The most common method of outlet selection is by using noise criteria (NC) for a device at the required cfm. The designer determines the outlet type and size by using the required cfm for an outlet and the maximum NC levels desired for a space. The NC targeted values most commonly used are from Table 1 of the 2011 ASHRAE Handbook--HVAC Applications, Chapter 48, Noise and Vibration Control (examples of recommended NC values from the Handbook are shown in Table 1).

Although this method will select devices that meet required sound levels, it does not address the primary requirements of maximizing thermal comfort in the occupied zone. Using this method, the diffusers can be spaced too close together creating a draft with a velocity of more than 50 fpm (0.25 m/s) in the occupied zone. This method can also lead to stagnant zones where there is little or no induction from the space into the supply outlet.

Selection Using Throw Data

Using the published throw data obtained from a manufacturer's catalog is one method of outlet selection that can be used to predict room air velocity. This information will indicate the performance of the discharge jet once it leaves the outlet and can be used to fairly accurately predict resulting space velocities (Figures 3a and 3b).

Throw data obtained per ASHRAE Standard 70-2006 is typically given in a manufacturer's catalog at 50, 100 and 150 fpm (0.25, 0.51 and 0.76 m/s) (Figure 4). Throw is defined as the distance, in ft (m), from the center of the outlet perpendicular to a point in the mixed airstream where the velocity has been reduced to a specified terminal velocity. In most cases, throw data is based on isothermal air. If either cooled or heated air is shown, the throw data does not indicate the drop or rise of the jet or the spread of the jet. Using the throw information, a designer can map out the location of outlets so as to predict and maintain velocity in the occupied zone below 50 fpm (0.25 m/s).

[FIGURE 3 OMITTED]

Selection by [T.sub.50]/L and ADPI

Another available method to predict air velocities and comfort in the occupied zone is by using the [T.sub.50]/L ratio to predict the resulting ADPI value for a space where [T.sub.50] is the cataloged throw data to 50 fpm and L is the characteristic length of the space being evaluated. Characteristic Length L is the horizontal distant from the outlet to the outside of the zone the outlet serves. If the outlet is placed so that there are differing distances from the outlet out to the zones served (i.e. a four way pattern), the outlet may have up to four different L values that are used to calculate the [T.sub.50]/L ratio in each direction. Characteristic Length L is defined in Table 3 in Chapter 57 of the 2011 ASHRAE Handbook--HVAC Applications.

[FIGURE 4 OMITTED]

What is ADPI

Air diffusion performance index (ADPI) is a single number that quantifies the overall comfort of a space when in cooling. ADPI is the percentage of points in a space where the effective draft temperature is between -3[degrees]F and +2[degrees]F (-19[degrees]C and -17[degrees]C) and the air velocity is less than 70 fpm (0.36 m/s). A high percentage of people have been found to be comfortable in cooling applications for office-type occupations where these conditions are met. High ADPI values generally correlate to high space thermal comfort levels with the maximum obtainable value of 100.

The effective draft temperature provides a quantifiable indication of comfort at a discrete point in a space by combining the physiological effects of air temperature and air motion on a human body.

A point is considered comfortable if the results of Equation 1 are between -3[degrees]F and +2[degrees]F (-19[degrees]C and -17[degrees]C), and the measured velocity at the point is less than 70 fpm (0.36 m/s).

[T.sub.ed] = ([T.sub.x] - [T.sub.c]) - 0.07([V.sub.x] - 30) (1)

where

[T.sub.ed] = effective draft temperature, [degrees]F

[T.sub.x] = local airstream dry-bulb temperature, [degrees]F

[T.sub.c] = average (control) room dry-bulb temperature, [degrees]F

[V.sub.x] = local airstream centerline velocity, fpm

By determining the value of [T.sub.50] from a manufacturer's catalog, and measuring the characteristic length L from the project's plans, the ratio can be determined and the predicted ADPI value can be estimated from Table 2.

