-‘

 

\ w,“

 

 

. V““““v"~‘-" I'lfllgl’h;““ "H. ‘."'I.:'I?'4I'I‘. ', I" ' '. II. I I ,I . . I— . ,‘r-L-u I. .
$3.15,...“ -‘,,~I«-III«AI,\|~I‘I‘(VI Ara-AI .-."\:/.';.‘: I" I .-""'.‘.‘.\' I, .l . J. I I: ' I. N‘- r ’1 r. .W ‘ ' ‘ ‘

A SYSTEMS ANALYSIS OF SUMMER V _ , ‘
ENVIRONMENT FOR LAYING .IIENS ' ‘~ *

Thesis for the Degree of Ph, D.‘
MICHIGAN STATE UNIVERSITY
’ RICHARD EARL PHILLIPS

f .1970 ’

.HESI.
".;;'hw—.‘”
, f k ‘ ‘ .. .
‘ f5. ‘; ‘3!”
¢.. _ _,_ I \ ,'.
V
I
I v_ " '
\‘l '
-l I".‘. .' -.’
”Id-u .- - - “
',.
t ' ‘* ..
. ..-....Ew.u«~~i
"2A A «

This is to certify that the
thesis entitled

A SYSI‘EMS ANALYSIS OF SUMMER
ENVIRONMENI' FOR LAYING HENS

presented by

RICHARD EARL PHILLIPS

has been accepted towards fulfillment
of the requirements for

Mdegree inflame]. Engineering

K, Major professW

Date 7/25I/7O
/ /

 

0-169

ABSTRACT

A SYSTEMS ANALYSIS OF SUMMER
ENVIRONMENT FOR LAYING HENS

BY

Richard Earl Phillips

The objective of this study was to apply the systems
approach to the analysis of summer environment for laying
hens and to develop a simulation model which could be
used in the study of parameters affecting the environment.

The system was defined as the environment surrounding
the laying bird and enclosed by the inner surfaces of the
containing structure. A mathematical model was then
developed to predict system temperature and humidity as
a function of heat and mass transfer rates across system
boundaries at discreet time points located at half hour
intervals throughout the day. Items evaluated by the model
included bird heat production, heat transfer through struc—
tural components, electrical heat production, and heat and
moisture exchange with ventilating air. Evaporation of
free moisture from the manure surface was evaluated using
a routine based on the Reynolds analogy for mass transfer

in turbulent flow over a flat plate.

Richard Earl Phillips

Model performance was verified in a series of 22 one-
day tests in a research caged laying house located at the
Michigan State University Poultry Science Research and
Teaching Center. Mean deviations between actual and pre-
dicted system conditions over the 22 runs were 1.9 degrees
F for temperature and 5.1 percent for relative humitity.
Deviations were largely attributable to two factors. First,
the model used two discreet functions for night and day
bird heat production without transitional values. Second,
the model responded instantaneously to rapid changes in
interior or exterior conditions while actual system response
appeared to be buffered by structural or physiological
effects. A significant finding during these tests was that
the floor slab, largely ignored in previous research and
analysis, plays a major role in the determination of system
conditions.

Simulation studies were made using a hypothetical
commercial sized production unit to evaluate the effects
of different ventilation and management practices on system
performance. Items investigated included ventilation rates,
housing density, phase shifting between artificial and
natural day periods, and a logic based ventilation control
system. Conclusions from these studies included the
following:

1. Ventilation rates in excess of 4.5 cfm/bird

(l cfm/lb of body weight) do not significantly

reduce peak temperatures in the system. Higher

Richard Earl Phillips

ventilation rates can increase daily
temperature range by lowering minimum
temperatures experienced during night

time hours.

Housing densities between .7 and 1.7 square
feet per bird did not have a significant
effect on the diurnal temperature cycle of
the system when using an occupancy based
ventilation rate.

Changing the phase relationship between
artificial and natural day can moderate
system temperature extremes; however,

this is done at the expense of reducing
the daily range.

The logic based control system using
differential temperature sensing as a
basis for ventilation rate regulation
provides a means of increasing daily
temperature range and reducing operating

costs.

Approved mJZ/L/é i)

Majhr Professor

Approved (2 gig W

Department Chairman

A SYSTEMS ANALYSIS OF SUMMER

ENVIRONMENT FOR LAYING HENS

BY

Richard Earl Phillips

A THESIS

Submitted to
Michigan State University
in partial fulfillment of the requirements
for the degree of

DOCTOR OF PHILOSOPHY

Department of Agricultural Engineering

1970

(~97 2 '5 3"

ACKNOWLEDGEMENTS

The author wishes to express his appreciation and
thanks to the following persons and institutions for the
help which made this study possible.

To Dr. M. L. Esmay, committee chairman, Dr. C. C.
Sheppard, Dr. T. J. Manetsch, and Dr. J. B. Holtman who
served as members of his guidance committee.

To the Agricultural Engineering and Poultry Science
Departments at Michigan State University for providing
financial support and physical facilities used in this
research.

To the University of Connecticut for providing a
sabbatic leave in order that the author be able to under-
take graduate study.

To his wife and family who willingly exchanged the
security of established home and community roles for the
frustrations often attendant to the completion of a

graduate program.

ii

TABLE OF CONTENTS

ACKNOWLEDGEMENTS . . . . . . .

LIST OF TABLES . . . . . . . .

LIST OF FIGURES . . . . . . . .

Chapter
1. INTRODUCTION . . . . . . .
2. MODEL DEVELOPMENT . . . . . .
2.1 System Definition and General Hypothesis
2.2 Generation of External Environmental
Conditions . . . . .
2.3 Bird Heat Production . .
2.4 Electrical Heat Production Within
the System . . . . .
2.5 Wall and Ceiling Heat Exchange
2.6 Floor Slab Effects . . .
2.7 Ventilation and Evaporation
2.8 Computer Program Outline .
3. MODEL VERIFICATION . . . . .
3.1 Facilities and Equipment .
3.2 Experimental Procedure . .
3.3 Results and Discussion . .
4. SIMULATION STUDIES . . . . .
4.1 Values Common to All Studies
4.2 Ventilation Rates . . .
4.3 Density Effects . . . .
4.4 Variations in Artificial Da
4.5 Logic Based Ventilation Control
5. CONCLUSIONS . . . . . . . .

iii

Page

ii

vi

UIU'IH

Chapter Page
6. RECOMMENDATIONS FOR FUTURE WORK . . . . . . . 73
REFERENCES . . . . . . . . . . . . . . . 75
APPENDICES . . . . . . . . . . . . . . . 80

Appendix A . . . . . . . . . . . . . 81
Appendix B . . . . . . . . . . . . . 92

iv

Table

LIST OF TABLES

Page
Total incident solar radiation on a plane
normal to the sun as a function of solar
altitude . . . . . . . . . . . . . 12

Solar altitude at 42 degrees North latitude
for July . . . . . . . . . . . . . 12

Heat production at various levels of ambient
temperature for S.C. White Leghorn hens . . . l4

Thermocouple locations in test pen . . . . . 31
Summary of experimental runs . . . . . . . 33

Effect of various levels of constant
ventilation on system temperatures . . . . . 50

Effect of housing density on system
temperatures . . . . . . . . . . . . 55

Effect of different "days" on system
temperatures . . . . . . . . . . . . 6O

Figure

3.1

3.2

3.3

3.4

3.5

3.6

3.7

3.8

4.1

4.2

LIST OF FIGURES

Floor plan of pen used in verification
studies . . . . . . . . . . . .

Outside, inside, and predicted inside
temperatures for run 6 . . . . . . .

Outside, inside, and predicted inside
temperatures for run 8 . . . . . . .

Outside, inside, and predicted inside
temperatures for run 12 . . . . . .

Outside, inside, and predicted inside
temperatures for run 14 . . . . . .

Outside, inside, and predicted inside
temperatures for run 18 . . . . . .

Outside, inside, and predicted inside
temperatures for run 19 . . . . . .

Outside, inside, and predicted inside
temperatures for run 25 . . . . . .

Effect of different constant ventilation
rates on interior temperature-~normal
outside temperatures . . . . . . .

Effect of different constant ventilation
rates on interior temperatures--extreme
outside temperatures . . . . . . .

Effect of housing density on interior
temperatures-~normal outside temperatures

Effect of housing density on interior
temperatures-~extreme outside temperatures

Effect of different artificial day periods

on interior temperatures--normal outside
temperatures . . . . . . . . . .

vi

Page

29

37

38

39

4O

41

42

43

51

52

56

57

61

Figure Page

4.6 Effect of different artificial day periods
on interior temperatures--extreme
outside temperatures . . . . . . . . . 62

4.7 Flow chart for logic based ventilation
contr01 O O O O O O O O O O O O O O 66

4.8 Interior temperature profile using logic
based ventilation control--normal outside
temperatures . . . . . . . . . . . . 67

4.9 Interior temperature profile using logic

based ventilation system--extreme outside
temperatures . . . . . . . . . . . . 68

vii

1. INTRODUCTION

Maximum efficiency in egg production is achieved in
an environment which provides ambient temperature in the
range of 55-60 degrees F (Longhouse g£_gl,, 1960). The
currently popular windowless housing structure is able
to contain this desired environment during winter months
through a combination of thermal barriers to reduce sensible
heat losses and temperature regulated mechanical ventila-
tion systems which serve the dual purpose of introducing
fresh air and removing excess water. During summer
months, outside temperature frequently exceeds the desired
range and increased ventilation is not able to provide
Optimum conditions for most efficient production.

Traditionally, the design of environmental control
systems for poultry structures has involved assignment of
desired interior conditions, arbitrary selection of maxi-
mum, minimum, or mean exterior design conditions, and the
application of classical steady state heat and mass trans-
fer relationships to establish a thermal and moisture

balance. The number of calculations involved has in most

cases limited the designer to only a few possible combi-
nations of building design factors and management systems.
During winter months, when interior conditions can be held
at desired levels through varying ventilation rates, the
steady state analysis has provided a useful tool for
environmental design. As an aid to designing for summer
conditions, it has two major deficiencies: first” the
thermal capacitance of the structural components tend to
exert a moderating influence on environmental extremes

and to both delay and prolong their effect on interior
environment. The effect of this thermal capacitance on
air conditioning loads was studied by Livermore (1943).
Leopold (1948) developed a hydraulic analogue for solu-
tion of heat storage problems in air conditioned struc-
tures and indicated that cooling of components is due
largely to convective heat transfer and occurs at a
slower rate than heating where radiant transfer is pre-
dominant.

The second major problem in steady state analysis
during summer is the fact that bird heat production is
temperature dependent. Ota and McNally (1961) in calorimter
studies found that, although heat production is relatively
constant in the thermoneutral range, there is a decrease
in sensible heat and an increase in latent heat production
with increases in ambient temperature above this range.

Esmay §E_al., (1966) used the data of Ota and McNally

in a study of the psychrometrics of air exchange in

commercial egg production units during hot summer days and
noted increased levels of latent heat production at higher
outside temperatures. Reece and Deaton (1969) studied
sensible and latent heat production of growing birds on

a whole house basis and discovered important diurnal varia-
tions in sensible heat removal from the structure which
they attributed to 1) reduced bird heat production at high
ambient temperatures, 2) use of floor and litter as a
temporary heat sink during hot periods, and 3) use of
sensible heat to evaporate free moisture in the structure
during periods of lowered outside relative humidity. It
was also suggested that sensible heat alone is not a sat-
isfactory predictor of maximum interior temperatures.

It is apparent that steady state techniques are not
completely satisfactory in the analysis of structural
environment under diurnally varying conditions. This is
particularly true during summer months when conventionally
used control systems are not able to eliminate large
variations in internal conditions. Jordan and Barwick
(1965) developed an electrical analog model to study farm
building construction and ventilation effects. They
reported that the model provides a more meaningful pre-
diction of building response than steady state calcula-
tions do. The role of the floor slab as a temporary heat
sink was not, however, fully developed in the model and

constant heat production within the structure was assumed.

