NBS

A11100 ^44^1 PUBLICATIONS

NBSIR 81-2277

Control Strategies for Energy

Conservation — A Case Study of

the Materials Building, National

Bureau of Standards

James Y. Kao

E. Thomas Pierce

Building Equipment Division

Center for Building Technology

U.S. Department of Commerce

National Bureau of Standards

Washington, DC 20234

May 1981

Sponsored by

Plant Division

Office of the Director of Administration

and Information Systems

ational Bureau of Standards

'ashington, DC 20234

MATIOBAL BUR1*a ' OF STANDARDS

UBBART

JUL 2 0 1981

NBSIR 81-2277

CONTROL STRAGEGIES FOR ENERGY

CONSERVATION ~ A CASE STUDY OF

THE MATERIALS BUILDING, NATIONAL

BUREAU OF STANDARDS

James Y. Kao

E. Thomas Pierce

Building Equipment Division

Center for Building Technology

U.S. Department of Commerce

National Bureau of Standards

Washington, DC 20234

May 1981

Sponsored by

Plant Division

Office of the Director of Administration

and Information Systems

National Bureau of Standards

Washington, DC 20234

U.S. DEPARTMENT OF COMMERCE, Malcolm Baldrige, Secretary

NATIONAL BUREAU OF STANDARDS, Ernest Ambler, Director
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PREFACE

This study was funded by the Plant Division of the National Bureau of Standards

(NBS). It is the objective of the NBS Plant Division to determine the annual

energy savings that may be realized from implementation of new air handling

system control strategies and thus to plan air handling system control retrofits

Bureau wide. The retrofit of these controls will aid the Plant Division in

obtaining their 20 percent reduction in energy consumption by FY 85 compared to

FY 75, as required by the Department of Energy’s Ten Year Energy Conservation

Buildings Plan. The Plant Division presently has a boiler improvement study

under way to determine the heating plant efficiency, and is planning to evaluate the refrigeration plant performance in the near future. Verification of the

predicted results of some of the control strategies in this study is currently

being prepared and will be evaluated in the future. The NBS energy monitoring

and control system will be used to collect building energy consumption data and

to implement enthalpy control and system shutdown strategies.

The control strategies selected in this study and the input data for the

calculations were determined jointly by the Plant Division and the authors.

The authors wish to express their appreciation to Christopher Conley and Kendall

McDaniel of the Plant Division for their assistance.

iii
ABSTRACT

The BLAST-2 computer program is used to investigate various heating, ventilating

and air conditioning control strategies and their combinations to reduce the

energy consumption of a laboratory building located at the National Bureau of

Standards Gaithersburg site. The techniques of modeling the building load and

air system performance are explained. The results are presented and discussed.

Control strategies investigated include dry-bulb and enthalpy economizer cycles,

resetting supply air temperatures by outside temperature and zone demand, shutdown of fan systems selectively, and converting interior systems to VAV systems.

By combining the various control strategies, eight percent, twenty-nine percent

and eight percent of heating, cooling and fan energy respectively may be saved.

Keywords: building energy analysis; computer modeling, control strategies;

controls, energy conservation for non-residential buildings; load

calculations.

iv
CONVERSION FACTORS TO METRIC (SI) UNITS

Physical

Quantity Symbol

To Convert

From To

Multiply

By

Length ft m 3.048 x 10 1

Temperature T °F °C T C = (Tf - 32)/l .8

Volume Rate of Flow V CFM m

3 /s 4.719 x 10“A

Coil Capacity Qs Btu/hr J/s 2.931 x 10

_1

Energy Btu J 1.055 x 103

v
TABLE OF CONTENTS

Pa8e

PREFACE iii

ABSTRACT iv

CONVERSION FACTORS TO METRIC (SI) UNITS v

1. INTRODUCTION 1 2 . BUILDING AND BLAST IMPLEMENTATION 2

2.1 Building Description 2

2.2 BLAST Modeling 2

3. CONTROL STRATEGIES AND MODELING 6

3.1 Control Strategies 6

3.2 Air Balance 9

3.3 System Shut-down Modeling 12

4. RESULTS - DATA 19

5. CONCLUSIONS 28

REFERENCES 29

APPENDIX - Input Data for Base Case 30

vi
1 . INTRODUCTION

The Gaithersburg site of the National Bureau of Standards (NBS) has over 2.2

million square feet of floor space. Used mainly for office and laboratory

functions, most of the buildings were constructed in the 1960's. Several

years later, during the early 1970's, major efforts were made to reduce the

energy consumption of the building heating, ventilation and air conditioning

(HVAC) systems [1]*. Lighting reductions, office-space HVAC-system shut-downs,

space thermostat adjustments, and raising the air-handling system discharge-air

temperatures resulted in approximately a 12 percent electricity reduction and

18 percent heating fuel reduction. A further overall energy reduction of

approximately 5 percent [2] was made during FY 1980 (using FY 1975 as a base).

This reduction was attributed to the implementation of the Emergency Building

Temperature Restriction [3], shutting down of additional mechanical equipment

during non-occupied hours, and the implementation of new HVAC control systems.

Several of the HVAC control strategies compared in this study were previously

evaluated at NBS. During the mid-1970's, a computer program and bin method were

used to predict the energy savings of enthalpy control, supply-air temperature

reset, and shutting down of office spaces during non-occupied hours.

As a continuing effort in energy conservation at NBS, the HVAC control

strategies in the General Purpose Laboratory (GPL) buildings are examined in

this study. At this site, there are seven GPL's with similar constructions

and physical dimensions as well as similar HVAC-system arrangements. The energy

conservation control strategies and energy saving predictions for one laboratory

building should be applicable to all the others, with minor modifications. The

building chosen for this study is Building 223, also known as the Materials

Building.

One of the dominant factors influencing the amount of energy consumption in

non-residential buildings, such as the NBS laboratories under study here, is

the performance of automatic temperature and humidity controls that regulate

the operation of the HVAC systems. Although these controls generally include

the heating and cooling generation, as well as the air systems to deliver the

desired heating and cooling energy to the occupied spaces, the present study

is limited to the consideration of the latter only. At NBS, the heating and

cooling media are generated in a central plant and are distributed to individual

buildings through underground steam and chilled water pipes. This study investigates some of the control strategies which may be used for the air handling

systems inside the Materials Building and therefore, the energy amount predictions are the energy required to be delivered at the building boundary.

*Figures in brackets indicate references on page 30
2. BUILDING AND BLAST IMPLEMENTATION

2.1 BUILDING DESCRIPTION

The Materials Building is a three-story building, 385 feet long, and 105 feet

wide, with the long axis along the true east-west direction. The result of

this orientation is that all windows are facing either north or south. The

building is of heavy reinforced concrete construction. The building is

divided into interior and perimeter spaces. The interior rooms are used mainly

for laboratories and the perimeter rooms are generally used for offices. Six

air-handling units serve the interior zones, and an additional four air-handling units serve the perimeter offices, two units each for the north and

south sides. Constant volume HVAC systems are located on the attic floor.

The air-handling units are composed of air filters, steam preheat coils,

steam humidifiers, chilled water cooling coils, supply-air fans and returnair fans. A simplified building floor plan and cross section are shown in

figure 1.

A constant volume of air is supplied to the rooms with reheat provided by hot

water reheat coils. The reheat coils for the laboratories are of the duct

type, and those for the perimeter offices are of the induction type with the

induction units located under the windows. There are over 80 laboratory

exhaust fans discharging air through the roof. Steam at 150 psig and 42°F

chilled water are supplied from the central plant. Closed-loop hot water is

generated inside the building from steam.

2.2 BLAST MODELING

The computer program BLAST-2 [4] was used to calculate the building energy con- sumptions. BLAST, one of the public-domain building energy analysis programs,

is recognized as representing the state-of-the-art. The basic design is to

model each room as a single office or laboratory module, rather then to lump

large sections together without separating partitions. These individual-space

modules are to provide for radiation exchange between the walls, floor and

ceiling of the module. Multipliers ("zone-multipliers" in the terminology of

BLAST) then establish the correct number of spaces for each air handling system.

The six interior (laboratory) air handlers were combined into a single interior

air handler for this analysis, and the four perimeter (exterior offices) air

handlers were modeled as in the real building.

The interior air handler of the model has 84 general purpose and 96 more critical

laboratory spaces, a total of 180 module spaces, and is designated system twenty

in this report. The four exterior air handlers are designated systems three,

five, six, and eight, and serve 36, 45, 47, and 38 offices respectively.

A single BLAST plant simulation supplies heating, humidification and cooling to

all of the air handlers, so as to summarize the overall steam and chilled water

energy requirements for the building.

People, lights, and electrical equipment were scheduled so as to approximate

the sensible and latent effects resulting from these sources of internal heat

2
m #«

* • “T “ “ ' '

f

1 ACU #6

m #io m #4 ICU #2

m #i

L ACU #7 ! m #i

m #5

i

ii ACU #3

Simplified building plan showing areas

served by air handling systems

CORRIDORS

Figure 1. Simplified building plan and cross section

3
Table 1. Internal Load Profiles

Hours

From

To

5 6 7 6 7 88 9 10 11 12

9 10 11 12 13

People

Lights

Equipment

.1 .1

.2 .2

.2 .2

.2 .8

.2 .5

.2 .2

1 1

1 1

1 1

1 .8

1 1

1 1

Hours

From 13 14 15 16 17 18 19 20

Nights

and

To 14 15 16 17 18 19 20 21 Weekends

People 1 1 1 1 .6 .2 .1 .1 .0

Lights 1 1 1 1 1 .2 .2 .2 .2

Equipment 1 1 1 .4 .2 .2 .2 .2 .2

gains, as shown in table 1. The numbers in the table are scaling factors, by

which the peak magnitudes of people, lights and equipment for each space are multiplied to determine the hourly internal loads.

Weather data for the energy analysis requires hourly information about weather

parameters. A Typical Meteorological Year (TMY ) weather file for Washington,

D.C. was used in the present study. TMY files are composed of "typical" months

selected from SOLMET files for different years, and include solar intensity data.