Location of Return/Exhaust Grilles

ASHRAE Handbook--HVAC Applications, Chapter 57, Room Air Distribution, recommends that "A return inlet affects room air motion only in its immediate vicinity. The intake should be located in the stagnant zone to return the warmest room air during cooling or the coolest room air during heating. The importance of the location depends on the relative size of the stagnant zone, which depends on the type of outlet."

Also, the return or exhaust grille does not short circuit the supply jet. In fact, if a supply jet is at or above 150 fpm (0.76 m/s) and directed over a return, the jet will either pull air out to the return or exhaust or create a "blanking effect" over the return or exhaust where no air is taken out of the space. If the return or exhaust is placed at the end of the supply jet where the velocity is 150 fpm (0.76 m/s) or less, the air being returned is at or near room temperature and the amount of air being returned is close to 5% of the total air motion in the space.

[FIGURE 5 OMITTED]

[FIGURE 6 OMITTED]

High Velocities in Occupied Zone

A system can be designed with proper capacities and air changes but still result in discomfort due to air greater than 50 fpm (0.25 m/s) entering the occupied zone. Designing to avoid the air-distribution problems shown in Figures 5 and 6 will greatly improve the comfort of a space.

Examples Using Throw Data

The following examples show how the throw data can be used to predict the resulting air motion in a space. In this example, the space is 20 ft x 20 ft with 9 ft (6 m x 6 m with 3 m) ceilings and the required airflow is 950 cfm (448 L/s).

[FIGURE 7 OMITTED]

[FIGURE 8 OMITTED]

Example 1

In this example (Figure 7), colliding airstreams will generate a high velocity in the occupied zone. The [T.sub.50]/L calculation shows a value of 3.6, higher than the desired 1.4 to 2.7, indicating a draft in the occupied zone. We also can predict too high a velocity in the center of the space by mapping out the throws of the outlets.

Example 2

To reduce the room air velocity, one diffuser is selected and placed in the center of the room (Figure 8). The value of [T.sub.50] /L is now 2.4 and within the recommend range to maximize the ADPI value for the space. Although the supply jet does reach the floor and enters the occupied zone, from Figure 2 we know that the ankle region is much more tolerant to higher velocities compared to the neck region.

This selection has eliminated one diffuser compared to Example 1 and the associated costs while providing a higher level of comfort.

Conclusion

Most HVAC designers spend a significant amount of time selecting chillers, air handlers, pumps and cooling towers with the purpose of maintaining occupant thermal comfort in a space. Most conventional air distribution systems in North America are mixed air systems where space comfort is maintained through the induction of air from the occupied zone into the unoccupied zone. The definition of comfort includes maintaining room air velocities below 40 fpm to 50 fpm (0.20 m/s to 0.25 m/s). This is sometimes overlooked by designers, resulting in discomfort to the space occupants caused by excessive air motion.

By using some simple selection techniques such as mapping cataloged throw data and the [T.sub.50]/L method to predict ADPI, designers can select and space outlets to maximize the comfort level in an occupied space. Using these methods also offers the opportunity to reduce the required number of outlets and the associated costs.

References

(1.) Fisk, WJ. 2002. "How IEQ affects health, productivity." ASHRAE Journal 44(5).

About the Author

David A. John, P.E., is chief engineer for Metal Industries in Clearwater, Fla. He is an ASHRAE Distinguished Lecturer, a member of ASHRAE TC 5.3, Room Air Distribution, and chair of SPC 129, Measuring Air-Change Effectiveness.

By David A. John, P.E., Member ASHRAE
Table 1: Examples of recommended NC values (from 2011 ASHRAE
Handbook-HVAC Applications).