Stewart (1969) pointed out some of the deficiencies
in present environmental design analysis methods and
suggested the application of the systems approach to the
study of environment. He also listed some of the para-
meters he felt will be of importance in future design
work.

This research project was directed towards the appli-
cations of the systems approach to the analysis of tempera-
ture and moisture conditions inside a closed egg production
structure during summer months. A mathematical model was
developed to predict interior temperatures and relative
humidities throughout the day as a function of external
environment, type of construction, and management prac-
tices.

Field studies were conducted to verify model per—
formance. Simulation runs were made using a digital com-
puter to investigate effects of variations in management
and environmental control practices on internal environ-

ment.

2. MODEL DEVELOPMENT

2.1 System Definition and General Hypothesis

Stewart (1969) defined a system as "a recognizable
entity which accomplishes a process." A system is made
up of physical and/or biological parts encompassed by
some definable boundaries across which system inputs and
responses can be viewed and analyzed.

The system defined by this research is the environ-
ment surrounding the laying hen and enclosed by the interior
surfaces of the housing unit which contains her. Inputs to
the system considered to be of importance in this study
were heat and moisture. Outputs were changes in system
temperature and relative humidity.

The system was dynamic and digital computer techni-
ques require discreet time points for analysis. It was
therefore decided to View the environment at half-hour
intervals throughout the day. The assumption was made
that there was no net heat flow across the system boundry
at these discreet time points. Net heat flow was defined

as follows:

Q _ _
net — O — Qb + Qe + Qw + Qc + Qf + Qv

where:
Qnet = net heat flow across system boundries
Qb = heat added to system by birds
Qe = heat added by electrical usage in the building
Qw = heat flow through building walls
QC = heat flow through ceiling
Qf = heat flow through floor
Q = heat removed by ventilation system

If we define occupancy, management practices, con-
struction, and exterior conditions, all of the independent
variables except electrical heat in the above equation
become functions of system temperature. It is then possi-
ble to use approximation techniques to solve for system
temperature. Newton's method of successive approximations
was used in the model to converge on a temperature. This

method is mathematically represented as

f(t )
tn+1 = tn ' swip-
where:
tn+1 = new approximation to the solution
tn = previous approximation value
f(tn) = net heat flow across system boundries
at temperature tn
f'(tn) = first derivitive of f(tn) which was

determined by the following central

finite difference approximation

(f(tn+ - f(tn-.l))

.2

l
. _ .1
f (tn) -

Additional assumptions inherent in the model design
are listed below:

1. Single storied windowless construction with
concrete floor slab on grade;

2. Caged laying confinement system with manure
dropping areas below the cages;

3. Mechanical ventilation system consisting
of controlled exhaust fans and fresh air
slot inlets; and

4. Solar radiation effects do not make signi-
ficant contributions to wall heat exchange
because of roof overhangs which shade the
wall areas for a considerable portion of

the day.

2.2 Generation of External Environmental Conditions
Diurnal dry bulb temperature behavior can be closely

approximated by a sinusoidal function with amplitude vary-
ing equally about the daily mean temperature. Minimum
daily temperature was expected at approximately 6:00 a.m.
and maximum about 3:00 p.m. during July in Michigan. Con—
sidering time as the number of half-hour periods elapsed
since midnight, the following three equations were developed
to generate dry-bulb temperature as a function of minimum

daily temperature and expected range:

for 12:30 a.m. to 6:00 a.m.

. _ t .
tdb(l) ‘ tmin+ §br(1 + cos ($§%—l§)H)

 

for 6:30 a.m. to 3:00 p.m.

(1-cos(i—§§33)H)

 

tdb
i) t . + r

tdb( ‘ mln 2

for 3:00 p.m. to midnight

 

 

tdei) = Emin+t§brI1 + cos (i—§539)R)
where

tdb(i) = dry-bulb temperature at time = i half
hours after midnight (deg F)

tmin = minimum temperature expected = daily
average - gbr (deg F)

tdbr = expected daily range in temperature (deg F)

H = 3.14

All simulations were for July when the expected mean
temperature for Lansing, Michigan was 72 degrees F and the
daily range was 23 degrees F.

The ASAE Yearbook (1970) indicated that the mean
daily wet-bulb depression for the Lansing area was approx-
imately 8 degrees F for the month of July. This mean
depression was used in conjunction with the mean dry-bulb
temperature to establish an assumed constant dew point
temperature. Dew-point and dry-bulb temperatures were then
used in a modified version of the PSYCRO subroutine des-
cribed below to arrive at a spectrum of wet-bulb tempera-

tures for the day.

Brooker (1966) presented a series of mathematical
equations which can be used to mathematically determine
all the psychrometric properties of air, from any two
known properties. These equations were developed into a
subroutine called PSYCRO for use in the model. Given the
values for wet and dry-bulb temperatures in degrees F,
PSYCRO returns all the other properties of air required
for subsequent calculations.

Solar radiation effects were incorporated through
development of a sol-air temperature spectrum for the day.
Sol-air temperature is a fictitious ambient temperature
used to represent the total effects of ambient temperature
and solar radiation in the analysis of structural heat
transfer problems. As proposed by Mackey and Wright

(1944), Sol-air temperature is

t... = t. + 21
c
where:
tsa = sol-air temperature (deg F)
ta = dry bulb temperature (deg F)
b = solar absorptivity of surface
I = intensity of solar radiation (BTU/hour
(Sq Ft))

fc = film coefficient of heat transfer (BTU/hour

(Sq Ft) (deg F))
The major weakness in the sol-air temperature calcu-

lation.as presented above is the fact that it makes no

10

attempt to account for surface radiation from the building
to the sky or adjacent structures during night hours. This
is not of serious consequence for commercial structures
which have relatively small surface area per unit floor
area; however, it should be considered in agricultural
structures where the surface to floor area ratio usually
exceeds 1.0. Parmelee and Aubele (1952) presented the
following modification which provides a sol-air temperature

that does consider night time emissions of radiant heat

t'sa = [(aI — eAR)/(hco + h'r)] + tdb
where
t'sa = modified sol-air temperature (deg F)
a = surface absorptivity
e = surface emissivity
AR = difference between black body radiation

at ambient air temperature and radiation
received by a horizontal surface

hCO = outdoor surface convection coefficient
(BTU/hour(Sq Ft)(deg F))

I = total incident solar radiation (BTU/hour
(Sq Ft))

tdb = outdoor ambient air temperature

h'r = surface radiation coefficient

Incident solar radiation for a horizontal surface as
a function of time in half hours after midnight can be

dete mined by

ll

I(i) = (sinB(i)) (Ir(i))

where:
I(i) = radiation on horizontal surface at time
t = i half hours after midnight (BTU/hour
(Sq Ft))
8(i) = solar altitude angle at time t = i
Ir(i) = total incident radiation on plane normal

to sun at time t = i (BTU/hour Sq Ft)

Total incident radiation on a plane normal to the sun as
a function of solar altitude as given in the ASHRAE Guide
(1963) is presented in Table 2.1.

Solar altitude as a function of time in half hours
after midnight for the month of July at latitude 42
degrees North is presented in Table 2.2 (Threlkeld, 1962).

Using these values and the sol-air temperature
modifications prOposed by Parmelee and Aubele (1952), the
model uses the following series of equations to calculate
sol-air temperatures for the 48 half-hour intervals dur-

ing the day

AR = otdba(i)4 (1 - .55 + .33 «FT'Tv 1)

tsa(i) = [(aI(i) -sAR)/(hCO + h'r)] + tdba(i)

Where:
0 = Stephan Boltzman constant (.173 x 10.8)
s = a = .5
PV(i) = vapor pressure of air at time t = i

(inches hg)

12

TABLE 2.l.--Tota1 incident solar radiation on a plane
normal to the sun as a function of solar

 

 

altitude.

Solar Radiation Solar Radiation
Altitude BTU/Hours Altitude BTU/Hours
Degrees (Sq Ft) Degrees (Sq Ft)

5 67 40 258
10 123 45 266
15 166 50 273
20 197 60 283
25 218 70 289
30 235 80 292
35 248 90 294

 

TABLE 2.2.--Solar altitude at 42 degrees North latitude

 

 

for July.

Time in Half Hours Solar Altitude
After Midnight Degrees - Minutes
12 36 15 - 08
14 34 26 - 00
16 32 37 - 07
18 30 48 - 10
20 28 58 - 38
22 26 67 - 15

24 -- 71 - 0

 

13

tdba = absolute air temperature at time t = i
(deg R)

(hco+h'r)= 4.0 BTU/hour (Sq Ft) (deg F)

.55 + .33= constants determined by Parmelee and
Aubele.

Other terms as previously defined.

2.3 Bird Heat Production

 

Total heat and moisture production of the chicken has
been well documented in the research literature. Barott
and Pringle (1941 and 1946) reported the results of calori-
meter studies of metabolism levels in Rhode Island Red hens
as a function of ambient temperature. They found that heat
production remained relatively constant in the ambient
temperature range of 65-80 degrees F. Above 80 degrees,
total heat production increased, sensible heat decreased,
and latent heat increased. Diurnal variations in metabolic
rate were observed. These variations were in phase with
the natural day which the birds had been previously exposed
to.

Ota and McNally (1961) conducted calorimeter studies
with three breeds of laying birds at different ambient
temperatures. During the night-time hours, sensible heat
production declined about 17 percent as compared to daytime
conditions. There was no significant difference in latent
heat production between day and night. Data obtained with

Single Comb White Leghorns are presented in Table 2.3.

14

TABLE 2.3.--Heat production at various levels of ambient
temperature for S.C. White Leghorn hens.

 

 

Ambient Sensible Heat Latent Heat
Temperature (BTU/Hour (Lb)) (BTU/Hour (Lb))
Day Night Day Night
26 11.1 6.9 1.7 1.6
34 8.3 6.8 2.1 2.0
47 7.3 6.1 2.3 1.9
56 6.6 5.3 3.2 2.6
64 6.5 5.1 3.3 2.2
74 --- --— 3.4 2.0
84 6.3 3.6 4.2 3.5
94 .2 .6 5.3 4.7

 

Although the calorimeter studies were conducted without
diurnal variations in temperature, the work of Reece and
Deaton (1969) with broilers indicated that heat production
was continually being altered with changes in ambient temp-
erature.

The model was developed accordingly with the data of
Table 2.3 being used in a linear interpolation routine called
TABLI which was developed by Llewellyn (1965) for use in
dynamic simulation programs. The selection of day and night
levels of heat production is made on the basis of whether

or not lights are on in the structure.

2.4 Electrical Heat Production Within the System

 

Use of electricity for artificial lighting and to
power materials handling equipment provides a direct source

0f sensible heat to the system. The amount of electrical

15

energy added during the hours of artificial daylight was
estimated at 1 watt per square foot of floor area and the

amount of heat added is

Q = 3.413 A

e
where:
Qe = rate of sensible heat addition to system
by electrical usage (BTU/hour)
3.413 = BTU/watt hour
A = floor area in square feet

Electrical usage during "night" hours was assumed to

be negligible and not to add any heat to the system.

2.5 Wall and Ceiling Heat Exchange
Conventional steady state analysis of heat flow
through structural components is based on the Fourier

equation for heat conduction

Q = -KAAt
where:
Q = rate of heat conduction (BTU/hour)
K = thermal conductivity of the component ((BTU)
(Unit thickness)/(hour)(deg F))
A = surface area normal to direction of heat

flow (Sq Ft)
At = temperature difference between inside and
outside (deg F)
When time varying boundry conditions are included, the

equation governing one dimensional unsteady state heat

16

flow for materials with constant thermal properties becomes

(Holman 1963)

2
K %;§.= pC %%
where:
321* .
——§-= second partial derivitive of temperature with
3x respect to distance
p = density of material (lbs/cu ft.)
C = specific heat of material (BTU/lb(degF))
-§§ = first partial derivitive of temperature with
respect to time

K = previously defined

Although numerical methods involving finite difference
approximations are easily adaptable to solution of this
equation for homogeneous materials, the non-homogeneous
construction of most poultry house walls and ceilings
introduces considerable complexity.