The year 1979 determined the position of the sun for any particular day, and

the weather file established the location as latitude = 39.0, longitude = 77.7

degrees.

Five design days were also used during certain tests of the BLAST models. These

are not the sort of design day used for sizing equipment, but rather are used

to see how a building performs under a variety of conditions, as shown in

table 2. Temperatures are in degrees Fahrenheit, and the wet-bulb temperature

corresponds to the highest dry-bulb temperature of the day. At lower dry-bulb

temperatures, BLAST holds the same humidity ratio until saturation is reached,

and then tracks downward along the saturation curve (and back up along the same path). Design day DD5 is cloudy; the rest have clear skies.

BLAST heating and cooling capacities were established as follows: for a particular air handling system, the top floor receives 20 percent more supply

air than the two lower floors. These supply-air quantities established the

cooling capacities for each space according to the formula Q s = 1.085 x V x

( T room “ T supply)> where T room and T SUpp iy are the room and supply air temperature in °F dry bulb, V is the supply air volume in cubic feet per minute, and

Qs is the supply air capacity for those particular temperature conditions in

Btu/hour. The heating capacities were considered adequately sized, so that the

4
Table 2. Design Days

Design Day Temperature, °F

Name High Low Wet-Bulb Date

DDl 91 71 77 21 July

DD2 78 58 65 21 April

DD3 62 42 52 21 April

DD4 33 13 27 21 January

DD5 13 13 11 21 January

space temperature would not drop below the local heating setpoint temperatures

during non-shut down hours®

During perimeter system night shutdown, it was considered that without the

induction air the heating setpoint temperatures would not always be maintained,

so that the resulting space temperature drift was simulated with a ramp control,

fully on at 55°F and fully off at 65°F. The fully on heating capacity for

use during system shutdown was set at the rate required to maintain the space at

65°F over the whole TMY year. This resulted in a simulated space temperature

drift during night shutdown that went down to approximately 57 °F with the

design day DD5, and reached a low of approximately 58°F on the TMY-year weather

file. During the office hours on design day DDl with 60°F supply air temperature, the space temperature varied between 72°F and 75°F in the third floor

perimeter offices on the south side of the building and between 74°F and 77 °F

in the north side third floor perimeter offices. During the night shutdown,

the space temperature drifted to approximately 81 °F and 82°F, respectively,

in these offices. There was, of course, no cooling capacity available during

the time when an air-handling system was shut down. The higher temperature in

the north offices than the south offices was caused by lower supply air quantities to the north side than to the south side.

Each of the air-handling systems has a cooling coil designed for NBS conditions

(rather than making use of the BLAST default coil). Other model system characteristics include steam humidification to 30 percent RH, a 1°F throttling range

in the cold deck control, steam preheat in the mixed air chamber, and a 3 inch

supply fan pressure rise.

5
3. CONTROL STRATEGIES AND MODELING

3.1 CONTROL STRATEGIES

A simple constant-volume, fixed discharge-air temperature (not necessarily the same temperature for all air-handling systems), fixed outside air amount, and

space controlled reheat temperature model was used as a base case for energy

consumption comparisons. The control strategies tested including raising the

cooling coil discharge air temperature, adding dry-bulb return air economizer

control, adding enthaply economizer control, resetting the perimeter system

supply air temperature seasonally or by outside air temperature, converting

interior systems to variable air volume (VAV), controlling interior system supply air temperature by zone demand, selectively shutting down perimeter systems

during non-office hours, and different combinations of these strategies.

Finally, an architectural retrofit, using double-glazed windows for the singlepane windows, was modeled for the base case. The modeling of some of these

strategies is described in detail below.

Case 1. BLAST Base Case

For the basic BLAST base case, as few BLAST options as reasonable were used, so that the effect of existing as well as new control options could be studied.

Hence, the case 1 configuration has a constant volume, fixed outside air quantity (no damper control), 30 percent minimum relative humidity in the space,

with the off-coil air temperature of the cooling coils at 57°F for interior

systems and 60°F for perimeter systems. Complete input data of the base case

may be found in the Appendix.

Case 2. Raising Perimeter System Supply Air Temperature to 65 °F in Winter

This is the same as case 1, except that the supply air (SA) temperature for

perimeter systems is set at 65°F during the months of November through April.

The BLAST input form is

COLD DECK TEMPERATURE =65;.

Cooling and reheat energy should both be saved, since the cold supply air is

closer to the room temperature. However, depending on the outside air

conditions, more steam may be required to attain the required space humidity.

Case 3. Dry-Bulb Economizer for All Air-Handling Systems

The BLAST input form is

MIXED AIR CONTROL = RETURN AIR ECONOMY CYCLE;.

This is a damper control in which the outside air (OA) dampers range between a minimum established by the exhaust air (EA) quantity and a maximum of 100 percent. Return air and outside air are mixed to achieve mixed air (MA) at the

cold deck dry bulb temperature, if possible.

6
Case 4. Dry-Bulb Economizer with Perimeter Winter Supply Air Temperature at

65°F

The perimeter system supply air temperature is seasonally adjusted as in case

2. This is a combination of cases 2 and 3.

Case 5. Enthalpy Economizer for Perimeter Systems

An enthalpy test permits dry-bulb control of the OA dampers in those cases

where the OA-enthaply is less than that of the return air. The enthalpy test

decides whether minimum or 100 percent outside air should be admitted. If the

outside air enthalpy and dry-bulb temperature are less than those of the return

air, the outside air damper is controlled to give mixed air temperature not

lower than that of the supply air. The BLAST input form is

MIXED AIR CONTROL = ENTHALPY ECONOMY CYCLE;.

Case 6. All 10 Systems have Enthalpy Economizer

Similar to Case 5, all 10 systems add enthalpy economizer cycle to the base case.

Case 7. Perimeter System OA-Reset

The BLAST input form is

COLD DECK CONTROL = OUTSIDE AIR CONTROLLED;

COLD DECK CONTROL SCHEDULE = (65 AT 65, 60 AT 66);.

The supply air temperature is 65°F when outside temperature is 65°F and below,

and changes to 60°F when outside is 66°F and over. It simulates a flip-over

type of supply air temperature control for the perimeter systems. The one degree (65°F to 66°F) is to allow for the BLAST throttling range in the cold

deck control. An error in the BLAST program code (previously uncorrected even

at CERL) was discovered during this study and was corrected by NBS.

Case 8. Perimeter S ystem OA-Reset

This is similar to Case 7, except that a linear reset schedule is established

between two sets of outdoor air and supply air temperatures. In this case, the

supply air temperature is set at 65°F when the outside is at 40°F and below,

the supply air is at 60°F when the outside air is at 80°F and above. In between

40°F and 80°F outside temperature, the supply air is controlled linearly between

65°F and 60°F. The BLAST input form is changed for case 7 to

COLD DECK CONTROL SCHEDULE = (65 AT 40, 60 AT 80);.

7
Cases 9, 10, and 11. Perimeter Systems Shut-Downs During Non-Office Hours

These cases are for shutting down the perimeter systems and toilet exhaust fans

during non-office hours (nights and weekends). Due to the requirement for constant laboratory exhaust air, and to the heating of the reheat-induction units

during heating seasons, more complicated modeling schemes are needed. These

will be discussed later in this section.

Case 12. Interior Systems Converting to VAV

The supply air volume is controlled to maintain 65°F in the non-critical

laboratory spaces. That is, there is a quite narrow throttling range for the zone dampers to move from fully open to minimum positions. In this case,

only the non-critical laboratories are converted to VAV systems.

Case 13, Interior System VAV Adding Enthaply Economizer Cycle

This is similar to case 12, adding enthalpy economizer cycles to the interior

systems.

Case 14 to 17. Interior System Supply Air Temperature Reset by Zone Demand

and Selected Combinations

Instead of converting interior systems to VAV as assumed in case 12, the

interior non-critical laboratories may be retrofitted to have varying discharge

air temperature which is set by the most demanding zones. Case 14 is a single

strategy case, to vary the supply air temperature from 50°F to 60°F. Case 15

is case 14 modified by a seasonal change, reset supply air temperature from 50°F

to 60°F between May 1 and September 30, and from 50°F to 70 U F between October 1 and April 30. Case 16 is similar to case 14, adding enthalpy economizer cycles

to all systems. Case 17 is similar to case 15, also adding enthalpy economizer

cycles to all systems. The reason for having the seasonal reset schedules in cases 15 and 17 is to achieve maximum reset benefit yet to avoid unacceptably

high space humidity during the summer seasons.

Case 18 and 19. Comprehensive Combined Control Strategies

Case 18 combines the perimeter system supply air reset to 65°F when outside is

65°F and below, and to 60°F when outside is 66°F and above (as in case 7),

shutting down ACU #6 and the toilet-exhaust fans during non-office hours (as

in case 9), interior system supply air temperature reset by zone demand from

50°F to 60°F (as in case 14), and all systems under enthalpy economizer cycle

(as in case 6). Case 19 is similar to case 18 except that the perimeter supply

air temperature reset is changed to 65°F when outside is 40°F and below, to 60°F

when outside is 80°F above, and controlled linearly between the 60°F and 65°F

conditions (as in case 8)

8

i
Case 20. Base Case with Double-Glazed Windows

This is the only case for which architectural retrofit was involved in this

investigation.

3.2 AIR BALANCE

In order to obtain the best energy consumption calculation results, it is

important that the actual building operating data, including air balance data,

be used in this kind of study. Therefore, the system air balance data had been

measured by a combination of tracer gas and pitot tube techniques, as shown in

figure 2. Tracer gas measurements were used to find the ratio of supply to

return air (SA/RA), and pitot measurements measured return and exhaust air quantities. Table 1A shows those data as determined by these techniques. The

return and exhaust columns show the directly measured data, and the supply and

outside air quantities are derived by the equations

SA = (SA/RA)RA, and

OA = (( SA/RA)- 1)RA

The outside and exhaust air totals differ by four percent of the supply air total,

which is a measure of the possible accuracy of these results. Since the tracer

gas is believed to provide quite accurate results, the exhaust data were considered less significant in developing the magnitudes used in BLAST, as shown in

table IB.