Room Types                                    NC/RC    dBA     dBC

Rooms with             Traffic Noise           N/A      45      70
Intrusion from         Aircraft Flyovers       N/A      45      70
Outdoor Noise
Sources

Residences,            Living Areas             30      35      60
Apartments,            Bathrooms,               35      40      60
Condominiums           Kitchens,
                       Utility Rooms

Hotels/Motels          Individual Rooms or      30      35      60
                       Suites
                       Meeting/Banquet          30      35      60
                       Rooms
                       Corridors and            40      45      65
                       Lobbies
                       Service/Support          40      45      65
                       Areas

Office Buildings       Executive and            30      35      60
                       Private Offices
                       Conference Rooms         30      35      60
                       Teleconference Rooms     25      30      55
                       Open-Plan Offices        40      45      65
                       Corridors and            40      45      65
                       Lobbies

Table 2: Air diffusion performance index (ADPI) selection guide
(from Table 4, Chapter 57 of the 2011 ASHRAE Handbook--Applications).

Terminal Device        Room Load,             [T.sub.50]/L for
                       Btu/h x [ft.sup.2]     Maximum ADPI

High Sidewall          80                     1.8
Grilles                60                     1.8
                       40                     1.6
                       20                     1.5
                       <10                    1.4

Circular Ceiling       80                     0.8
Diffusers              60                     0.8
                       40                     0.8
                       20                     0.8

Sill Grille,           80                     1.7
Straight Vanes         60                     1.7
                       40                     1.3
                       20                     0.9

Sill Grille,           80                     0.7
Spread Vanes           60                     0.7
                       40                     0.7
                       20                     0.7

Ceiling Slot           80                     0.3
Diffusers              60                     0.3
(For [T.sub.100]/L)    40                     0.3
                       20                     0.3

Light Troffer          60                     2.5
Diffusers              40                     1.0
                       20                     1.0

Perforated,            11 to 50               2.0
louvered ceiling
diffusers

Terminal Device        Maximum                For ADPI
                       ADPI                   Greater Than

High Sidewall          68                     --
Grilles                72                     70
                       78                     70
                       85                     80
                       90                     80

Circular Ceiling       76                     70
Diffusers              83                     80
                       88                     80
                       93                     90

Sill Grille,           61                     60
Straight Vanes         72                     70
                       86                     80
                       95                     90

Sill Grille,           94                     90
Spread Vanes           94                     80
                       94                     --
                       94                     --

Ceiling Slot           85                     80
Diffusers              88                     80
(For [T.sub.100]/L)    91                     80
                       92                     80

Light Troffer          86                     80
Diffusers              92                     90
                       95                     90

Perforated,            96                     90
louvered ceiling                              80
diffusers

Terminal Device        Range of
                       [T.sub.50]/L

High Sidewall          --
Grilles                1.5 to 2.2
                       1.2 to 2.3
                       1.0 to 1.9
                       0.7 to 2.1

Circular Ceiling       0.7 to 1.3
Diffusers              0.7 to 1.2
                       0.5 to 1.5
                       0.7 to 1.3

Sill Grille,           1.5 to 1.7
Straight Vanes         1.4 to 1.7
                       1.2 to 1.8
                       0.8 to 1.3

Sill Grille,           0.6 to 1.5
Spread Vanes           0.6 to 1.7
                       --
                       --

Ceiling Slot           0.3 to 0.7
Diffusers              0.3 to 0.8
(For [T.sub.100]/L)    0.3 to 1.1
                       0.3 to 1.5

Light Troffer          <3.8
Diffusers              <3.0
                       <4.5

Perforated,            1.4 to 2.7
louvered ceiling       1.0 to 3.4
diffusers
COPYRIGHT 2011 American Society of Heating, Refrigerating, and Air-Conditioning Engineers, Inc.
No portion of this article can be reproduced without the express written permission from the copyright holder.
Copyright 2011 Gale, Cengage Learning. All rights reserved.

Article Details
Printer friendly Cite/link Email Feedback
Title Annotation:TECHNICAL FEATURE
Author:John, David A.
Publication:ASHRAE Journal
Geographic Code:1USA
Date:Sep 1, 2011
Words:3261
Previous Article:Optimizing design & control of chilled water plants: Part 2: condenser water system design.
Next Article:Library sets example.
Topics:

Terms of use | Privacy policy | Copyright © 2019 Farlex, Inc. | Feedback | For webmasters