Mackey and Wright (1944) developed a method of evalu—
ating transient heat flows in homogeneous walls or roofs
which they later (1946) extended to cover non-homogeneous
construction. This method predicts interior surface temp-

eratures as

.606(tsa-ti)

 

t - = t- +
$1 1 L
_E. .__cg__—
tsi“ 51 + Ae [tsa(1 15 tsa]

l7

 

where:
tSi = mean interior surface temperature for
the day

.“i - - ' ' ='—.._?l
tsi(l 15 — sol air temperature at time t l 15
-I% = harmonic lag time in hours

A1+A2 .

Ae= 2 = mean harmonic decrement factor for the

first two harmonics.

The values of A and o versus L/K and KpC for a given
wall or roof section have been plotted by Mackey and Wright
(1944) and a graphical solution is possible once these
governing parameters have been evaluated.

Interior surface temperature for a composite wall
section is evaluated using the same technique with the
exception that apparent values are developed for L/K and

KpC.

 

(9-) = Li

K apparent all layers R—
i
L

_L ‘i
(Kpc)apparent - all layers 1'1 -;4(KpC)i +

L
(-K-)

 

apparent

 

14-);
(KDC)L[(R)L all’layers except L'

T IE)
K apparent
where:

L = outermost layer

second term is dropped if it i 0

18

Heat transfer rates through wall and ceiling areas was

determined by

Q = 1.65 A (ts. - ti)

1
where:
Q = heat transfer rate (BTU/hour)
1.65 = inside surface heat transfer coefficient
(BTU/hour(Sq Ft)(deg F))
A = area of wall or ceiling (Sq Ft)
si , ti = previously defined

Sol-air temperature was not used in wall heat flow
calculations because of the assumed negligible effect of

radiation on these normally shaded surfaces.

2.6 Floor Slab Effects

Exchanges of heat between poultry house environment
and the floor slab have been largely ignored by previous
researchers. Jordan and Barwick (1965) considered the
floor as a heat storage area only, while Reece and Deaton
(1969) offered temporary heat storage by the floor as an
eaxplanation of variation in data without attempting to
CIuantify it. Other researches have dismissed slab effects
EiS negligible due to the insulating effect of litter.

Approximately 25 percent of the concrete floor slab
:in.the modern cage laying house is utilized for walkways
and equipment placement and, as such, is exposed directly
to the interior environment without the buffering effect

of insulating coatings of manure. The differential equation

19

governing transient heat transfer presented in the pre-

ceeding section is also applicable to the floor slab and
similar solution techniques can be applied. However, it
was felt that the relatively high conductivity values of
concrete and the porous fill material located beneath the
slab provided a situation which was ameniable to the more
rapid lumped parameter method of analysis. Heat exchange

with the uncovered portion of the floor was calculated as
Qf = (1.65) (.25) A (tf - ti)

where:
Qf = heat transfer rate (BTU/hour)

-l.65 = inside surface coefficient previously

defined

.25 = proportion of floor surface exposed to
environment

A = total floor area (Sq Ft)

tf = surface temperature of floor (deg F)

t. = environmental temperature adjacent to floor

determined as the average of outside temp-
erature and mean inside temperature to
compensate for normal stratification expected
(deg F)'

Floor surface temperature was assigned an initial
value equal to the mean outside temperature for the day
plus 5 degrees. This value was approximately equal to the
mean expected interior temperature for the day and was

intended to eliminate long term storage effects. Subsequent

20

values were determined for each time interval by means of

the following equation

 

(t I = (t ) - of
f new f old (C)(M)(.25)(A)
where:

(tf)new = slab temperature for next time period
(deg F)

(tf)Old = slab temperature for present time period
(deg F)

M = mass of one square foot of slab plus mass

of sufficient fill below the slab to make
up a total thickness of 10 inches. Four
inches of concrete plus 6 inches of sand
was assumed for all simulations. This
yielded a mass of 120 lbs. per square foot
of floor space.

Other terms previously defined.

2.7 Ventilation and Evaporation
The introduction of outside air into the system and
its subsequent removal by the exhaust fan permits the
exchange of both latent and sensible heat. Sensible heat
added or removed from the system can be determined from
the change in temperature and the mass of air per unit time

being moved through the system

vs db)

21

where:
st = sensible heat removed from the system
(BTU/hour)
.24 = specific heat of air (BTU/1b. (deg F))
Ma = mass of ventilating air leaving building
(lbs/hr)
t.,tdb = previously defined

Latent heat removal is somewhat more difficult to
evaluate. Latent heat arises from two sources; vaporized
moisture produced directly by the birds, and moisture
evaporated from the wetted surfaces of manure beneath the
cages. Latent heat produced by the birds is well documented
as a function of ambient temperatures and it is common
practice to assume that all of this moisture is removed by
the ventilation air stream. Free moisture evaporation from
other wetted surfaces has been estimated in several more
or less arbitrary ways in the literature. Three of the
more common methods are noted below with potential limita-
tions of each:

1. Complete equilibrium where moisture is evaporated
at the rate produced and the production rate is assumed
constant over the 24 hour period. This is the method used
by Phillips (1968) in his analysis of supplemental heat
requirements for poultry brooding. The relatively high
temperatures associated with brooding are conducive to a
great deal of evaporation and lower bird density provides

large surface area per unit volume of moisture. The method

 

22

does not appear to be well adapted to summer conditions in
the laying house.

2. Assignment of a fixed proportion of free waterv
production for removal by the ventilation system. Long—
house gt_gl. (1960) suggest an approach of this type for
winter ventilation calculations, noting that some portion
of the moisture is removed with periodic cleaning opera-
tions and thus unavailable for evaporation. The two major
problems inherent in this approach for summer calculations
are the fact that free water production is temperature
dependent and the amount of moisture removed with the
manure will depend upon the frequency of cleaning.

3. Assignment of a fixed relative humidity level for
ventilation air leaving the structure. Saeed (1966)
reported that during summer, ventilation air appears to be
exhausted from the poultry house at relative humidity of
.62-.72 irregardless of exterior conditions. He refers to
this phenomenon as "humidity index" and characterizes it
as a structural phenomenon. It appears somewhat question—
able if this phenomenon would persist throughout the range
of conditions which might be tested in a simulation model.

In view of the limitations envisioned with these
previously used and suggested methods, it was felt that
moisture evaporation calculations based more on physical
relationships within the systemeould be appropriate. The
first assumption in the development was that all vaporized

moisture from respiration would be removed by the

23

ventilation air. Mass transfer equations using the Rey-
nolds analogy for mass transfer in turbulent flow over a
flat plate were adapted to predict evaporation rates.

The basic equations are as follows

EVAP = hd(.75)(2)(A)(CO - CS)

where:
EVAP = evaporation rate (lbs HZO/hour)
h = mass transfer coefficient (lbs HZO/hour
unit difference in concentration)
.75 = proportion of floor area covered with manure
2 = factor included to account for added surface
area due to surface roughness
A = surface area (Sq Ft)
C = mass concentration in air outside boundry
layer (lbs HZO/lb mixture)
C = mass concentration in saturated air at sure
face (lbs HZO/lb mixture)

The mass transfer rate (hd) is determined by

h = S 9 V

d t a
where:
St = Stanton number
pa = average density of air in the turbulent zone
(lbs/cu ft)
V' = mean velocity of air outside the boundry layer

(ft/sec)

24

The Stanton number is a dimensionless parameter

determined from the Colburn correlation equation (Dhanac,

 

1969)
CF
ST:
2 S .667
c
where:
SC = Schmidt number for air = .6
CF = skin friction coefficient
.667,2 = constants

The skin friction coefficient (CF) is in turn calcu-
lated from the following equation for turbulent flow over

a flat plate

 

.288
CF =
R 1/5
e
where:
1/5,.288 = constants
R = Reynolds number

e

The mean velocity of air outside the boundry layer

was calculated by dividing the total ventilation rate by
the longitudinal cross sectional area of the structure and
then applying a factor of 3 to account for natural stream
effects and obstructions of cages and other equipment.
The resulting velocities agreed well with subsequent mea-
surements using a hot wire anemometer and work by Lilleng
(1969).

All heat required for evaporation of free moisture

‘was assumed to be provided by the ventilating air stream.

 

25

The net heat exchange due to ventilation was the sum of
the latent heat required to vaporize the evaporation water
plus the sensible heat required to effect any temperature
change in the air.

One of the most sensitive parameters in this analysis
is surface temperature of the manure which is used to
determine water concentration at the assumed saturated
condition. The model estimates surface temperature as the
average of slab temperature and the air temperature above
the slab as previously determined in the evaluation of heat

exchange with the exposed slab area.

2.8 Computer Program Outline

The model was programmed in Fortran IV language for
Operation on the Control Data Corporation model 6500 come
puter at the Michigan State University Computer Laboratory.
A complete listing of the program as used in simulations
is contained in Appendix A and a brief description of its
operation follows below.

The program first reads in data values for outside
conditions. Included are average daily temperature, range,
wet bulb depression, solar altitude angles, and incident
radiation. Values are then read for start of artificial
day, thermal values for the structure, structure size and
housing density.

The first major execution section of the program
generates outside temperature, relative humidity, and

sol-air temperature spectrums for the 48 half-hour time

 

26

interval node points. These generated data are then
printed out on the line printer.

An array of zeros and ones is then generated to
represent the times when lights are either off or on.
This array is subsequently used in determination of
electric heat and bird heat production levels. It could
also be used to trigger any "day" or "night" related
management practice.

The program then enters the control loop which steps
it through the 48 time points for the day. The first step

in this loop is the initialization and updating of array

 

 

location values to be used in subsequent steps. The pro-
gram then assumes a system temperature equal to outside
temperature plus 5 degrees and enters the Newtonian con-
vergence routine. Subroutine HEAT, called from the con-
vergence routine, determines net heat flow into the system
as a function of given parameters by calling supporting
subroutines designed to calculate heat flows through
specific boundaries.

Once the system conditions for a particular time
point are determined, they are printed out along with the
heat and moisture contributions across the various system
boundaries. At the completion of the 48 time point day,
control leaves the do loop and a printer plot of inside
and outside temperatures for the 48 time periods is con-

structed using subroutine PLOT.

3. MODEL VERIFICATION

3.1 Facilities and Equipment

Verification studies were conducted in a 31' x 40’
pen contained in a 40' x 152' single story, clear-span
poultry house located at the Michigan State University
Poultry Science Research and Teaching Center, East Lansing,
Michigan. The pen was separated from the adjacent pen on
one side by a stud frame partition wall sheathed with a
single thickness of 3/8" thick fir plywood. The opposite
wall, separating the pen from a feed and utility room,
was of stud frame construction sheathed both sides with
3/8" thick fir plywood and containing a 2-inch thickness
of batt-type fiberglas insulation in the space between
the studs. The two end walls of the pen were coincident
with the sidewalls of the building and were constructed
of an inner layer of 3/8" thick fir plywood, 3-inches of
batt-type fiberglas insulation, and an outer surface of
corrugated aluminum siding which was painted dark green
in color. The ceiling was also covered with 3/8" fir
plywood secured to furring strips attached to the lower

chords of the roof trusses. There was a 6-inch thick

27

28

fiberglas batt insulation immediately above the ceiling
and the roofing material consisted of natural finish
corrugated aluminum secured to purlins attached to the
upper chords of the roof trusses. Floor construction
consisted of a flat surfaced concrete slab, 4 inches in
thickness, laid over a 6-inch thick sand fill base. The
general orientation of the building ridge line was North-
west-Southeast with the 40 foot dimension of the pen being
at right angles to this direction.

The pen contained three rows of modified stair step
cages which were suspended from the ceiling in the loca-
tions shown in Figure 3.1. At the start of the testing
period, the cages contained 647 Single Comb White Leghorn
hens and 144 White Rock hens. Randomly selected samples
of 20 White Leghorns and 10 White Rocks yielded average
weights per bird of 4.4 lbs. and 6.5 lbs. respectively.