The building is assumed to be balanced in the baseline condition. That is, for

the building as a whole, the net infiltration is zero, and the total of the

exhaust air and return air exactly equals the supply air to the spaces of the

building. Thus the outside air is equal to the exhaust air.

SA = RA + EA , OA = EA

This assumption is conservative in that additional infiltration might result in

additional energy consumption, and is consistent with the observation that in

fact the building pressure varies from neutral to very slight exfiltration.

Within the building, the individual space air handlers are not balanced. For the

exterior systems, there is no exhaust, and the supply air exceeds the return air

with the excess conditioned air (CA) going to the interior systems:

SA = RA + CA , EA = 0.

For the interior systems, this excess conditioned air plus the interior supply

air is equal to the return air plus the exhaust air:

SA + CA = RA + EA.

The exhaust air includes the air taken by laboratory hoods, general exhausts, and

toilet exhausts. No exhaust is assigned to the exterior systems.

9
Figure 2. Measurement of air quantities. Tracer-gas determines ratio SA/RA;

EA and RA are measured directly.

10
Table 1A. Available Data on Real Air Balance

SA/RA Return Exhaust Supply Outside

cfm cfm cfm cfm

Labs 1 .853 46 870 62 300 86 860 39 990

Toilets 0 2 250 0 0

ACU-3 1.548 7 630 0 11 800 4 170

ACU-5 1.862 7 490 0 13 940 6 450

ACU-6 2.008 5 400 0 10 840 5 440

ACU-8 1.572 5 850 0 9 200 3 350

73 240 64 550 132 640 59 410

Table IB. Air Balance for BLAST

Return Exhaust SuPP1 y Outside

cfm cfm cfm cfm

Labs 46 870 57 160 86 860 39 990

Toilets 0 2 250 0 0

ACU-3 7 630 0 11 800 4 170

ACU-5 7 490 0 13 940 6 450

ACU-6 5 400 0 10 840 5 440

ACU-8 5 850 0 9 200 3 350

73 240 59 410 132 640 59 410

Note: The air quantities under the outside columns do not add up to the

total quantities due to round-offs.

11
In the BLAST model, the program parameters to be input are the supply and exhaust

air volumes, and BLAST derives the return air and outside air quantities. For

the exterior systems, the excess conditioned air is designated exhaust air, and

the actual supply air volume is used. This forces an exterior system to

condition an equal quantity of outside air, and again we have

SA = RA + EA , OA = EA

For the interior systems, the excess conditioned air is exhausted without further

energy transfer, so the measured outside air quantity is designated exhaust air,

and again the actual supply air volume is used.

These concepts and assumptions are illustrated by figures 3, 4, and 5.

3.3 SYSTEM SHUTDOWN MODELING

Several of the energy conserving strategies considered involve shutting down the

fans for one or more of the perimeter systems during nights and weekends. Such a shutdown here includes turning off the toilet exhausts, and may also involve

switching one or more of the remaining perimeter systems to 100 percent outside

air in order to have satisfactory laboratory exhaust. Thus a shutdown may cause changes in the air balance of the building, relative to the initial assumption

that the base case building is balanced.

In the BLAST model, such changes in air balance were considered to result in

changes in the quantity of system outside air, and were applied as an increase or decrease in the exhaust air of the interior (laboratories) system so that the

outside air and exhaust air remain exactly balanced. That is, it was assumed

that an increase in outside air came in through the systems, rather than as infiltration, and required energy to reach space conditions. Similarly, a decrease in outside air was assumed to decrease energy consumption.

As described above, there are two view points from which to consider the air

balance data. Quantities relevant to both points of view are presented in table 2.

Case 1 shows a repeat of the data from table IB, and follows the same format.

The return air quantities correspond to the data for the real building return air

fan — the total of the air returned. Similarly, the exhaust air and supply air

columns correspond to data for the real building. The column "outside air" has

a dual function: it is the real-building estimate of outside air, and it is also

the BLAST model data for exhaust air.

Cases 9, 10, and 11 are the system shutdown cases. The toilet exhausts are off

in each, and 100 percent outside air is used for those perimeter air-handling

units that are in cases 10 and 11. The resulting assumptions about air balance

for these cases are also shown in the table.

BLAST does not easily model a system shutdown for a building operating under NBS

conditions. The system changes in air balance described above could not be

modeled in a single computer run, since for each space the supply and return air

quantities are input only once, and stay the same year round (except for VAV).

12
Figure 3. Air balance assumption

FOR THE BUILDING AS A WHOLE, BALANCE IS ASSUMED: NO RELIEF AIR, AND NO

INFILTRATION.

13
RA

Figure 4. Air transfer between systems

WITHIN THE ACTUAL BUILDING, CONDITIONED AIR IS TRANSFERRED FROM THE

OFFICE TO THE LABS.

14
OA

F ~s

OFFICE

PERIMETER

1 SA m KANDUN6 L— OFFICES, EA=CA

MIXED AIR UNITS

1

PERIMETER

1 -a

LABS

MIXED AMI

Figure 5. BLAST air balance

AS MODELED IN BLAST,

EXHAUST AIR, AND THE

THE EXCESS CONDITIONED AIR FROM THE OFFICES IS DESIGNATED

LAB EXHAUST AIR IS REDUCED TO EQUAL THE LAB OUTSIDE AIR.

15
Table 2. Air Balance for BLAST During Shutdowns

(All Air Quantities are in cfm)

Return Exhaust Supply Outside and Exhaust

(Real Bldg) (Real Bldg) (Both) (In BLAST)

BLAST Base-Case, Case 1

Labs 46 870 57 160 86 860 39 990

Toilets 0 2 250 0 0

ACU-3 7 630 0 11 800 4 170

ACU-5 7 490 0 13 940 6 450

ACU-6 5 400 0 10 840 5 440

ACU-8 5 850 0 9 200 3 350

73 240 59 410 132 640 59 410

Return Exhaust Supp ly Outside and Exhaust

ACU-6 Shutdown, Case 9

Labs 43 680 57 160 86 860 43 190

ACU-3 7 630 0 11 800 4 170

ACU-5 7 490 0 13 940 6 450

ACU-8 5 850 0 9 200 3 350

64 650 57 160 121 800 57 160

Return Exhaust Supply Outside and Exhaust

ACU's-3 and 6 Shutdown, Case 10

Labs 52 840 57 160 86 860 34 020

ACU-5 0 0 13 940 13 940

ACU-8 0 0 9 200 9 200

52 840 57 160 110 000 57 160

Return Exhaust Supply Outside and Exhaust

ACU's-3 , 6, and 8 Shutdown, Case 11

Labs 43 640 57 160 86 860 43 220

ACU-5 0 0 13 940 13 940

43 640 57 160 100 800 57 160

16
Also, when the air is off, the window induction units are to continue to provide heat, although somewhat less efficiently as convection heaters, but BLAST

would turn on the supply fan whenever such heat is supplied.

Thus it was necessary to devise a way to model the energy results of a shutdown

option. This was done by combining the data from four computer runs: 1) the

heat load during shutdown for the shutdown offices (a loads-calculation only';

2) heating and cooling during the shutdown hours for the rest of the building, in

its normal (daytime) operation mode; 3) the same as run 2 with the parameters

modified to the shutdown air balance, including the return fans off where a system went 100 percent OA; 4) The whole building heating and cooling energy,

excluding shutdown offices during shutdown hours, based on the daytime operation

mode air quantities. Note that runs 1, 2, and 3 operate only during nights and

weekends. Run 1 provides correct data, but runs 2 and 3 include pulldown or startup errors when the systems are on at the beginning of the night. Fortunately, those errors are probably similar for the two runs, since they are subtracted one from the other to obtain the effect of the change in air balance.

Finally, the pulldown or startup effects in run 4 are real: the shutdown offices

will have drifted slightly in temperature in the summer, and cooling energy will

be expended to return them to their daytime conditions. The building energy

consumption is obtained by subtracting the results of run 2 from the sum of runs

I , 3 , and 4

An example of this procedure is given in table 3. The columns are labeled with

the above run-numbers. Case 9 involves the shutting down of exterior system 6, as well as turning off the toilet exhausts. Note that although the data of runs

2 and 3 are relatively large, their differences are much smaller. Also, note how

little energy is used for space heating (run 1). Most of the heating and cooling

energy of a commercial building comes from cooling and reheating the circulating

air, and from conditioning the outside air.

17
Table 3. Shutdown Example — Case 9

(Run 3)

-(Run 2)

Month Run 3 Run 2

( Run 3

)

-(Run 2) Run 1 Run 4

+(Run 1 +(Run 4

Heating Energy (in 10 9 Btu)

1 1.4250 1.3201 .1049 .0168 1.8080 1.9297

2 1.2179 1.1455 .0724 .0142 1.4984 1.5850

3 .8570 .7876 .0694 .0031 1.0927 1.1652

4 .4903 .4718 .0185 .0003 .7413 .7601

5 .3971 .3970 .0001 — .6668 .6669

6 .3551 .3555 -.0004 — .5818 .5814

7 .3684 .3693 -.0009 — .5712 .5703

8 .3403 .3410 -.0007 -- .5663 .5656

9 .3914 .3918 -.0004 — .6043 .6039

10 .4773 .4713 .0060 — .7458 .7518

11 .6899 .6487 .0412 .0023 .9483 .9918

12 1.1458 1.0499 .0959 .0115 1.4016 1.5090

E 8.1554 7.7495 .4060 .0482 11.2265 11.6807

Cooling Energy (in 10 9 Btu)