Ventilation air was admitted to the pen through a
continuous slot inlet located in the ceiling at the South—
west wall of the pen. The inlet was designed to bring air
over the top of the wall plate directly from outside. A
baffle was used to direct the inlet air downward along the
wall surface. Solid blocking between roof trusses, ceil-
ing, and roofing material adjacent to the ceiling slot prev
vented air from the attic space from entering the pen. Air
was moved through the pen by a 24-inch diameter direct drive
axial-flow exhaust type ventilating fan located in the

center of the Northeast wall. Two different fans were used

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

 

0 1n
{fir .11
3 2
N
'14
o 15 50 04
Recorder o 12
o 13
m .—I Z-
8 5 $3.
a: N a:
3;" 8 3»
(U m (U
U U
G)
(31
65
U
U
30'4" j
16 9
4?: l. . . g
o
8

Figure 3.l.--Floor plan of pen used in verification studies.

30

in this location during the course of the studies. The
first was a constant speed 1/3 horsepower unit designed

for thermostatic control. The second was a 1/4 horsepower
unit equipped with an SCR (Silicon Controlled Rectifier)
motor speed controller designed to utilize the temperature
dependent resistance of a thermistor to automatically
adjust fan speed in an attempt to maintain a preset
interior temperature. In order to obtain the constant
ventilation rates desired for the verification studies, the
thermistor sensor was replaced with a precision wound 0-100
K ohm variable resistance unit which was adjusted to pro—
vide the desired fan volumes.

Copper-constantan thermocouples were installed in
the pen area at the locations shown in Figure 3.1 and tab-
ulated in Table 3.1. Two thermocouples were installed at
each point and connected in parallel to provide an average
temperature for the location. Thermocouple lead lengths
and parallel connections were made in accordance with
procedures described by Finch (1962). wet bulb tempera-
tures were obtained by wrapping a gauze wick around a
thermocouple and immersing one end of the wick in a supply
of distilled water. The wick encased thermocouples were
then oriented so that their maximum surface area was per—
pendicular to the direction of the air stream. The gauze
wicks were cleaned twice daily and replaced every three
days or oftener if they had become uncleanable due to

dust accumulation.

 

31

TABLE 3.l.--Thermocouple locations in test pen.

 

 

Thermocouple
No. Location
1 Inlet air stream in slot inlet
2 Outlet air stream at exhaust fan
3 Wet bulb in air stream at exhaust fan
4 Wall surface on feed room side of South—
east pen wall
5 Wall surface on pen side of Southeast
wall
6 Wall surface on adjacent pen side of
Northwest wall
7 Wall surface on pen side of Northwest
wall
8 Wall surface on exterior of Southwest
wall
9 Wall surface on pen side of Southeast
wall
10 Wall surface on exterior of Northwest
wall
11 Wall surface on pen side of Northwest
wall
12 3.5 inches below surface of floor slab
13 Surface of floor slab
14 Upper surface of insulation in attic
15 Ceiling surface in pen

16

Wet bulb in air stream at slot inlet

 

32

A l6-point Brown—Honeywell recording potentionmeter
was used to record thermocouple output for the test periods.
The recorder was equipped with a time clock which turned
on the chart drive and cycling mechanism every 30 minutes.
After a complete cycle through the 16 points, a micro
switch assembly turned off the recorder until the time

clock initiated the next sequence.

3.2 Experimental Procedure

 

A total of seven different trials were made using
five different ventilation rates and three different
lighting schedules. Each trial was replicated on three
consecutive days with the exception of the sixth trial
which was replicated on four days due to weather conditions.
A minimum conditioning period of two days was used between
trials in which lighting schedule changes were made. A
summary of the daily test conditions appears in Table 3.2.

Birds in the pen were counted at the beginning of
each trial period and the average weights obtained pre—
viously were used in conjunction with the count to estab-
lish a total bird weight for each trial period. The
average weight did not vary from 4.8 lbs. per bird over
the entire test period.

Ventilation rate for a trial period was determined
by use of a hot wire anemometer to measure air velocity
over the face area of the fan discharge housing. This
area was circular with a diameter of 25 inches and was

divided into two concentric outer rings, each 4 inches

33

TABLE 3.2.--Summary of experimental runs.

 

 

Run Ventilation Rate No.
No. Date Lighting Period (cfm/Bird) Birds
4 6-18-70 2:00 am-4:00 pm 8.1 773
5 6-19-70 " " " "
6 6-20-70 " " " "
7 6-23—70 10:00 pm-12:00Noon 8.1 771
8 6-23-70 " " " "
9 6-25-70 " " " "
10 6-28-70 6:00 am-8:00 pm 8.2 765
ll 6-29-70 " " " "
12 6-30-70 " " " "
l3 7-2-70 6:00 am-8:00 pm 4.5 765
14 7-3-70 " " " "
15 7-4-70 " " " "
16 7-14-70 6:00 am-8:00 pm 3.1 752
17 7-15-70 " " " "
18 7-16-70 " " " "
19 7-18-70 6:00 am-8:00 pm 6.1 743
20 7-19-70 " " " "
21 7-20-70 " " " "
22 7-21-70 " " " "
23 7-23-70 6:00 am-8:00 pm 2.6/7.l* 743
24 7-24-70 " " " "
25 7-25-70 " " " "

 

*Low rate during lighted hours, high rate at night.

34

wide and a center circle 9 inches in diameter for purposes
of calculation. Velocity readings were taken at one-inch
radial intervals in each quadrant of each area in order

to determine a mean velocity for the area. The mean velo-
city for each area was then used to determine volume and
volumes were summed over the three areas to get total
ventilation rate. This rate was then divided by the num-
ber of birds to obtain the net rate per bird.

Ventilation rates for the seventh trial were varied
between day and night by placing relay activated resist-
ances in the SCR motor control circuit. The relay was
placed in the lighting control circuit and wired so that
it would activate the resistance associated with low
volume delivery when the lights were on. When the lights
were turned off, the relay placed the resistance associated
with high volume delivery in the SCR circuit.

Temperature data at the half hour interval recording
points were entered on computer cards for analysis. The
simulation program was modified to utilize actual outside
conditions and initial floor slab temperature instead of
generated data to predict system conditions at half-hour
intervals. These predicted conditions were then printed
out along with the actual conditions recorded during the
test. Structural heat transfer values for the exterior
walls and ceiling evaluated according to methods described

in Chapter 2 were as follows:

35

walls:
(Kpc)apparent = .099
L _
(K)apparent - l2°58
Xe = .035
¢/15 = 3.5 hours
ceiling:
(KDC)apparent = .059
L _
(E)apparent _ 23°94
Ae = .012
¢ _
15 — 5 hours

Heat flow through walls separating the pen from the adja-
cent pen and from the feed room was assumed to be negligible
and was not included in the data analysis simulation.

A second computer program which utilized the recorded
surface temperatures in a steady state approximation to
actual heat flows was developed. Output from this program
was used as a comparison for order of magnitude of heat
flows through the various structural components as predicted

by the simulation model.

3.3 Results and Discussion
The model was an acceptable predictor of system con-
ditions for all runs. Actual outside and inside tempera-
tures, along with predicted inside temperatures for one

run from each trial period are plotted in Figures 3.2

36

through 3.8. Data for all runs are tabulated in
Appendix B.

Mean deviation between actual and predicted tempera-
tures for all runs was 1.9 degrees F. Mean deviation
between actual and predicted relative humidities for all
runs was 5.1 percent. Maximum deviations from predicted
values occurred when exterior or interior conditions were
changing rapidly. In these situations, the model tended
to respond instantaneously while actual conditions were
buffered by structural or physiological effects. These
effects were particularly evident for the last series of
trials (Figure 3.8) where ventilation rate was changed
by a factor of 3 and the birds were switched from day to
night simultaneously. Mean deviations between actual and
predicted values for the three runs where this was done
were 3.1 degrees F for temperature and .073 for relative
humidity. This was in direct contrast to those runs
conducted under conditions where ventilation was constant
and outside temperature levels are nearly sinusoidal in
behavior. An example of this was run 19 (Figure 3.7)
where the mean deviations were 1.0 degrees F and .031 RH.

Higher than actual temperature predictions were
associated with low humidity predictions and vice versa.
This tended to indicate that the surface temperature of
manure, which has major influence on evaporation, was in

fact responding more rapidly than the model predicted.

37

.w can now mmusuoquEmp opflmcw empowowum can :moflmcfl :mofimusoII.~.m musmah

 

 

 

 

 

mafia
m m m .2 NH m m m
1.3
mowmcfl copowpmum I

839: all: . . . . .. . :8

@2320 ll: . . . ..
o Icom
. . :2.
.bm

prmflz A. sea Em;— ..
.ba

 

(a Esp)
exniexedmel

.m can How mmusumuwmswu moans“ oouoflowum pom .oofiwcw .oofimusoII.m.m musmflm

 

mafia
m m m .2 NH m w m
l u 0 IL I u u as
woflmcfl concatenm ..om
moflmsw u :

  

wwflmudo all...

 

38

 

 

 

uscfiz

>mo

1L

.om

.om

 

(a 699)
eanexedmel

39

.NH can Mom mmusuwummsop monCA owpoflpmum one .mpwmcfl .monDDOII.v.m onsmflm

 

 

mafia
m m m .2 NH m m m
A u u u a u I» q
:8
mpwmcfl pmuoatmum allblls
wUflmCfl Qulblb
tom
mmeDSO Illd
.I III [I
_I 232

 

Rd 232 I— :2.

 

 

 

(a 58p)
eaneledmel

40

 

.va can you monopwuomEmu monCH concaomum pom .ocflmcfl

P
‘

 

m .2 NH

I
dII 1

mowmsfl concaomum

moaned

moflmpso

mafia

4

.monDSOII.m.m musmfim

db

 

 

 

 

 

unmaz

 

 

ov

O
1‘

 

(a flap)
BIHQEISdMSL

41

.mH can you mmssumsmasmu mefimcfl emsosemum ace .mesmas .oesmuso-n.m.m musmfis

 

 

 

 

 

 

mEHB
m m m .2 NH m m m
A v RI # u I? w 0v
ooflmsfi omno«omum.. . a :
GCHWEH o O u 1' om
OCHmLPDO I1 .5.
l U U 1' CW
. . . . 3 Oh
. . I‘....
h .. 1r
. 1.0m
Iv om
T , I L.

 

(a 58?)
elniexedmem

42

.mH csu How mmusumummsmu onmCH omuoHpmHm can .mpHmsH .prmusoII.h.m musmHm

 

 

 

 

 

 

 

wEHB
m m .2 NH m m m
n o u u u u n ov
moncH omDOHcmum ollollo
:om
OGHmCH elllolo
f
opHmuso ollbllb m
48 maid
a.e
as:
IV e
J.+
(n
. . a
o :10“
.%
tom
“332 To II 232 l ..
sea
5

 

43

.mm can now monsumummsmp mchcH pmpoHomum can .mpHmcH roonDSOII.m.m ousmHh

d-

 

UHHQ\EmO H.n

«I.
‘

monCH omDOHpmnm
ooncH

monuso

}

QIIIOl-ld

I

 

ssas\suo e.m

 

eufin\suo H.EI

 

 

 

usmHz

 

moo

pnmfiz

ow

.om

.05

tom

.om

 

(a 589)
eanexedmem

44

There was some tendency for the model to predict too
high a temperature during the 4-5 hours immediately follow-
ing the start of the artificial day within the structure for
those trials using a day of 6:00 a.m.-8:00 p.m. (Figures 3.4
through 3.8). Two items could contribute to this observed
phenomenon. First, this was a period of rapidly increasing
outside temperature which could promote a more rapid
increase in moisture evaporation than predicted. Second
the model assumes instant assumption of a constant daytime
metabolic rate when the lights are turned on in the struc-
ture. Barott and Pringle (1946) reported that metabolic
rate is cyclic and doesn't reach a maximum level until
sometime after initiation of day. It then declines and
reaches a minimum level approximately 12 hours later.