1 .0316 .0429 -.0113 — .0819 .0706

2 .0348 .0443 -.0095 — .0849 .0754

3 .1521 .1699 -.0178 -- .3129 .2951

4 .4232 .4446 -.0214 — .7088 .6874

5 .8076 .8119 -.0043 — 1.2513 1.2470

6 1.2164 1.1982 .0182 — 1.8631 1.8813

7 1.7449 1.7007 .0442 __ 2.5902 2.6344

8 1.4535 1.4234 .0301 — 2.2990 2.3291

9 1.2873 1.2673 .0200 — 1.8461 1.8661

10 .5328 .5512 -.0184 — .8775 .8591

11 .2046 .2283 -.0237 — .4613 .3926

12 .0354 .0491 -.0137 — .1043 .0906

I 7.9242 7.9319 -.0076 — 12.4362 12.4287

18
4. RESULTS-DATA

The base case monthly heating and cooling energy consumptions for the interior,

north and south perimeter systems are shown in tables 4, 5, and 6. The base

case monthly heating, cooling and fan (including supply, return and exhaust

fans) energy consumptions for the entire building are shown in table 7. These

energy quantities, except for fan energy, are also plotted in figure 6. From

these tables and figure 6, some of the energy consumption characteristics of the

building may be seen, and possible opportunities for reducing energy consumption

may be assumed. Of the total building heating energy, about 74.5 percent is

consumed by the interior systems, 12.2 percent is consumed by the north systems

and 13.3 percent is used by the south systems. For cooling, the distributions

are 74.4 percent, 11.3 percent, and 14.2 percent, respectively. The large ratio

of the interior system consumption to that of the perimeter system consumption

indicates that emphasis of energy conservation controls should be placed on the

interior systems. Of the 8.732 x 10^ Btu interior heating consumption, 0.655 x

10^ Btu is spent for preheat coil load, 0.957 x 10^ Btu is used for humidifying

load, yet 7.119 x 10^ Btu is consumed by the reheat coils. This amounts to

over 80 percent (81.5 percent to be exact) of the interior heating load being

used by the reheat coils. For the whole building, over 60 percent of the entire

heating load is spent in the interior reheat coils. Part of the high interior

load is attributed to the larger interior floor areas (the ratio of interior to

perimeter floor areas is 1.4 to 1), high equipment load, and the heat needed to

raise the winter fan discharge air (around 60°F) to the space conditions; but

the pure reheat effect on the energy consumption should be examined. This is

also evident from table 4 and figure 6 that the interior system reheat energy

consumption during the summer months is over .53 x 10^ Btu per month. The

control strategy cases 12, 14, and 15 (interior system VAV conversion and reset

by zone demand) should have major impact on the overall building energy reduction.

On the other hand, cases such as 7 and 8 (perimeter reset) may not have large

effects, on overall building percentage basis.

The yearly heating and cooling energies and fan electric energies of the building

for the various control strategies are as tabulated in table 8. As described in

the previous section, the base case has a fixed outside air quantity. The supply

air temperature is set at 5/°F for the interior systems and 60°F for the perimeter

systems. Table 9 shows the normalized energy consumption for the same control

strategies as listed in table 8 using the base case yearly energy consumption as

one.

In all cases, when economy cycle control is added, either dry-bulb return air

comparison or enthalpy comparison, the cooling energy is decreased but the heating

energy is increased. The reason for the increase in heating energy is mainly due

to the added humidifying load during the time when the dry outside air is introduced into the air-handling systems. Figure 7 compares the monthly humidifying

loads for the base case and case 6 (enthalpy economizer cycle). The highest

humidifying load occurs in January, but the highest increase between the two cases occurs in March and April. Of the yearly total heating energy, 11.2 percent is

consumed by the humidifiers in the base case while 15.5 percent is used in the case with enthalpy control. Therefore, it is feasible to minimize the heating

energy increase under the economizer cycle by reducing the humidity requirements

during the non-cooling seasons.

19
Table 4. Monthly Heating and Cooling Energy for Interior Systems

Base Case

Month

Heating Energy

Btu x 10 9

Cooling Energy

Btu x 10 9

1 1.2334 .0739

2 1.0261 .0757

3 .7984 .2637

4 .6067 .5715

5 .5879 .9745

6 .5426 1.4150

7 .5436 1.9360

8 .5378 1.7190

9 .5582 1.4040

10 .6271 .6986

11 .7081 .3448

12 .9622 .0942

Yearly Total 8.7321 9.5709

Table 5. Monthly Heating & Cooling Energy for North Perimeter

Systems Base Case

Month

Heating Energy

Btu x IQ 9

Cooling Energy

Btu x 10 9

1 .3366 .0032

2 .2757 .0037

3 .1799 .0221

4 .0776 .0668

5 .0352 .1402

6 .0121 .2335

7 .0063 .3454

8 .0079 .2995

9 .0178 .2301

10 .0699 .0825

11 .1488 .0317

12 .2584 .0036

Yearly Total 1.4262 1.4583

20
Table 6. Monthly Heating & Cooling Energy for South Perimeter

Systems Base Case

Month

Heating Energy

Btu x 10 9

Cooling Energy

Btu x 10 9

1 .3543 .0053

2 .2918 .0061

3 .1901 .0321

4 .0903 .0889

5 .0530 .1772

6 .0249 .2858

7 .0190 .4165

8 .0141 .3663

9 .0259 .2844

10 .0729 .1125

11 .1534 .0253

12 .2713 .0065

Yearly Total 1.5540 1.8269

Table 7. Monthly Energy Consumption for the Building

Base Case

Month

Heating Energy

Btu x 10 9

Cooling Energy

Btu x 10 9

Fan Ener,

Btu x 10

1 1.9246 .0825 .2581

2 1.5935 .0855 .2396

3 1.1682 .3180 .2581

4 .7747 .7272 .2498

5 .6760 1.2919 .2581

6 .5796 1.9344 .2498

7 .5619 2.6976 .2581

8 .5599 2.3852 .2581

9 .6019 1.9138 .2498

10 .7703 .8936 .2581

11 1.0102 .4219 .2498

12 1.4919 .1043 .2581

Total 11.7127 12.8560 3.0455

21
COOLING

EWEStGY,

10*

Btu

HEATING

ENERGY,

10

s

iti

I 1 ~T~—I HEATING A CHUNG ENERGY CONSUMPTION BASE CASE

4 — V INTERIOR SYSTEMS

SOUTH PERIMETER SYSTEMS

A NORTH PERIMETER SYSTEMS

O ALL SYSTEMS

JULY SEPT HOV DEC

Figure 6. Heating and cooling energy consumption—base case

22
Table 8. Yearly Energy Consumption of Various Control Strategies

Cases

Heating Energy

Btu x 109 Cooling EnergyBtu x 109 Fan Energy

Btu x 109

1. Base case 11.71 12.86 3.04

2. Same as base case, except, 65°F

supply air temperature in winter

for perimeter systems 11.57 12.68 3.04

3. Dry-bulb economizer for

all systems 12.36 11.33 3.04

4. Same as 2, adding dry-bulb

economizer for all systems 12.21 11.23 3.04

5. Enthalpy economizer for

perimeter systems 11.77 12.54 3.04

6. Enthalpy economizer for

all systems 12.37 11.01 3.04

7. Perimeter system supply

air temperature reset from

outside air temperature:

65°F at 65°F , 60°F at 66°F 11.58 12.36 3.04

8. Same as 7 except,

65°F at 40°F, 60°F at 80°F 11.51 12.38 3.04

9. ACU #6 and toilet exhaust fans

off during non-office hours 11.68 12.43 2.79

10. ACU #3 and 6 off, toilet exhaust

fan off, ACU's #5 and 8 on 100 percent 0A during non-office

hours 11.62 12.43 2.52

U. ACU's #3, 6 and 8 off,

toilet exhaust fans off, ACU //5 on 100 percent OA

during non-office hours 11.88 11.87 2.32

12. Interior systems on VAV 11.15 11.32 2.48

13. Interior systems on VAV and

enthalpy economizer 11.50 10.32 2.48

14. Interior system supply air

temperature reset between

50°F and 60°F by zone demand 10.65 11.13 3.04

15. Same as 14 except 50°F-60 e F between May 1 and Sept. 30,

50°F-70°F between Oct. 1 and

April 30 10.53 10.93- 3.04

16. Same as 14, adding enthalpy

economizer for all systems 11.08 9.65 3.04

17. Same as 15, adding enthalpy

economizer for all systems 10.89 9.56 3.04

18. Perimeter system supply air

temperature reset from outside

air temperature, 65°F at 65°F,

60°F at 66°F; ACU # 6 and

exhaust fans off during non- office hours; interior system

supply air temperature reset

by zone demand, 50°F-60°F;

enthalpy economizer for all

systems 10.85 9.18 2.79

19. Same as 18, changing perimeter

system supply air temperature

reset from outside air tem- perature 65°F at 40°F and

60°F at 80°F 10.79 9.12 2.79

20. Base case with double-glazed

windows 11.42 12.83 3.04

23
Table 9. Yearly Energy Consumption Comparison of Various

Control Strategies

Cases Heating EnergyBtu x 10^

Cooling Energy

Btu x 10^ Fan EnergyBtu x lo”

1. Base case 1.00 1.00 1.00

2. Same as base case, except, 65°F

supply air temperature in winter

for perimeter systems .99 .99 1.00

3. Dry-bulb economizer for

all systems 1.06 00 00 1.00

4. Same as 2, adding dry-bulb

economizer for all systems 1.04 .87 1.00

5. Enthalpy economizer for

perimeter systems 1.01 .98 1.00

6 . Enthalpy economizer for

all systems 1.06 .86 1.00

7. Perimeter system supply

air temperature reset from

outside air temperature:

65°F at 65°F , 60°F at 66°F .99 .96 1.00

8. Same as 7 except,

65°F at 40“F, 60“F at 80"F .98 .96 1.00

9. ACU #6 and toilet exhaust fans off during non-office hours 1.00 .97 .83

10. ACU #3 and 6 off, toilet exhaust

fan off, ACU's #5 and 8 on 100 percent OA during non-office

hours .99 .97 .83

11. ACU's // 3, 6 and 8 off,

toilet exhaust fans off, ACU #5 on 100 percent 0A

during non-office hours 1.01 .92 .76

12. Interior systems on VAV .95 .88 .82

13. Interior systems on VAV and

enthalpy economizer .98 .80 •

00

14. Interior system supply air

temperature reset between

50°F and 60°F by zone demand .91 .87 1.00

15. Same as 14 except 50°F-60°F

between May 1 and Sept. 30,

50°F-70°F between Oct. 1 and

April 30 .90 .85 1.00

16. Same as 14, adding enthalpy

economizer for all systems .95 .75 1.00

17. Same as 15, adding enthalpy

economizer for all systems .93 .74 1.00

18. Perimeter system supply air

temperature reset from outside

air temperature, 65°F at 65°F,

60°F at 66°F; ACU #6 and

exhaust fans off during non- office hours; interior system

supply air temperature reset

by zone demand, 50°F-60°F;

enthalpy economizer for all

systems .93 .71 .92

19. Same as 18, changing perimeter

system supply air temperature

reset from outside air tem- perature 65°F at 40°F and

60°F at 80°F .92 .71 .92

o

CN Base case with double-glazed

windows .98 1.00 1.00

24
HUMIDIFIER

ENERGY,

10

Btu

Figure 7. Comparison of humidifer energy consumption

25
The energy reductions for the perimeter system shutdown cases (cases 9, 10, and

11, and other combinations) are smaller than one would anticipate. As discussed

in the previous section, the techniques modeled assumed the air-handling system

outside air equaled the exhaust fan capacities. This is not completely true in

reality. When some perimeter systems are turned off, the building is starved for

air, but it "balances" itself by increasing air infiltration, increasing outside

air coming into the air-handling systems, and reducing the exhaust air quantities.

Therefore, the results of cases 9, 10, 11, 18, and 19 are conservative. Without

measured data on air quantities during shutdown cases, it is difficult to judge

quantitatively the additional energy savings caused by the reduced exhaust.

Although the overall building energy reduction, in percentage, is small for the

perimeter temperature reset option, the savings on a system basis are substantial.

Table 10 shows the yearly energy consumptions of the north and south systems

and table 11 shows the percentage energy savings compared to the base case for

the north, south, and the combined systems.

Table 10. Annual Heating and Cooling Energy for Perimeter

System Supply Air Temperature Reset

North Systems South Systems

Heating Cooling Heating Cooling

IQ 9 Btu 10 9 Btu 10 9 Btu 10 9 Btu

Base Case 1.4262 1.4583 1.5540 1.8269

Case 7 Reset,

6 5°F at 65°F,

60°F at 66°F 1.3625 1.2481 1.4880 1.5392

Case 8 Reset

65°F at 40° F

,

0 O

vO at 80°F 1.3340 1.2572 1.4463 1.5570

26
Table 11. Annual Savings for Perimeter System Supply

Air Temperature Reset

North and South

North Systems South Systems Systems Combined

Heating Cooling Heating Cooling Heating Cooling

Case 7 4.5 % 14.4% 4.2% 15.7% 4.4% 15.2%

Case 8 6.5% 13.8% 6.9% 14.8% 6.7% 14.3%

Table 11 shows that over 4 percent in heating energy and over 14 percent in

cooling energy savings may be obtained by either of these temperature resets.

These savings result from shaving the unnecessary cooling capacities during the

part-load conditions to match closer to the space loads. It is interesting to

note that when the strategies are combined, the overall saving trends may not

agree with those of the individual strategies. For the perimeter system supply

air temperature reset cases, case 7 (65° at 65°F and 60°F at 66°F) saves more

than case 8 (65°F at 40°F and 60°F at 80°F) in heating but saves less in cooling. When the same resets are applied with other strategies, as in cases 18

and 19, the savings of both heating and cooling favor case 19.

It is obvious from tables 8 and 9 that installing double-glazed windows in this

building is hardly a viable retrofit option for energy conservation.

27
5. CONCLUSION

Ranking of the control strategies investigated in this report is not feasible,

since that would require the investigation of the efficiencies of the heating

and cooling plants and the fuel costs for their generation, which would go

beyond the boundaries of this building and the scope of this report (see Preface). From the individual heating, cooling, and fan energy consumptions of

this building, the following conclusions are stated:

1. All of the basic control strategies (case 20 is not considered a control

strategy) should save considerable amounts of energy, even though the

percentage of savings of some of the strategies to the total building #

. consumption are small. The costs for control strategy modifications^ tnAi f

2. Both dry-bulb and enthalpy economizer cycles are energy saving controls.

The enthalpy type has a two percent saving edge in cooling over the drybulb type. The heating energy increase caused by these controls may be

reduced, if the minimum indoor humidity requirement during the noncooling seasons is reduced.

3. The overall building energy reduction from the perimeter system supply air

temperature reset by outdoor temperature is relatively small (four percent).

4. The energy reduction from perimeter system shutdowns may save a considerable

amount of energy. The actual savings should be larger than those predicted

here.

5. The largest energy saving should be possible with the interior systems.

Resetting interior system supply air temperature by zone demand saves slightly (three percent in cooling and five percent in heating) more than

converting to VAV system, fan energy savings from VAV being ignored.

6. Annual energy savings of 0.29 x 10^ Btu in heating, 3.66 x 10^ Btu in

cooling and 0.25 x 10^ Btu in fan operation may be achieved by combining

various control strategies (case 19). This amounts to eight percent,

twenty-nine percent, and eight percent in heating, cooling and fan energy

savings, respectively, as compared to the base case.

Obviously, it must be emphasized that these conclusions are drawn from the

results for this particular laboratory building under the Washington, D.C.

weather conditions.

28
REFERENCES

1. Hoffman, J.D., "Energy Conservation at the NBS Laboratories," NBSIR 74-593,

1974.

2. Conversation with Chris Conley of NBS Plant Division, October 1980.

3. "Emergency Building Temperature Restrictions," Federal Register, Volume 44,

Number 130, Thursday, July 5, 1979, pp. 39354-39369.

4. Hittle, D.C., The Building Loads Analysis and System Thermodynamics (BLAST)

Program, Version 2.0: Users Manual, Volume I, U.S. Army Construction Engineering Research Laboratory, 1979. Available from NTIS, Springfield, VA.

22151.

29
APPENDIX

Input Data for Base Case

1 . INTRODUCTION

This appendix is presented here for the readers who are familiar with the

BLAST-2 program applications and wish to examine how the building and the airhandling system control details for the base case were handled. Specific

modelling methods and other control strategies are as described in the text.

30
m •

A

123

4

56

7B

910

1112

13

14

15

16

17

18

19

20

21

22

23

24

25

26

27

28

29

30

31

32

33

34

35

36

37

38

39

40

41

42

43

44

45

46

47

48

49

50

51

52

53

54

55

56

57

58

59

60

61

62

63

64

65

INPUT DATA

BEGIN INPUT)

RUN CONTROL?

NEW ZONES*

NEW AIR SYSTEMS?

CENTRAL PLANT?

UN ITS( IN-ENGLISH? OUT=ENGLISH)»

DEFINE LOCATION?

HASH I NG=

( LAT = 38.85? L0NG= 77.03»TZ= 5))

END LOCATION)

DEFINE DESIGN DAYS?

DD1-<HIGH-91'L0W=71?WB=77? DATK=21 JUL)

END DESIGN DAYS)

DEFINE SCHEDULE ( NBS PEOPLE)?

MONDAY THRU FRIDAY *(21 TO 5

- 9 TO 12 - 13 TO 17 - SATURDAY THRU SUNDAY =( 0 TO 24 - END SCHEDULE)

DEFINE SCHEDULE (NBS LIGHTS)?

MONDAY THRU FRIDAY =(18 TO 8

- 9 TO 18 - SATURDAY THRU SUNDAY =( 0 TO 24 - END SCHEDULE)

DEFINE SCHEDULE (NBS ELECTRIC EQUIPMENT)?

0 . 0 ? 1 . 0 ? 1 . 0 ? 0 . 0 )

0 . 2 ? 1 . 0 )

0 . 2 ) ?

. 1 »

1 '

,

2 '8 '

. 8 ?

• 6 '. 2 '. 1 '. 1 )'

HOLIDAY=SUNBAY

)

.5»

HOLIDAY=SUNDAY

MONDAY THRU FRIDAY =(18 TO 9 - 0.2'

9 TO 16 - 1 .0»0.4'0.2)

SATURDAY THRU SUNDAY =( 0 TO 24 - 0.2)' HOL I DAY=SUNDAY

)

END SCHEDULE)

DEFINE CONTROLS (GENERAL LAB)? **SA=57» REHEAT=65

PROFILES?

P7= ( 1 , 0 AT 64? 0.0 AT 65» -0.286 AT 65» -1.0 AT 85))

SCHEDULES?

SUNDAY THRU SATURDAY = (00 TO 24 - P7)» HOL I DAY=SUNDA Y

)

END CONTROLS)

DEFINE CONTROLS(CRITICAL LAB)? **SA=57» REHEAT=72

PROFILES?

P8= (1,0 AT 71.5? 0.0 AT 72' -0.536 AT 72' -1.0 AT 85))

SCHEDULES?

SUNDAY THRU SATURDAY = (00 TO 24 - PS)» HOLIDAY = SUNDAY

END CONTROLS)

DEFINE CONTROLS( OFFICE SIXTY)? «*SA*60

PROFILES?

P10=(1.0 AT 64' 0.0 AT 6§» -0,2 AT 65? -1.0 AT 85))

SCHEDULES?

SUNDAY THRU SATURDAY * (00 TO 24 - P10)» HOLIDAY=-SUNDAY

)

END CONTROLS)

DEFINE MATERIALS?

ACOUSTIC TILE=

<L=0.0625»K=0.033»D=20.0'CP=0.2)»

AIRSPACE VERT I CAL = (R=l .01 'AIR)

)

FACE BRICK=

(L=0.3229»K=0.75'D*130.0'CP=0.2)»

CONC 6-

(L=0.5000'K=1 . 0 » D=140 . 0 » CP=0 . 2 )

)

CONC 8=

(L=0,6667'K=1 «0'D*140.0'CP=0»2)

FLOOR TILE=

( R=0 . 05 )

)

GYP BOARD=

(L=0.0417»K*0.0938'D*50.0»CP*0.2)»

METAL ROOF DECK=

(L=0.0052.K*26.2'D=489.0.CP*0.12)

)

METAL WALL SKIRr

31
66 (L*0.0052fK®26.2fD"489.0fCP®0.12)!