The high level of insulation in the ceiling prevented
the solar radiation effects from having any noticable effect
on heat exchange in the system. Because of this, the model
appeared to function equally well on both cloudy and clear
days.

Maximum interior temperatures on extremely hot days
remained 5-7 degrees below outside temperatures during the
warmest part of the day. The model correctly predicted
this condition (Figure 3.4) and an analysis of component
parts disclosed that the lower temperature was due to a
combination of lower sensible heat production at the high
ambient temperature, heat absorption by exposed areas of

the cooler concrete floor slab, and increased evaporation

 

45

of moisture with its subsequent cooling effect. The heat
sink effect of walls and ceiling was not a significant
factor in contributing to the lowered interior temperature.
The order of magnitude comparison of predicted heat
flows with calculations using measured surface tempera-
tures and conventional steady state relationships revealed
no major discrepancies between actual and model predicted

exchange rates.

4 . SIMULATION STUDIES

4.1 Values Common to All Studies

One of the major assets of a simulation model such as
the one developed in this study is its usefulness as a tool
in the study of variations in the parameters which affect
system behavior. This chapter presents the results of a
study made of three such parameters and also of a prOposed
ventilation control system which maximizes the effectiveness
of exterior environmental conditions in reducing stresses
induced by summer conditions.

The structure chosen for use in these studies was a
single storied, clear span, windowless unit with outside
dimensions of 40' x 200'. Sidewall construction was
assumed as outer and inner layers of 3/8" thick exterior
grade plywood with a 3" thick layer of blanket type insu-
lation between the two layers. Interior sheathing for the
ceiling area was also assumed to be 3/8" plywood with a
3" thick batt insulation immediately above it. Roofing
was .020" thick corrugated aluminum secured to roof purlins
on tOp of trussed rafters. The floor was assumed to be 4"

thick concrete slab placed over 6" of porous fill material.

46

47

Seventy five percent of the floor was occupied by manure
storage.

Evaluation of thermal properties for the composite
wall and ceiling areas according to the previously cited
Mackey and Wright method yielded the following values which

were entered as data in the simulator.

walls:
(KDC)apparent = .095
L
(K)apparent _ 13°05
Xe = .036
.51 _
15 - 3.5 hours
ceiling:
(Kpc)apparent = .104
L
(E) apparent — 12.58
Xe = .038
9 _
15 — 4.0 hours

Occupancy of the simulated structure was assumed to
be Single Comb White Leghorn hens having an average weight
of 4.5 lbs. each.

During the course of the summer ventilation period,
the system is subjected to a variety of external environ-
mental conditions which are only generally represented by
the average temperature conditions presented in Section

2.2. Maximum physiological stress on the bird is induced

48

by high system temperatures not usually associated with

the normal outside temperature values for the Lansing

area. In order to evaluate system performance over more

of a range of exterior conditions, two different exterior
temperature profiles were used in the simulation studies.
The first was the normally expected July value of 72 degrees
F mean temperature, daily range of 23 degrees, and average
wet bulb depression of 8 degrees. The second was regarded
as an extreme conditionauuiutilized values of 85 degrees,

30 degrees, and 12 degrees for mean, range, and wet bulb

depression respectively.

4.2 Ventilation Rates

Deep body temperature of the chicken is 107.5 degrees
F (Esmay, 1969). When ambient temperature of the system
surrounding the bird exceeds 90 degrees F, she is placed
under high thermal stress and heat prostration is likely.
If ambient temperature exceeds 100 degrees, Baker gt_al,
(1958) state there is extreme danger of death.

The principal means of temperature control in the
more humid northern areas of the United States has been
through ventilation. The inadequacy of conventional steady
state heat flow equations to evaluate system temperature
under summer conditions has led to the development of a
considerable number of "recommended" ventilation rates
and management control practices for ventilation systems.

The first simulation study was directed towards the

49

determination of the effect of ventilation rate on system
temperature.

A total of six different constant ventilation rates
were simulated for one day of operation at each of the two
outside temperature profiles. Rates used were 2.5, 3.5,
4.5, 5.5, 6.5, and 7.5 cfm/bird (cubic feet per minute per
bird). A housing density of .7 sq ft/bird and a 14—hour
artificial day extending from 6:00 a.m. to 8:00 p.m. were
used.

A summary of simulation results is presented in
Table 4.1 and temperature profiles for the 2.5, 3.5, 5.5,
and 7.5 cfm/bird rates are plotted in Figures 4.1 and 4.2.

The lowest ventilation rate produced the highest
maximum, highest average, and minimum daily temperature
range for both normal and extreme outside temperature
conditions. Conversely, the highest ventilation rate
produced minimum system temperatures and maximum daily
ranges for both exterior temperature profiles.

For normal exterior temperatures, system temperature
at the 2.5 cfm/bird rate never went below exterior temp—
erature. Increasing the ventilation rate from 2.5 to 7.5
cfm/bird decreased the daily maximum system temperature
5.5 degrees indicating that the heat required by increased
evaporation was greater than that required to offset the
sensible heat added by the higher ventilation rate. Of
this 5.5 degree decrease, 3.3 degrees was obtained by

increasing the ventilation rate to 4.5 cfm/bird. The

50

TABLE 4.l.--Effect of various levels of constant

ventilation on system temperatures.

 

ventilation Rate

System Temperatures for Day (deg F)

 

 

 

 

(cfm/bird) Maximum Minimum Average Range
Normal Outside Temperatures
2.5 84.9 67.1 76.3 17.8
3.5 82.9 64.8 73.8 18.1
4.5 81.6 63.4 72.4 18.2
5.5 80.6 62.5 71.3 18.1
6.5 79.9 61.8 70.7 18.1
7.5 79.4 61.3 70.1 18.1
Extreme Outside Temperatures
2.5 91.7 76.7 85.5 15.0
3.5 90.7 74.5 83.8 16.2
4.5 90.1 73.1 82.6 17.0
5.5 89.9 72.3 82.0 17.6
6.5 89.7 71.8 81.6 17.9
7.5 89.6 71.4 81.3 18.2

 

51

.mmusumuwmfiwp onmuno HmEHocIImHspmummfiwp
MOHHmucH so mopmu GOHDMHHuco>.u:mumcoo ucmHmMMHo mo DommmmII.H.v wHDmHm

 

 

 

mEHB
a m m .2 «H m m m

i u n x T u 0 cs

OUMmHDOI ..
OUHmr—H .. om
. : om
UHHQ\EMO m.h \ .- Oh

esfin\suo m.m ..

when
4 \smo m.m : om
._ IAIIII eufln\eLo m.~
Al om
unmflz IT was II nsmflz I:
4

 

(& 589)
eanexadmem

52

.mwusumquEmu mpwmuso mfimuuxmtlmmusumummawu
uoHumucH so woven coHDMHHucm> ucmumcoo uanOMMHp mo pommmmII.m.v musmHm

 

 

 

mEHB
m w m .z mH m w m
n . h . u u “I ov
mfiflmfido I
.uom
meflmcfl
—l l.) L Lu CW
41
nf ON-

 

UHflQ\EMU m o N. \l .v
:. om
esfln\suo m.m \\\. euflnxsuo m.m
UHHQPGO m . m

.om

 

A

 

(a 569)
exnieredmal

53

threefold increase in ventilation rate decreased the mini-
mum daily system temperature 5.8 degrees and resulted in
an increased daily range of .3 degrees.

Maximum system temperatures did not reach the 100
degree maximum of the extreme outside conditions with any
of the ventilation rates tested. At the 2.5 cfm/bird
level, maximum system temperature was 8.3 degrees below
exterior temperature which reflected the decreased sensi-
ble heat production, increased heat transfer to the floor,
and higher evaporation rates associated with higher system
temperature. Increasing the ventilation rate from 2.5 to
7.5 cfm/bird decreased the maximum system temperature only
2.1 degrees with 1.6 degrees of this decrease being asso-
ciated with ventilation rate increase from 2.5 to 4.5
cfm/bird. The decreased effectiveness of higher ventila-
tion rates under extreme outside conditions as compared
to normal conditions is due to the fact that heat required
for the higher evaporation rates associated with high
ventilation is only slightly greater than the heat required
to offset the increased addition of sensible heat by the
ventilating air. The 5 cfm/bird increase in ventilation
rate decreased the daily minimum temperature 6.3 degrees
F with 4.4 degrees of this decrease being associated with
the increase from 2.5 to 5.5 cfm/bird. The more rapid
decrease in minimum temperature with increasing ventilae
tion rates indicated that the higher rates were more

effective in reducing system temperature during the night.

54

At this time, exterior temperatures were lower than system
temperatures and ventilation air did not contain more
sensible heat than system air.

Increasing the ventilation rate tended to minimize
the transitional effect between night and day which the
model exhibits. This is to be expected since the effect
is due to the assumed instantaneous change in sensible
heat production and the increased air exchange at the
higher ventilation rates dilutes the effect of the heat

on system temperature.

4.3 Densitnyffects

 

Housing density and its subsequent effect on exposure
factor as defined by ASAE:D270 (ASAE Yearbook, 1970) is
an important element in determining housing design and
ventilation parameters for winter conditions. We might
also expect density to have some effect on summer environ-
ment since it directly affects total bird heat production,
a major system input. This series of simulations was
designed to investigate the density effect.

A total of 12 one-day simulations were made using
six different housing densitiesand the two outside temp-
erature profiles. Densities used were .7, 19, 1.1, 1.3,
1.5, and 1.7 sq ft/bird (square feet per bird). A constant
ventilation rate of 4.5 cfm/bird and an artificial day of
6:00 a.m. to 8:00 p.m. were used for all runs.

Summarized results for the housing density simula—

tions are presented in Table 4.2 and temperature profiles

55

TABLE 4.2.--Effect of housing density on system
temperatures.

 

Density System Temperatures for Day (deg F)
(sq ft/bird) Maximum Minimum Average Range

 

Normal Outside Temperatures

 

 

 

.7 81.6 63.4 72.4 18.2
.9 81.6 63.4 72.4 18.2
1.1 81.2 63.3 72.1 17.9
1.3 80.9 63.3 71.9 17.6
1.5 80.7 63.3 71.8 17.4
1.7 80.5 63.3 71.7 17.2
Extreme Outside Temperatures
.7 90.1 73.1 82.6 17.0
.9 89.4 73.0 82.2 16.4
1.1 89.0 72.9 82.0 16.1
1.3 88.6 72.8 81.8 15.8
1.5 88.3 72.8 81.5 15.5
1.7 88.0 72.7 81.4 15.3

 

56

oEHB
.2 NH

m
I" u

.mmusumummfimp
oonpso HmEuosIImmusumuomEou HOHuoucH co NuHmcmo mchson mo Doommmlt.m.v musmHm

ov

 

ID

I.
q-

d

ochpso

mcamca

 

enfln\uu am a.

enfln\uu em m.H

 

 

i.

ucmHz woo

 

I unmflz

 

(J Bap)
eanexedme;

57

.mmusumnwmswu
monuso msmuumeImmHsumnmmfimp Homuwucw so huHmcmo mchsoc mo pomMMMII.v.e musmHm

 

 

 

 

 

msHs
a m m .z 3 a m m
. . . I I .. u 3
l
.Uom
Tm
:3 Im
Pd
I i
l 'I—ll 'LI'
_4, uanz mom Ifi ufimHz SJ saw
(m
:3 e
4'
atom
ssfln\sm am m.H
oan\umImm s. ..om

 

58

for the .7 and 1.5 sq ft/bird levels are plotted in
Figures 4.3 and 4.4.

Maximum system temperature was decreased 1.1 degrees
F when density was decreased from .7 to 1.7 sq ft/bird
under normal outside temperature. Minimum temperature
was decreased only .1 degree for the same density change.

In the case of extreme outside temperature, the .7
to 1.7 sq ft/bird decrease in density reduced the maximum
system temperatures 2.1 degrees F and minimum system
temperatures .4 degrees F.