67 HOCK EARTH RIO68 <L-1 ,0fK®0, IOOf »* 100. Op CP-O. 2)

69 MOCK EARTH THICK70 (R-IOO.O)I

71 PLATE GLASS 1-4 CLEAR®

72 (R-0.048fGLASSfTRANS-»80fVERY SMOOTH)!

73 RIGID INS 1.5=

74 (L-0«125fK®0.027fD-15.0fCP®0.17)!

75 BUILT UP ROOFING®

76 (L-0.0313fK-0.094fD-70.0fCP=0.35fVERY ROUGH)!

77 ROOF INS78 (R-8.0)!

79 VENETIAN BLIND®

80 (R=0.00004fSHADEfTRANS=0.18fABS=0.40fREF*0.42)!

81 END MATERIALS!

82 DEFINE WALLS?

83 BRICK WALL®

84 (FACE BRICKf

85 AIRSPACE VERTICALf

86 CONC 8 ? 87 AIRSPACE VERTICALf

88 METAL WALL SKIN)!

89 CONC DIAGONAL WALL®

90 (CONC 8)!

91 CURTAIN WALL INS PANEL®

92 (METAL WALL SKINf

93 RIGID INS 1 • 5

94 METAL WALL SKIN)!

95 LAB WALL®

96 (METAL WALL SKINf

97 AIRSPACE VERTICALf

98 METAL WALL SKIN)!

99 OFFICE WALL®

100 (METAL WALL SKINf

101 GYP BOARDf

102 METAL WALL SKINf

103 AIRSPACE VERTICALf

104 METAL WALL SKINf

105 GYP BOARDf

106 METAL WALL SKIN)!

107 END WALLS!

108 DEFINE ROOFS?

109 FLAT ROOF INS®

110 (BUILT UP ROOFINGf

111 ROOF INSf

112 METAL ROOF DECK)!

113 FLOOR-CEILING ATTIC®

114 (CONC 6 f 115 ACOUSTIC TILE)!

116 MIDDLE FLOOR-CEILING®

117 (FLOOR TILEf

118 CONC 6)!

119 END ROOFS!

120 DEFINE FLOORS?

121 FLOOR ATTIC®

122 (ACOUSTIC TILEf

123 CONC 6) ! 124 MIDDLE FLOOR®

125 (CONC 6

126 FLOOR TILE)!

127 INTERIOR GROUND FLOOR®

128 (MOCK EARTH THICK f 129 CONC 6)!

130 PERIMETER GROUND FLOOR®

131 (MOCK EARTH RIOf

32
132

133

134

135

136

137

136

139

140

141

142

143

144

145

146

147

148

149

150

151

152

153

154

155

156

157

158

159

160

161

162

163

164

165

166

167

168

169

170

171

172

173

174

175

176

177

178

179

180

iei

182

183

184

185

186

187

188

189

190

191

192

193

194

195

196

197

CONC 6)1

END FLOORS $ DEFINE WINDOWS?

SINGLE PANE GLASS*

< PLATE GLASS 1-4 CLEAR ; VENETIAN BLIND )

END WINDOWS;

PROJECT S 0JK47Z MBS 6P LAB AND OFFICE » BLDG 223*5

L0CATI0N=WASHXNG5

GROUND TEMPERATURES* ( 60 » 60 » 60 * 60 » 60 * 68 » 68 » 68 * 68 » 60 » 60 » 60 )

DESIGN DAYS=DD1

MWEATHER TAPE FROM 01 JAN 79 THRU 31 DEC 795

BEGIN BUILDING DESCRIPTION;

NORTH AX I S=0

ATTIC 1 *ATT I C*?

NORTH AX I S=0

EXTERIOR WALLS?

STARTING AT <383;103;0) FACING <0)

CURTAIN WALL INS PANEL <383 BY 12)

;STARTING AT <383;0;0) FACING <90)

CURTAIN WALL INS PANEL <103 BY 12)

;STARTING AT <0;0;0) FACING <180)

CURTAIN WALL INS PANEL <383 BY 12)

;STARTING AT <0;103;0> FACING <270)

CURTAIN WALL INS PANEL <103 BY 12)

; PARTITIONS?

STARTING AT <87;13;24) FACING <0)

CONC DIAGONAL WALL <87 BY 12)

;STARTING AT <87;0;24) FACING <9Q)

CONC DIAGONAL WALL <13 BY 12)

STARTING AT <383;0;C) FACING <15)

CONC DIAGONAL WALL <396 BY 12)

;STARTING AT <Q;0;0) FACING <165)

CONC DIAGONAL WALL <396 BY 12)

;STARTING AT <0;103;0) FACING <195)

CONC DIAGONAL WALL <396 BY 12)

;STARTING AT <383;103;0> FACING <345)

CONC DIAGONAL WALL <396 BY 12)

5 ROOF?

STARTING AT <0;0;12) FACING <180)

FLAT ROOF INS <383 BY 103)

; ATTIC FLOOR?

STARTING AT <0;103;0) FACING <180)

FLOOR ATTIC <383 BY 103)

5 END zone; ZONE 2 *LOWER GENERAL LABS*?

NORTH AXIS =05

LIGHTS=5.460; NBS LIGHTS;

PE0PLE = 3 . 0 ; NBS PEOPLE

ELECTRIC EQUIPMENT=4.436; NBS ELECTRIC EQUIPMENT

CONTROLS=GENERAL LAB; 1000000 HEATING; 29.321 C00LING5

PARTITIONS?

STARTING AT <11;24;0) FACING <0)

LAB W^LL .<11 BY 22.333)

33
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STARTING AT (ll'O.O) FACING <90)

LAB WALL (24 BY 22.333)

fSTARTING AT (O'O'O) FACING (180)

LAB WALL (11 BY 22.333)

STARTING AT (0»24»0) FACING (270)

LAB WALL (24 BY 22.333)

CEILING?

STARTING AT (0»0'22.333) FACING (180)

MIDDLE FLOOR-CEILING (22 BY 24)

) SLAB ON GRADE FLOOR?

STARTING AT (0'24'0) FACING (180)

INTERIOR GROUND FLOOR (11 BY 24)

) FLOOR?

STARTING AT (0»24»0> FACING (180)

MIDDLE FLOOR (11 BY 24)

) END ZONE ) ZONE 3 *UPPER GENERAL LAB*?

NORTH AXIS *0)

L IGHTS*2 . 730 » NBS LIGHTS)

PEOPLES. 5» NBS PEOPLE)

ELECTRIC EQUIPMENTS. 218' NBS ELECTRIC EQUIPMENT)

CONTROLS = GENERAL LAB » 1000000 HEATING* 14.660 COOLING)

PARTITIONS?

STARTING AT (U.24'0) FACING (0)

LAB WALL (11 BY 11.167)

STARTING AT (11»0'0) FACING (90)

LAB WALL (24 BY 11.167)

STARTING AT (O'O'O) FACING (180)

LAB WALL (11 BY 11.167)

»STARTING AT (0»24»0) FACING (270)

LAB WALL (24 BY 11.167)

) CEILING UNDER ATTIC?

STARTING AT (0»0»24) FACING (180)

FLOOR-CEILING ATTIC (11 BY 24)

) FLOOR?

STARTING AT (0»24»0) FACING (180)

MIDDLE FLOOR (11 BY 24)

) END ZONE)

ZONE 4 *LOWER CRITICAL LABS*?

SAME AS ZONE 2 EXCEPT?

CONTROLS=CRITICAL LAB' 1000000 HEATING' 29.321 COOLING)

END ZONE)

ZONE 5 *UPPER CRITICAL LAB*?

SAME AS ZONE 3 EXCEPT?

CONTROLS= CRITICAL LAB' 1000000 HEATING' 14.660 COOLING)

END ZONE)

ZONE 6 *LOWER OFFICES SIXTY SOUTH*?

NORTH AXIS =0)

LI GHTS«3 . 0 » NBS LIGHTS)

PEOPLES, 0» NBS PEOPLE)

ELECTRIC EQUIPMENTS. 3412' NBS ELECTRIC EQUIPMENT)

CONTROLSSFFICE SIXTY' 1000000 HEATING' 16.17 COOLING)

EXTERIOR WALLS?

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STARTING AT Yo»0? 6) 'FACING <180)

BRICK WALL <11 BY 22.333)

WITH WINDOWS OF TYPE

SINGLE PANE GLASS <4.5 BY 16) AT <3,2.5)

t PARTITIONS?

STARTING AT (11,0,0) FACING <90>

OFFICE WALL <23 BY 22.333)

,STARTING AT <11,23,0) FACING <0>

OFFICE WALL <11 BY 22.333)

,STARTING AT <0,23,0) FACING <270)

OFFICE WALL <23 BY 22.333)

CEILING?

STARTING AT (0,0,22.333) FACING <180)

MIDDLE FLOOR-CEILING <22 BY 23)

5 SLAB ON GRADE FLOOR?

STARTING AT (0,23,0) FACING (180)

PERIMETER GROUND FLOOR <11 BY 23)

i FLOOR?

STARTING AT <0.23>Q) FACING <180)

MIDDLE FLOOR <11 BY 23)

5 END ZONE

ZONE 7 BUPPER OFFICE SIXTY SOUTH#?

NORTH AXIS =05

L I GHTS=1 . 5 . NBS LIGHTS.

PE0PLE=1 .5. NBS PEOPLE

ELECTRIC EQUIPMENT = 0. 1706. NBS ELECTRIC EQUIPMENT

CQNTROLS=OFFICE SIXTY, 1000000 HEATING, 9.71

EXTERIOR WALLS?

STARTING AT (0,0,0) FACING <180)

BRICK WALL <11 BY 11.667)

wi rn windows of type

SINGLE PANE GLASS <4.5 BY 8) AT (3,2.5)

5 PARTITIONS?

STARTING AT (11,0,0) FACING (90)

OFFICE WALL <23 BY 11.167)

STARTING AT <11,23,0) FACING <0>

OFFICE WALL <11 BY 11.167)

STARTING AT (0,23,0) FACING (270)

OFFICE WALL (23 BY 11.167)

5 CEILING UNDER ATTIC?

STARTING AT (0,0,11.167) FACING (180)

FLOOR-CEILING ATTIC <11 BY 23)

» FLOOR?

STARTING AT <0,23,0) FACING <180)

MIDDLE FLOOR <11 BY 23)

ZONE 8 BLOWER OFFICES SIXTY NORTH*?

NORTH AXIS =1805

SAME AS ZONE 6 EXCEPT?

CONTROLS=OFFICE SIXTY, 1000000 HEATING, 11.72

END ZONE 5 ZONE 9 BUPPER OFFICE SIXTY NORTH#?

NORfU MIS.. *080J

C00LING5

COOLIN65

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SAME AS ZONE 7 EXCEPT?

CONTROLS-OFFICE SIXTY? 1000000 HEATING. 7.54 COOLINGI

END zone; END BUILDING DESCRIPTION}

BEGIN FAN SYSTEM DESCRIPTION}

VARIABLE VOLUME SYSTEM 20 ^INTERIOR 204 SERVING ZONE 2>3»4*SI

**VAV BECAUSE IT-S AN OPTION TO BE TRIED

FOR ZONE 2? *«LOUER FLOORS GENERAL PURPOSE LABS

SUPPLY AIR VOLUME* 965.13}

EXHAUST AIR VOLUME* 444.36}

REHEAT CAPACITY=1000000}

ZONE MULTIPLXER=28»

END ZONE}

FOR ZONE 3? **TOP FLOOR GENERAL PURPOSE LAB

SUPPLY AIR VOLUME* 482.57}

EXHAUST AIR VOLUME* 222.185

REHEAT CAPACXTY*1000000I

ZONE MULTIPLIER=2B5

END ZONE.

FOR ZONE 4? **LOUER FLOORS CRITICAL LABS

SUPPLY AIR VOLUME* 965.13}

EXHAUST AIR VOLUME* 444.36}

MINIMUM AIR FRACTION*! .0}

REHEAT CAPACITY*1000000}

ZONE MULTIPLIER=32}

END ZONE}

FOR ZONE 5? **TOP FLOOR CRITICAL LAB

SUPPLY AIR VOLUME* 482.57}

EXHAUST AIR VOLUME* 222.18}

MINIMUM AIR FRACTIONS .0}

REHEAT CAPACITY-100000©}

ZONE MULT1PLIER=32»

END ZONE}

OTHER SYSTEM PARAMETERS?

HUMIDISTAT L0CATI0N=4}

MIXED AIR CONTROL*FIXED PERCENT}

HOT DECK TEMPERATURE* 1000.0}

COLD DECK TEMPERATURE *57 . 0}

COLD DECK THROTTLING RANGE-1.01

SUPPLY FAN PRESSURE* 3.0}

EXHAUST FAN PRESSURE*© .5}

RETURN FAN PRESSURE* 1.25}

SUPPLY FAN EFFICIENCY* 0.75}

EXHAUST FAN EFF IC IENCY*0 . 50

}

RETURN FAN EFFICIENCY* 0.70}

HUMIDIFIER TYPE-STEAM}

HUMIDISTAT SET POINT-30}

PREHEAT COIL LOCATION-MIXED AIR DUCT}

PREHEAT COIL CAPACITY-1000000}

PREHEAT ENERGY SUPPLY*STEAM

}

WEEKDAY MINIMUM OUTSIDE AIR SCHEDULE*(0 TO 24 - 0.0)}

WEEKEND MINIMUM OUTSIDE AIR SCHEDULE*(0 TO 24 - 0.0)}

VAV MINIMUM AIR FRACTION-1 .0} **CONSTANT VOLUME

VAV VOLUME CONTROL TYPE-INLET VANES}

END OTHER SYSTEM PARAMETERS}

EQUIPMENT SCHEDULES?

SYSTEM OPERATION-INTERMITTENT}

WEEKDAY SYSTEM SCHEDULE=<7 TO 18 - 1? 18 TO 7 - 1)}

WEEKEND SYSTEM SCHEDULED© TO 24 - 1)1

END EQUIPMENT SCHEDULES}

COOLING COIL DESIGN PARAMETERS?

AIR VOLUME FLOW RATE-86862}

WATER VOLUME FLOW RATE-77.107}

ENTERING AIR DRY BULB TEMPERATURE-85}

ENTERING AIR WET BULB TEMPERATURE *64

}

ENTERING WATER TEMPERATURE-42}

36
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461

LEAVING AIR DRY BULB TEMPERATURE-545

LEAVING AIR WET BULB TEMPERATURE-53.31

LEAVING WATER TEMPERATURE-54

BAROMETRIC PRESSURE-405 5 AIR FACE VELOCITY-360!

WATER VELOCITY-275*

END COOLING COIL DESIGN PARAMETERS*

END SYSTEM * VARIABLE VOLUME SYSTEM 3 4S0UTH EXTERIOR 3# SERVING ZONE 6»75

FOR ZONE 6? f SLOWER FLOORS

SUPPLY AIR VOLUME- 596*

EXHAUST AIR VOLUME- 2465

REHEAT CAPACITY-10000005

ZONE MULTIPLIER-125

END ZONE 5 FOR ZONE 7? SSTOP FLOOR

SUPPLY AIR VOLUME- 3585

EXHAUST AIR VOLUME- 1485

REHEAT CAPACITY-10000005

ZONE MULTIPLIER-125

END ZONE

OTHER SYSTEM PARAMETERS?

HUMIDJSTAT LOCATION-65

MIXED AIR CONTROL-FIXED PERCENT 5 COLD DECK TEMPERATURE-60,05

COLD DECK THROTTLING RANGE-1.05

SUPPLY FAN PRESSURE- 3.05

EXHAUST FAN PRESSURE-0.55

RETURN FAN PRESSURE- 1.255

SUPPLY FAN EFFICIENCY- 0,755

EXHAUST FAN EFFICIENCY-0.505

RETURN FAN EFFICIENCY- 0.705

HUMIDIFIER TYPE-STEAM

HUMIDISTAT SET POINT-305

PREHEAT COIL LOCATION-MIXED AIR DUCT 5 PREHEAT COIL CAPACITY-10000005

PREHEAT ENERGY SUPPLY-STEAM

WEEKDAY MINIMUM OUTSIDE AIR SCHEBULE=<0 TO 24 - 0.0)5

WEEKEND MINIMUM OUTSIDE AIR SCHEDULE- (0 TO 24 - 0.0)5

VAV MINIMUM AIR FRACTION-1 . 00

VAV VOLUME CONTROL TYPE-INLET VANES!

END OTHER SYSTEM PARAMETERS 5 EQUIPMENT SCHEDULES?

SYSTEM OPER AT I OH -INTERMITTENT I WEEKDAY SYSTEM SCHEDULE- <7 TO 18 - 1» 18 TO 7 - 1H

WEEKEND SYSTEM SCHEDULE® ( ® TO 24 - 1)5

END EQUIPMENT SCHEDULES*

COOLING COIL DESIGN PARAMETERS?

AIR VOLUME FLOW RATE-114485

WATER VOLUME FLOW RATE-10.1625

ENTERING AIR DRY BULB TEMPERATURE- 85

ENTERING AIR WET BULB TEMPERATUfte-64

ENTERING WATER TEMPERATURE-425

LEAVING AIR DRY BULB TEMPERATURE -54 5 LEAVING AIR WET BULB TEMPERATURE-53.35

LEAVING WATER TEMPERATURE =T>45 BAROMETRIC PRESSURE-4055

AIR FACE VELOCITY-3605

WATER VELOCITY-2755

END COOLING COIL DESIGN PARAMETERS*

END SYSTEM*

VARIABLE VOLUME SYSTEM 5 4S0UTH EXTERIOR 54 SERVING ZONE 6»75

FOR ZONE 6?

SUPPLY AIR VOLUME- 5965

EXHAUST AIR VOLUME- 2465

REHEAT CAPACITY=1 000000 5

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511

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513

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515

516

517

518

519

520

521

522

523

524

525

526

.527

ZONE. MULTIPLIER®!®!

END ZONE}

FOR ZONE 7?

SUPPLY AIR VOLUME* 3581

EXHAUST AIR VOLUME® 148}

REHEAT CAPACITY*100Q00Q}

ZONE MULTIPLIER*!®}

END ZONE!

OTHER SYSTEM PARAMETERS?

HUMIDISTAT L0CATIQN=6}

MIXED AIR CONTROL=FIXED PERCENT}

COLD DECK TEMPERATURE=60.0}

COLD DECK THROTTLING RANGE*!.©}

SUPPLY FAN PRESSURE® 3.0}

EXHAUST FAN PRESSURE*© . 5

}

RETURN FAN PRESSURE® 1.25}

SUPPLY FAN EFFICIENCY* 0.75}

EXHAUST FAN EFFICIENCY*©. 50}

RETURN FAN EFFICIENCY® 0.701

HUMIDIFIER TYPE=STEAM

}

HUMIDISTAT SET P0INT=3©}

PREHEAT COIL LOCATION=MIXED AIR DUCT}

PREHEAT COIL CAPACITY*100000©}

PREHEAT ENERGY SUPPL Y=STEAM

}

WEEKDAY MINIMUM OUTSIDE AIR SCHEDULE=(0 TO 24 - 0.0)}

WEEKEND MINIMUM OUTSIDE AIR SCHEDULE* < 0 TO 24 - 0.0)}

VAV MINIMUM AIR FRACT ION* 1 . 00

}

VAV VOLUME CONTROL TYPE*INLET VANES}

END OTHER SYSTEM PARAMETERS}

EQUIPMENT SCHEDULES?