Density effects were most noticable during the 11:00
a.m. to 6:00 p.m. period when outside temperatures are
above the daily mean. System temperatures for a given
outside temperature profile were essentially independent
of density effects during the cooler portion of the out-

side temperature cycle.

4.4 Variations in Artificial Day

Ota and McNally (1961) reported a 17 percent increase
in sensible heat production for daytime as compared to
night hours. Usage of electricity for lights and materials
handling equipment adds more heat during the daytime. The
results of Section 4.2 indicate that the ventilation system
is more efficient at heat removal during the night hours
inhen environment outside the system is at its lowest temp—
eeratures. Since the modern poultry house is windowless
aand apparent day in the system is completely under control

(3f the management of artificial lighting, the potential

 

59

exists for placing the period of maximum heat addition to
the system in phase with the period when the ventilating
air is best able to remove the unwanted heat. This parti-
cular series of simulations tested this possibility.

Ten simulated days of operation were run using the
two outside temperature profiles and five different 14-
hour artificial day periods. The "days" used were 6:00 a.m.-
8:00 p.m., 2:00 a.m.-4:00 p.m., 10:00 p.m.-12:00 noon,

6:00 p.m.-8:00 a.m., and 2:00 p.m.-4:00 a.m. A constant
ventilation rate of 4.5 cfm/bird and a housing density of
.7 sq ft/bird were used in all tests.

Results for the ten runs are summarized and presented
in Table 4.3 and system temperature profiles for two of the
"days" are plotted in Figures 4.5 and 4.6.

Under normal outside conditions, maximum system temp-
eratures were minimized by placing the artificial day
period at either 10:00 p.m.-12:00 noon or 6:00 p.m.-

8:00 a.m. Maximum temperature for these "days" was 78.4
degrees P which was a 3.2 degree decrease below maximums
encountered with the other three day periods tested. Mini-
mum temperature predicted for the two "days" was 65.6 which
was equal to the highest minimum system temperature for

all the day periods tested. Temperature range for the two
days was 12.8 degrees; the lowest experienced for the five
periods. Maximum daily range of 19.3 degrees occurred

with the 2:00 p.m.-4:00 a.m. day period which had high

and low system temperatures of 81.6 and 63.3 degrees F

respectively.

60

TABLE 4.3.--Effect of different "days" on system
temperatures.

 

 

 

 

 

"day" System Temperatures for Day (deg F)
Maximum Minimum Average Range
Normal Outside Temperatures
6:00 a.m.-8:00 p.m. 81.6 63.4 72.4 18.2
2:00 a.m.-4:00 p.m. 81.6 65.6 72.2 16.0
10:00 p.m.-12:00noon 78.4 65.6 72.1 12.8
6:00 p.m.-8:00 a.m. 78.4 65.6 72.2 12.8
2:00 p.m.-4:00 a.m. 81.6 63.3 72.3 19.3
Extreme Outside Temperatures
6:00 a.m.-8:00 p.m. 90.1 73.1 82.6 17.0
2:00 a.m.-4:00 p.m. 90.2 76.3 p 83.1 13.9
10:00 p.m.-12:00noon 89.6 76.3 83.5 13.3
6:00 p.m.-8:00 a.m. 89.6 76.3 83.2 13.3
2:00 p.m.-4:00 a.m. 90.2 73.1 82.8 17.1

 

61

.mmusumummsmu monuso HmEHoc
IImmusumudemu HoHuopsH co mooHHmm moo HMHOHMHDHM uconMMHp mo DomMMMII.m.v musmHm

 

 

   

mEHB
m m m .2 NH m m m
P b b D b b I
.év
QUHWHDO I
Ar
opHmCH
lvom
at
.vom
hop .E.m oouvI.E.m oouN
No .E.m u I.E.m ”
U 00 v 00 N :on
Atom
at
:om

 

(a 58p)
axnieiedmem

62

.2 NH

P
C

D
p
fiI-m

QUH MUHHO I

moamca

New .E.o oouvn.E.m ooum

mEHB

m

 

.mwusumummsmu monuso mEmHuxm
Ilwmusuwummfiwu uoHuchH co mpOHme moo HMHOHMHDHM ucmHmMMHp mo pomHMMII.m.v musmHm

 

moo .E.Q couVI.E.m oouN

 

ov

om

cm

on

om

om

(a Bap)
eanexedmem

63

A similar pattern of results was achieved with the
extreme outside temperature conditions. The lowest system
maximum of 89.6 degrees F was obtained with the 10:00 p.m.-
12:00 noon and 6:00 p.m.-8:00 a.m. "day" periods and the
minimum daily range of 13.3 degrees was also obtained with
these periods. The difference in maximum system tempera-
tures for extreme outside conditions varied only .6
degree over the five day periods tested while the varia-
tion for normal conditions was 3.2 degrees F; indicating
that phase shifting is more effective in reducing maximum

temperatures when outside conditions are normal.

4.5 Logic Based Ventilation Control System

Squibb (1959) reported that New Hampshire hens are
better able to withstand high average daily temperatures
when these temperatures are associated with wide diurnal
fluctuations. Similar results were also reported by
Squibb et_§1. (1959) for white leghorn hens.

Operating costs for a ventilating system are propor-
tional to the amount of air moved. Supplying 4.5 cfm/bird
for birds housed at .7 sq ft/bird in the simulated build-
ing would require 6 one-half horsepower fans which at
$ .02 per kilowatt hour would consume approximately $150.00
of electricity for a four-month summer period. Increasing
the rate to 7.5 cfm/bird requires an additional four fans
and increases operating costs by $100.00.

Traditional farm operations are coincident with the

period of natural daylight and even though most of the

64

equipment associated with egg production systems is auto—
mated, an operator is still required. It is questionable
if the small advantage shown for the temperature range of
the 2:00 p.m.-4:00 a.m. "day" would either justify or
influence changes to this operating schedule.

A combination of Squibb's research, economics, and
traditional operating patterns with the simulation results
of the preceeding three sections permits the establishment
of some management and ventilation control parameters
which will improve temperature profiles for the system
subjected to summer environment. These parameters would
be as follows:

1. Artificial day period within the structure of
6:00 a.m.—8:00 p.m.

2. Maximum ventilation rates during the warm part
of the day which do not exceed 4.5 cfm/bird or 1.0 cfm/
1b of body weight.

3. Ventilation rates during the cooler part of
the outside temperature cycle which will provide a lower
system temperature and thus increase daily range. Control
of this rate could be effected by an SCR fan controller
circuit which adjusted fan delivery rate based on maximum
temperature difference between outside and system condi—
tions.

A logic based control system which meets parameters
2 and 3 above and prevents system temperatures from dropping

below the thermoneutral range was designed for the simulator.

65

A computer program flow chart which illustrates the func-
tioning of this controller is shown in Figure 4.7. The
controller possesses three levels of control; 1) it
operates the ventilation system at a predetermined base
rate of air exchange; 2) if system temperature drops
below 55 degrees F, the controller reduces the ventila-
tion rate until the desired minimum of 55 degrees is
reached; 3) if system temperature is above 55 degrees F
and it is more than 4 degrees above outside temperature,
ventilation rate is increased to take advantage of the
cooling possible with the lower outside temperature.
Terminology used in Figure 4.7 is as follows:

VENTR = ventilation rate (cfm/bird)

T0 = outside temperature (deg F)
TI = system temperature (deg F)
BASE = base ventilation rate (cfm/bird)

IND = indicator variable

The controller was incorporated into the model and
one day simulations were made using a base rate of 3.0
cfm/bird and the two outside temperature profiles. The
desired 6:00 a.m.-8:00 p.m. day and a housing density of
.7 sq ft/bird were used for both runs. System temperature
and ventilation rates for the two days are presented in
Figures 4.8 and 4.9.

Ventilation rate for normal outside conditions ranged
between the base rate of 3.0 cfm/bird and a maximum of 5.3

cfm/bird. Average rate for the day was 3.4 cfm/bird.

66

 

VENTR BASE

IND = 0

L

NEWTONIAN CONVERGENCE ROUTINE

 

 

 

 

 

FOR SYSTEM TEMPERATURE PREDICTION

I

 

 

 

 

yes
61 .<_ 55>

no

 

 

VENTR = VENTR - .1
l TI-T034
no and
IND = l IND # 1

yes

 

 

 

 

 

 

 

 

 

 

 

 

 

t

VENTR = VENTR + .1 ._____4

 

 

 

 

 

I

 

 

EXIT FROM CONTROLLER

 

 

 

Figure 4.7.--Flow chart for logic based ventilation control.

67

.mdhfipmummfiou monuso HmEHoc

 

 

IIHouucoo GOHDMHHucm> comma OHmoH mchs wHHwoum wuspwuomfiou uoHuousHIl.m.e wusmHm
wEHB
m m m .2 NH m m m
u n NI » u u h
m
w
m
w
monpso l
om
msflmcs
on
om

 

h

 

ucmflz

Jl

 

NS 2E2

 

om

(PITQ/WJD)
uorqerrqueA

(& Bap)
eaneiedmam

68

LIEmummm COHumHHucw> omwmn OHmoH mchD wHHmoum onsumummfiwu HoHHoDCHII.m

db

mEHB
.2 NH

 

TIT

 

Inrmsz

opHmuso

mesmcfl

.mwusuonQEmu onmuso mEouuxm

m
9

L'1I i IIIIII

 

IIIIIIIIt
urmflz

 

A

.v ousmHh

 

(PITQ/WJD)
notietfqueA

(a Esp)
exniexadmem

69

Maximum system temperature for the day was 83.8 degrees F;
minimum was 64.5 degrees F; and the mean was 74.2 degrees
F. The resulting temperature range for the day of 19.3
degrees was wider than that of any of the constant ventila—
tion rates tested (Table 4.1). The ventilation rate
remained at 3.0 cfm/bird except for the 3:00 a.m.-10:30
a.m. period, reflecting the fact that lower ventilation
rates are required to maintain a given temperature differen-
tial during the warm portion of the outside temperature
cycle. This is due to a combination of lowered sensible
heat production by the birds and an increased evaporation
rate caused by lower moisture concentrations in outside
air.

Ventilation rate for the day also averaged 3.4 cfm/
bird for the extreme outside conditions with system temp-
eratures ranging between 91.0 and 74.0. Mean system
temperature for the day was 83.6. Ventilation rate exceeded
the 3.0 cfm/bird base from 3:00 a.m.-9:30 a.m. which was
one hour less than the period experienced with normal out—
side conditions. The range of 17.0 degrees was comparable
to that obtained with a constant ventilation rate of 4.5
cfm/bird for extreme conditions (Table 4.1).

Operational costs for the logic based control system
over a 4—month summer period using the previously developed
figures would be approximately $115.00 or a reduction of
23 percent as compared to the 4.5 cfm/bird constant rate
system. A comparison of performance with that predicted

for the 4.5 cfm/bird rate indicated that both maximum and

70

minimum daily temperatures for the system were higher with
the logic based control. Average daily temperatures,
however, were lower which reflected the desirability of
being able to increase ventilation rates during the cooler
part of the day. Daily temperature range was equal or

greater for the case of the logic based system.

5 . CONCLUSIONS

The following conclusions are based on simulations

and model verification studies conducted during this

research project.

1.

The simulation model developed in this study
provides an effective tool for the study of
structural and management factors influencing
summer environment for laying hens.

The floor slab, previously disregarded as an
insignificant contributor to environment,
plays a major role in the determination of
interior temperatures and evaporation rates.
Summer ventilation rates in excess of 4.5
cfm/bird (1.0 cfm/lb of body weight) will

not significantly reduce interior temperatures
during periods of extreme outside temperatures.
Ventilation rates higher than 4.5 cfm/bird are
effective in reducing the daily minimum system
temperatures experienced during the night or
cool period of the outside diurnal temperature

cycle. However, rates in excess of 5.5 cfm/

71

72

bird do not appear to be justified even

for night time conditions.

Housing density does not have a significant
effect on summer temperature profiles for the
system provided ventilation rates are based

on occupancy.