SYSTEM OPERATION* INTERMITTENT}

WEEKDAY SYSTEM SCHEDULE=<7 TO 18 - It 18 TO 7 - 1)}

WEEKEND SYSTEM SCHEDULE*(0 TO 24 - 1)}

END EQUIPMENT SCHEDULES}

COOLING COIL DESIGN PARAMETERS?

AIR VOLUME FLOW RATE*1431©}

WATER VOLUME FLOW RATE*12.703}

ENTERING AIR DRY BULB TEMPERATURE *85

ENTERING AIR WET BULB TEMPERATURE-64

}

ENTERING WATER TEMPERATURE* 42

}

LEAVING AIR DRY BULB TEMPERATURE® 54

}

LEAVING AIR WET BULB TEHPERATURE»53 . 3

LEAVING WATER TEMPER ATURE*54

BAROMETRIC PRESSURE*405

}

AIR FACE VELQCITY*36©}

WATER VE10CITY*275}

END COOLING COIL DESIGN PARAMETERS}

END SYSTEM}

VARIABLE VOLUME SYSTEM 6 #NQRTH EXTERIOR 6* SERVING ZONE 8t9}

FOR ZONE 8?

SUPPLY AIR VOLUME* 432} • *. EXHAUST AIR VOLUME* 189}

REHEAT CAPACITY®1000000}

ZONE MULTIPLIER*16t

END ZONE}

FOR ZONE 9?

SUPPLY AIR VOLUME* 2781

EXHAUST AIR VOLUME® 122}

REHEAT CAPACITY®!©©©©©©}

ZONE MULT I PL I ER® 1 5

END ZONE}

OTHER SYSTEM PARAMETERS?

HUMIDISTAT L0CATI0N®8}

MIXED AIR CONTROL*FIXED PERCENT}

COLD DECK TEMPERATURE®60.0}

ILIMS-JSAKBf

38
528

529

530

531

532

533

534

535

536

537

538

539

540

541

542

543

544

545

546

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548

549

550

551

552

553

554

555

556

557

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560

561

562

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570

571

572

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576

577

578

579

580

581

582

583

584

585

586

587

588

589

590

591

592

593

SUPPLY FAN PRESSURE* 3,0)

EXHAUST FAN PRESSURE-0 .5 I RETURN FAN PRESSURE* 1.251

SUPPLY FAN EFFICIENCY* 0.755

EXHAUST FAN EFFICIENCY-0 .50

RETURN FAN EFFICIENCY* 0.705

HUMIDIFIER TYPE-3TEAN5

HUMIDISTAT SET PGXNT-305

PREHEAT COIL LOCATION-MIXED AIR DUCT I PREHEAT COIL CAPACITY-10000005

PREHEAT ENERGY SUPPLY*STEAM

WEEKDAY MINIMUM OUTSIDE AIR SCHEDULE*(0 TO 24 - 0.0)5

WEEKEND MINIMUM OUTSIDE AIR SCHEDULE*(0 TO 24 - 0.0)5

VAV MINIMUM AIR FRACT I ON* 1 . 00

VAV VOLUME CONTROL TYPE-INLET VANES

END OTHER SYSTEM PARAMETERS5

EQUIPMENT SCHEDULES?

SYSTEM OPERATION -INTERMITTENT

WEEKDAY SYSTEM SCHEDULE=<7 TO 18 - 1 » 18 TO 7- 1)5

WEEKEND SYSTEM SCHEDULE-10 TO 24 - 1)5

END EQUIPMENT SCHEDULES 5 COOLING COIL DESIGN PARAMETERS?

AIR VOLUME FLOW RATE-110825

WATER VOLUME FLOW RATE- 9.8375

ENTERING AIR DRY BULB TEMPERATURE-855

ENTERING AIR WET BULB TEMPERATURE-645

ENTERING WATER TEMPERATURE-425

LEAVING AIR DRY BULB TEMPERATURE “54 5 LEAVING AIR WET BULB TEMPERATURE-53.35

LEAVING WATER TEMPERATURE-545

BAROMETRIC PRESSURE-4055

AIR FACE VELOCITY-3605

WATER VELOCITY-2755

END COOLING COIL DESIGN PARAMETERS

END SYSTEM 5 VARIABLE VOLUME SYSTEM 8 #NORTH EXTERIOR 8# SERVING ZONE 8*95

FOR ZONE 8?

SUPPLY AIR VOLUME- 4325

EXHAUST AIR VOLUME- 1895

REHEAT CAPACITY-10000005

ZONE MULTIPLIER-135

END ZONE 5 FOR ZONE 9?

SUPPLY AIR VOLUME- 2785

EXHAUST AIR VOLUME- 1225

REHEAT CAPACITY-10000005

ZONE MULTIPLIER-125

END ZONE 5 OTHER SYSTEM PARAMETERS?

HUMIDISTAT LOCATION-85

MIXED AIR CONTROL-FIXED PERCENT*

COLD DECK TEMPERATURE-60.05

COLD DECK THROTTLING RANGE-1.05

SUPPLY FAN PRESSURE- 3.05

EXHAUST FAN PRESSURE-0.55 - RETURN FAN PRESSURE- 1.255

SUPPLY FAN EFFICIENCY- 0.755

EXHAUST FAN EFFICIENCY-0.505

RETURN FAN EFFICIENCY- 0.705

HUMIDIFIER TYPE-STEAM 5 HUMIDISTAT SET POINT-305

PREHEAT COIL LOCATION-MIXED AIR DUCT

PREHEAT COIL CAPACITY-10000001

PREHEAT ENERGY SUPPLY-STEAM5

WEEKDAY MINIMUM OUTSIDE AIR SCHEDULEMO TO 24 - 0.0)5

WE EKEND M INI MUM OUTSIDE AIR SCHEDULE-(Q TO 24 - 0.0 )_5

39
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595

596

597

598

599

600

601

602

603

604

605

606

607

608

609

610

611

612

613

614

615

616

617

618

619

620

621

622

623

624

625

VAV MINIMUM AIR FRACTION*! >001

VAV VOLUME CONTROL TYPE® INLET VANES*

END OTHER SYSTEM PARAMETERS

EQUIPMENT SCHEDULES?

SYSTEM OPERATION® INTERMITTENT!

WEEKDAY SYSTEM SCHEDULE«<7 TO 18 - 1* 18 TO 7 - 1>!

WEEKEND SYSTEM SCHEDULE-<0 TO 24 - 1)1

END EQUIPMENT SCHEDULES!

COOLING COIL DESIGN PARAMETERS?

AIR VOLUME FLOW RATE®10290!

WATER VOLUME FLOW RATE® 9.134!

ENTERING AIR DRY BULB TEMPERATURE *85

ENTERING AIR WET BULB TEMPER AT URE*64 J ENTERING WATER TEMPERATURE*42!

LEAVING AIR DRY BULB TEMPERATURE=54!

LEAVING AIR WET BULB TEMPERATURE *53 . 3

LEAVING WATER TEMPERATURE*54f

BAROMETRIC PRESSURE®405

AIR FACE VELOC I T Y=360

WATER VELOC I T Y=275

END COOLING COIL DESIGN PARAMETERS!

END SYSTEM!

END FAN SYSTEM DESCRIPTION!

BEGIN CENTRAL PLANT DESCRIPTION!

PLANT 1 4PLANT 1# SERVING SYSTEMS 3»5. 6*8*20!

EQUIPMENT SELECTION?

1 BOILER OF SIZE 5200.0!

1 CHILLER OF SIZE 6800.0!

END EQUIPMENT SELECTION!

END PLANT!

END CENTRAL PLANT DESCRIPTION!

END INPUT!

40
-80 ) U.S. DEPT. OF COMM. 1. PUBLICATION OR 2. Performing Organ. Report NoJ 3. Publication Date BIBLIOGRAPHIC DATA

REPORT NO.

June 1961 SHEET (See instructions) NBSIR 81-2277

4. TITLE AND SUBTITLE

Control Strategies for Energy Conservation, A Case Study of the Materials

Building, National Bureau of Standards

-J

5. AUTHOR(S)

James Y. Kao and E. Thomas Pierce

6. PERFORMING ORGANIZATION (If joint or other than NBS, see instructions) 7. Contract/Grant No. NATIONAL BUREAU OF STANDARDS

DEPARTMENT OF COMMERCE 8. Type of Report & Period Covered

WASHINGTON, D.C. 20234

Final

9. SPONSORING ORGANIZATION NAME AND COMPLETE ADDRESS (Street. City, State , ZIP)

Plant Division

Office of the Director of Administrative and Information Systems

National Bureau of Standards

Washington, D.C. 20234

10. SUPPLEMENTARY NOTES

| | Document describes a computer program; SF-185, FIPS Software Summary, is attached.

11. ABSTRACT (A 200-word or less factual summary of most significant information. If document includes a significant

bibliography or literature survey, mention it here)

The BLAST-2 Computer Program is used to investigate various heating, ventilating

and air conditioning control strategies and their combinations to reduce the

energy consumption of a laboratory building located at the National Bureau of

Standards, Gaithersburg site. The techniques of modeling the building load and

air system performance are explained. The results are presented and discussed.

Control strategies investigated include dry-bulb and enthalpy economizer cycles,

resetting supply air temperatures by outside temperature and zone demand, shutdown of fan systems selectively, and converting interior systems to VAV systems.

By combining the various control strategies, eight percent, twenty-nine percent

and eight percent of heating, cooling and fan energy respectively may be saved.

12. KEY WORDS (Six to twelve entries; alphabetical order; capitalize only proper names; and separate key words by semicolons)

,-Building energy analysis, computer modeling, controls, control strategies, energy

conservation for non—residential buildings, load calculations.

13. AVAILABILITY 14. NO. OF

PRINTED PAGES

fx~l Unlimited

[ | For Official Distribution. Do Not Release to NTIS 115

f—1 Order From Superintendent of Documents, U.S. Government Printing Office, Washington, D.C.

20402. 15. Price

Order From National Technical Information Service (NTIS), Springfield, VA. 22161 $11.00

USCOMM-DC 6043-P 80
, mmtm