Placing the artificial day period in the
system out of phase with the natural day can
be used to modify temperature extremes and
place the period of maximum metabolic activity
in phase with minimum system temperatures.
Some phase relationships will significantly
reduce daily temperature range which previous
research has indicated will reduce the bird's
ability to cope with thermal stress.

The logic based ventilation control system
proposed in Section 4.5 reduces thermal stress
through increasing diurnal temperature range
and reduces operating cost for the ventilation
system by using maximum ventilation rates only

when they are effective in temperature control.

6. RECOMMENDATIONS FOR FUTURE WORK

The results of this research suggest the need for

additional work in the following areas:

1.

Investigation of bird heat production under
conditions of diurnally varying temperature.
A primary goal of this work would be the
development of a single function which can
make a smoother transition between day and
night rates than the two separate linear
interpolations used in this study.
Development of a ventilation rate control
system which employs differential sensing

to effect the type of ventilation control
discussed in Section 4.5.

Determination of the actual mass transfer
coefficients for evaporation of moisture
from the surface of wet manure.

A detailed investigation of the influence of
the concrete floor slab on environment within
the structure. This should include both the

the direct exchange of thermal energy with

73

74

the environment and the effect which the
slab temperature has on manure surface
temperature and subsequent mass transfer
rates. Of particular interest would be
the effect of either artificially heating
the floor slab or reducing its thermal
capacitance through the use of insulating
materials.

Determination of the economic benefits, if
any, to be obtained by reducing thermal
stress on the bird.

Reorganization of the simulation model so
that it could be used to study the struc-
tural and management factors which influence

winter environment in the poultry house.

 

REFERENCES

75

 

REFERENCES

ASAE Yearbook

1970

Published by American Society of Agricultural
Engineers, St. Joseph, Michigan.

ASHRAE Guide and Data Book

1963

Baker, V.
1958

Published by American Society of Heating,
Refrigerating, and Air Conditioning Engineers,
New York, New York.

H., M. Marshall, and C. E. Hawes

Poultry house ventilation design information.
Virginia Agricultural Experiment Station Bullee
tin 134. 20 pp.

Barott, H. G. and E. M. Pringle

1941

Energy and gaseous metabolism of the hen as
affected by temperature. Journal of Nutrition
22:3. 273-286 pp.

Barott, H. G. and E. M. Pringle

1946

Brooker,
1966

Energy and gaseous metabolism of chickens from
hatch to maturity as affected by temperature.
Journal of Nutrition 31:1. 35-50 pp.

D. B.

Mathematical model of the psychrometric chart.
ASAE Paper 66-815

Dhanac, A. M.

Drury, L.
1966

Esmay, M.
1966

Professor of Mechanical Engineering, Michigan
State University, East Lansing, Michigan.
Unpublished class notes prepared for ME 812.

N. and H. S. Siegel
Air velocity and heat tolerance of young chickens.
ASAE Transactions 9:4. 583-585 pp.

L., M. Saeed, and G. D. Wells

The psychrometrics of summer ventilation air
exchange in windowless poultry houses. ASAE
Paper 66-912.

76

 

77

Esmay, M. L.
1969 Principles of Animal Environment. AVI Publish-
ing Co., Westport, Conn. 325 pp.

Finch, D. I.
1962 General principles of thermoelectric thermometry.
Temperature-—Its Measurement and Control in
Science and Industry Vol. 3, Part II. 3-32 pp.

Holman, J. P.
1963 Heat Transfer. McGraw—Hill Co. 297 pp.

Jordan, K. A. and A. J. Barwick
1965 Periodic analog for ventilation design. ASAE
Transactions Vol. 8. 223-226 pp.

Leopold, C. S.

1948 Hydraulic analogue for the solution of problems
of thermal storage, radiation, convection, and
conduction. ASHRAE Transactions Vol. 54.
389-406 pp.

Lilleng, H.

1969 An investigation of how the inlet velocity,
direction, and temperature affect air flow
patterns and temperature distribution in cage
laying houses. Research Report to the Depart-
ment of Agricultural Engineering, Michigan State
University, East Lansing (unpublished).

Livermore, J. N.
1943 Study of actual vs. predicted cooling load on an
air conditioning system. ASH&VE Transactions
Vol. 49. 287-308 pp.

Llewellyn, R. W.
1965 Fordyn--An Industrial Dynamics Simulator. Pri-
vatly published by R. W. Llewellyn, Box 5353,
Raleigh, North Carolina. 150 pp.

Longhouse, A. D., H. Ota, and W. Ashby
1960 Heat and moisture design data for poultry housing.
Agricultural Engineering 41:9. 567-576 pp.

Mackey, C. O. and L. T. Wright, Jr.
1944 Periodic heat flow--homogeneous walls or roofs.
ASH&VE Transactions Vol. 50. 293-312 pp.

Mackey, C. O. and L. T. Wright, Jr.
1946 Periodic heat flow--composite walls or roofs.
ASH&VE Transactions Vol. 52. 283-296 pp.

Odden, N.
1961

78

T.

Heat transfer and the temperature change of
ventilation air passing through a poultry house
attic. Thesis for the degree of M.S., Michigan
State University, East Lansing (unpublished).

Ota, H. and E. H. McNally

1961

Parmalee,

1952

Phillips,
1968

Reece, F.
1969

Poultry respiration calorimetric studies of
laying hens--Single Comb White Leghorns, Rhode
Island Reds, and New Hampshire x Cornish cross.
USDA ARS 42-43. pp. 34.

G. V. and W. W. Aubele
Radiant energy emission of atmosphere and ground.
ASH&VE Transactions Vol. 58. 85-106 pp.

R. E.
A computer analysis of heating costs in poultry
brooding. ASAE Paper 68-916

N. and J. W. Deaton
Factors affecting design criteria for ventilation
of windowless broiler houses. ASAE Paper 69-452

Roller, W. L. and A. C. Dale

1962

Saeed, M.
1966

Heat losses from leghorn layers at warm tempera—
tures. ASAE Paper 62—428

Psychrometric aspects of heat and moisture
removal from a poultry house by ventilation.
Thesis for the degree of M.S., Michigan State
University, East Lansing (unpublished).

Siegel, H. S. and L. N. Drury

1968

Physiological responses of chickens to variations
in air temperature and velocity. Poultry Science
47:4. 1120-1127 pp.

Squibb, R. L., G. N. Wogan, and C. H. Reed

1959

Production of white leghorn hens subjected to
high environmental temperatures with wide diurnal
fluctuations. Poultry Science 38:5. 1182-1183

PP-

Squibb, R. L.

1959

Relation of diurnal temperature and humidity
ranges to egg production and feed efficiency of
New Hampshire hens. Journal of Agricultural
Science Vol. 52. 217-222 pp.

Stewart, R. E.

1969

An analysis of environmental research needs.
ASAE Paper 69-454

79

Threlkeld, J. L.

1962

Thermal Environmental Engineering. Prentice-
Hall. 514 pp.

Wilson, W. O.

1948

Zawdu, F.
1966

Some effects of increasing environmental temper-
ature on pullets. Poultry Science 27:6.
813-817 pp.

A theoretical analysis of air velocity distri-
bution inside a ventilated room with a long slot
inlet. Thesis for the degree of M.S., Michigan
State University, East Lansing (unpublished).

APPENDICES

8O

APPENDIX A

COMPUTER PROGRAM LISTING

81

82

PROGRAM ENVSIM (INPUT9OUTPUT)
DIMENSION TDBO(48)9TNBO(4B)9RHO(48)9X0l48l9SVAO(48)9
1 BETAlAB)9SOLRADC48)9RINC(48’9SOLT‘48)9TDBI(“B)9
2 ELPNR(AB)9XX(IOT
READ OUTSIDE HEATHER DATA
READ l9 AVTDBO9RANGE9WBDEP
l FORMAT (3F5o0)
READ 29 (BETAlll9l=1948l
2 FORMAT (24F3.0/24F3a0)
READ 39 (RINC(I)9 131948)
3 FORMAT (20F4.0/20F4¢0/8F400)
READ START OF ARTIFICIAL DAY
READ 49 ITON
4 FORMAT (12)
READ STRUCTURAL VALUES
READ S9 CDEC9ICPHI9CLK9UDEC9IUPHI9ULK
5 FORMAT (2(F10.S.I3.F10.S))
READ 69 BLTH9NIDTH9HEIT
6 FORMAT (3F5.1)
READ HOUSING DENSITY
READ 79 DENSTY
7 FORMAT (F4.2)
CALCULATE DRY BULB TEMPS FOR THE DAY
TMIN=AVTDBO-RNGZ
DO 8 1:1912
B TDBO‘I)=TMIN*RNG£*(1.§COS(l(FLOAT(1)918.)/300l*3ol4)l
DO 9 1313930
9 TDBO(I)=TMINORNGZ*(lo-COS( ( (FLOATlll’IZol/1893’3o 14) l
' DO 10 1331948
10 TDBO‘1)=TMIN*RNGZ*(1.0COS(((FLOAT(I)'30.)/30ol*3.l4)l
CALCULATE WET BULB TEMPS FOR THE DAY
THB=AVTDBO-HBDEP
CALL PSYCRO (TUBO(21)9THB9TDP9A9B9C9D9E)
DO 11 1:1948
11 CALL PSYCRO3 (TDBO(I)9TDP9TUBO(I))
DETERMINE OTHER NEEDED PROPERTIES OF AIR
DO 13 1:1948
12 CALL PSYCRO (TDBO(I)9TWBO(I)9D9RHO(I)9XO(I)9SVAOlll9E9F)
DETERMINE INCIDENT SOLAR RADIATION FOR HORIZ SURFACE
DO 13 J=1948
l3 SOLRAD‘J)= SlN‘BETA(J) ’ 3.14/180.) * RINClJl
CALCULATE SOL-AIR TEMPERATURES
CALL SOLAIR (SOLRAD9PVO9TDBO9SOLT)
AVSOLT=OQ
DO 14 L=1948
14 AVSOLT=AVSOLTOSOLT(Ll/48o
OUTPUT PROGRAM RESULTS TO THIS POINT
PRINT 159
IS FORMAT (1H196X9RDRY BULB TEMP NET BULB TEMP REL“9
1 * HUMIDITY SOLAR RADIATION SOL‘AIR TEMP”)

C

C
C

C

C

83

DO 16 J=1948
16 PRINT 179TDBO(J)9THBO(J)9 RHOlJ)9SOLRAD(J)9SOLT(J)
ll FORMAT (1H 95F15.2)
PRINT 189 AVTDBO9AVSOLT
18 FORMAT (1H099AVERAGE DRY BULB TEMP IS‘9F4.09* DEG“//
1 “AVERAGE SOL-AIR TEMP IS‘9F5.19* DEG F.)
ENTER AVERAGE BIRD HEIGHT
"BRDF-“OOS
SET UP ARRAY OF 0 AND 1 FOR PERIOD WHEN LIGHTS ARE ON AND
OFF ( 14 HOUR ON PERIOD)
IF (ITON .LE. 0) ITON=ITON048
ITOFF=ITON028
IF (ITOFF .GT. 48) 1019102
101 ITOFF=ITOFF-48
DO 103 1:1948
104 ELPHR(I)=0.
GO TO 103
105 ELPWR(I)=1.0
103 CONTINUE
GO TO 110
102 DO 106 1:1948
107 ELPHR(I)=1.0
GO TO 109
108 ELPWR(I)=0.
109 CONTINUE
106 CONTINUE
110 CONTINUE
CALCULATE NUMBER OF BIRDS IN SYSTEM
BRDS=BLTH*WIDTH/DENSTY
PUT HEADING ON OUTPUT SHEET
CALL HEADER
INITIALIZE VALUES USED IN SUMMARY
TIAVE=0.
RHIAVE=0.
TSLAB=AVTDBO
START DO LOOP WHICH STEPS THROUGH DAY
00 300 M=1948
IND=0
INITIALIZE ARRAY LOCATION VALUES
MM=M-ICPHI
MMM=M-INPHI
IF (MMM.LE.0) MMM=MMM948
VENTR=3o0
130 CONTINUE
START NEWTONIAN CONVERGENCE ROUTINE
XX(1)=TDBO(M)95.
DO 400 JK=199
CALCULATE FUNCTION AT T’.l

84

TI=XX(JK)‘01
CALL HEAT (TI9UBRD9BRDS9QSTOT9QLTOT9H9ELPHR(M)9AVTDBO9
1 ULKoNDEC9SOLTIHM)9CLK9BLTH9UIDTH9CDEC9HEIT9ONTOT9
2 QFTOT9XO(M)9SVAO(M)9TOBO(H)9EVAPT9VENTR9HTOTL9RHI9
3 TDBOIMMM)9FNA9ELHT9OCTOT9AVSOLT909TSLAB)
C CALCULATE FUNCTION AT T‘ol
TI=XXIJK)’01
CALL HEAT (TI9WBRD9BRDS9QSTOT9QLTOT9M9ELPWR(H)9AVTDBO9
1 HLK9HDEC9SOLT(HM)9CLK9BLTH9HIOTH9COEC9HEIT9OUTOT9
2 QFTOT9XO(H19SVAO(M)9TOBO(M)9EVAPT9VENTR9HTOTL9RHI9
3 TDBO‘MMH)9FNB9ELHT9QCTOT9AVSOLT909TSLAB)
C CALCULATE FUNCTION AT T
TI=XX(JK)
CALL HEAT (TI9HBRD9BROS9QSTOT9QLTOT9N9ELPHR(H)9AVTDBO9
1 ULK9HDEC9SOLT(MM)9CLK9BLTH9UIDTH9CDEC9HEIT9QUTOT9
2 QFTOT9XOTM)9SVAO(M)9TDBO‘H)9EVAPT9VENTR9HTOTL9RHI9
3 TDBO‘MMM)9FNX9ELHT9QCTOT9AVSOLT909TSLAB)
C DERIVITIVE APPROXIMATION BY FINITE DIFFERENCES
DFNX=(FNB-FNA)/o2
XX(JK*1)=XX(JK)’FNX/OFNX
IF (XX(JK*1)'XX(JK) oLEooO2oORoJKoEQo9) 604196040
401 TDBIIM1=XXTJK011
GO TO 402
400 CONTINUE
402 CONTINUE
C “9*““****“***99“ LOGIC CONTROL VENTILATION ROUTINE ***
IF (TUBI‘M) OLE. 550) 2009201
200 VENJR=VENTR'01
IND=1
GO TO 130
201 IF (TDBI‘H) 0LT. 600 00R. IND 0E0. 1) 1369202
202 IF (TDBOIM) 06E. 75.) 2039204
203 IF (VENTR 0E0. 405) 1369205
203 VENTR=4oS
GO TO 130
204 IF (TDBI‘M)-TDBO(M) 06E. 4.) 2069207
206 IF (IND 0E0. 3) 1369208
208 VENTR=VENTR901
IND=2
GO TO 130
207 IF (TOBI(M)'TDBO(M) oLE. 2. .AND. VENTR 05E. 2.0)
1 2099136
209 IF (IND oEQ. 2) 1369210
210 VENTR=VENTR*.1
INO=3
GO TO 130
C §§§OG§§§9§§ END OF CONTROL ROUTINE §5§§§*§§G§.§§§*§§§*
C UPDATE VALUES TO INSIDE TEMPERATURE CONDITIONS
136 TI=TOBI(M)
CALL HEAT (TI9UBRD9BRDS9QSTOT9OLTOT9M9ELPNR(M)9AVT0809
1 WLK9HDEC9SOLT(MH)9CLK9BLTH9UIDTH9CDEC9HEIT9QWTOT9
2 OFTOT9XO(M)9SVAOIM)9TDBO(N)9EVAPT9VENTR9HTOTL9RHI9

85

3 TDBO(MMM)9FNX9ELHT9OCTOT9AVSOLT919TSLAB)
C PRINT VALUES FOR THIS TIME PERIOD
PRINT 8009 M9TDBOIM)9RHO(M)9TDBI(M)9RHI9ELHT9QSTOT9
1 QLTOT9QCTOT9OHTOT90FTOT9HTOTL9EVAPT9VENTR
800 FORMAT (1H 9I49F5919F5929F6.19F59296FB.092F9909F8911
C CALCULATE MEAN VALUES FOR THE SUMMARY
RHIAVE=RHIAVE9RHII489
TIAVE=TIAVE9TDBI(M)/48.
300 CONTINUE
C PRINT SUMMARY FOR THE DAY
PRINT 4039 DENSTY
403 FORMAT (1H09*HOUSING DENSITY*9F4929*SQ FT/BIRD‘)
PRINT 4049 BROS
404 FORMAT(1H 9*TOTAL BIRDS IN SYSTEM*9F6.0)
PRINT 4059 ITON9ITOFF
405 FORMAT (1H 9*DAY STARTED AT“9I39* AND ENDED AT“9I3)
PRINT 4069 TIAVE
406 FORMAT (1H 9*AVERAGE INSIDE TEMPERATURE FOR THE DAYP9
1 F4.1)
PRINT 4079 AVTDBO
407 FORMAT (1H 9’AVERAGE OUTSIDE TEMPERATURE FOR THE DAY*9
1 F491)
PRINT 4089 RHIAVE
408 FORMAT (1H 9*AVERAGE INSIDE RELATIVE HUMIDITY FOR*9
1 “ THE DAY IS“9FS.2)
PRINT 4099UIDTH9BLTH9HEIT
409 FORMAT (1H 9*BUILDING SIZE*9F5.I9* FT. X'9F5919
I P FT. X*9FS.19* FTo’I '
C CALL TEMPERATURE PLOTTING ROUTINE
CALL PLOT (TDBO9TDBI9DENSTY9BRDS)
END

SUBROUTINE HEAT (TI9UBRD9BRDS9QSTOT9OLTOT9M9ELPUR9
1 AVTDBO9HLK9UDEC9SOLT9CLK9BLTH9UIDTH9CDEC9HEIT9QHTOT9
2 OFTOT9XO9SVAO9TDBO9EVAPT9VENTR9HTOTL9THI9TDBOZ9ONET9
3 ELHT9QCTOT9AVSOLT9INDIC9TSLAB)
REAL KHATT
C ELECTRIC POWER CALCULATED AT ONE MATT PER SQUARE FOOT
KWATT=BLTHRNIDTH/10009
C CALCULATE HEAT ADDED BY ELECTRICITY
ELHT=KHATT*3413.*ELPWR
C CALCULATE BIRD HEAT PRODUCTION
CALL BRDHT (TI9HBRD9BRDS9QSTOT9OLTOT9M9ELPHR)
C CALCULATE CEILING HEAT
CALL CEILHT(TI9SOLT9CLK9BLTH9NIDTH9CDEC9OCTOT9AVSOLT)
C CALCULATE HALL HEAT
CALL WALLHT (TI9TDBO29AVTDBO9HLK9HDEC9HEIT9BLTH9
1 H1OTH9QWTOT)
C CALCULATE FLOOR SLAB HEAT EXCHANGE
CALL FLORHT (TI9BLTH9HIDTH9QFTOT9TSLAB9INDIC)
C VENTILATION HEAT AND MOISTURE GAIN/LOSS

(TOCDF)O

86

CALL VENTHT (BRDS9XO9TI9QLTOT9VENTR9UIDTH9BLTH9HEIT9
1 SVAO9TDBO9EVAPT9HTOTL9RHI9TSLAB)

DETERMINE THE NET HEAT FLOH RATE PER HOUR
GNET=ELHTOQSTOT*QLTOT90CTOT’QWTOT‘OFTOT’HTOTL
RETURN
END

SUBROUTINE BRDHT (T9HT9BRDS9QS9QL9M9DALYT)

DIMENSION ARGS(7)9ARGL(8)9VSDAY(7)9VSNITE(7)9

1 VLDAY(8)9VLNITE(8)
DATA ENTRIES FOR BIRD HEAT PRODUCTION DETERMINATION

DATA (ARGSII)9I=I97)/2609340947.956.964.98409940/

DATA (ARGLII)9I=I98)/26093409470956096409740984.994.,

DATA (VSDAY(I)9I=197)/11.198.397.396.696.S96.39.2/

DATA (VSNITEII)9I=I97)/60996089601950395.I93.6906/

DATA (VLDAYTI)9I3198)II.792.192.393.293.393.494.295.3/

DATA‘VLNITE‘I)’IzlOBI/1.692.09109920692029200.3059407/

IF (DALYT oEQo I.) 192
DAYTIME HEAT PRODUCTION CALCULATIONS
I QS=WT*BRDS’TA8LI(VSDAY9ARGS9T97)

QL=HT*BRDS“TABLI(VLDAY9ARGL9T98)

RETURN
NIGHT TIME HEAT PRODUCTION CALCULATIONS
2 QS=WT*BRDS*TABLI(VSNITE9ARGS9T97)

OL=WT*BRDS*TABLI(VLNITE9ARGL9T98)

RETURN

END

SUBROUTINE PSYCRO (TDB9THB9TDP9RH9X9SVA9H9PV)
THIS SUBROUTINE DETERMINES AIR PROPERTIES FROM DRY BULB
AND HET BULB TEMPERATURES IN DEG F. IT RETURNS THE
FOLLOWING ITEMS DEN POINT TEMP9 REL. HUMIDITY9 HUMIDITY
RATIO9 SPEC. VOLUME OF AIR9 ENTHALPY
CONVERT INCOMING TEMPERATURES TO ABSOLUTE SCALE

THB=TWB9459.69 .

TDB=TDBO459.69
CALC. SATURATED VAPOR PRESSURE AT NB AND DB TEMPS

IF(TOB.LE.491.69) PSDB=EXP(23.3924-11286.64B9/TDB’

1 .46057*ALOG(TDB)1

IF(TDB.GT.491.69) PSDB=EXP(S4.6329’12301.688/TDB-

1 5.16923RALOG(TDB))

IFTTHB.LE.491.69) PSHB=EXP(23.3924-11286.6489/THB“

1 .460579ALOG(TWB))

IF(THB.GT.459.69) PSHB=EXP(54.6329-12301.688/TWB'

1 5.169239ALOGTTWBT)
CALC. LATENT HEAT OF VAPORIZATION FOR WATER AT TWB

IF (THB-491.69) 19293
I HWB=1220.B44“.05077§(TWB-459.691

GO TO 4
2 HW331075.B965

000

87

GO TO 4
3 HHB=1075.896S-.S6983*(THB*49I.69)
SLOPE OF WET BULB LINE
4 B=(.24OS*(PSUB'I4.696))lI.62194*HHB)
VAPOR PRESSURE DETERMINATION
PV=PSWB*B§(TDB'THB)
RELATIVE HUMIDITY
RHZPV/PSDB
HUMIDITY RATIO
X:.6219°(PV/(14.696-PV))
DEW POINT TEMPERATURE DETERMINATION
T‘491069
DO 5 N319680
T:T*QI
Q=EXP(54.6329'12301.688/T'5.16923*ALOG(T)I
IFTQ.LT.PV) GO TO 5
TDP=T
GO TO 6
5 CONTINUE
SPECIFIC VOLUME OF AIR IN CU FT/LB
6 CONTINUE
RHV=UNIVERSAL GAS CONSTANT FOR WATER VAPOR
RUV=37.7B
SVA=TX9RHV*TDB)/I144.*PV)
CALC. ENTHALPY OF AIR (BTU/LB OF DRY AIR)
IF (TDPOLTO‘091069) H=02405*‘IDB-459069) RX“ I 0448*1’08
1 ‘.01377*TDP9862.36)
IF(TDP.GE.491.691 H=.2“OS°ITDB'4S9.69)OX'(.448§TDB
1 ‘.01783*TDP*864.7168)
CONV. TEMPS BACK TO DEG. F FOR RETURN TO MAIN PROGRAM
TDB=TDB-459.69
TWB=THB'459.69
TDP=TDP-4S9.69
RETURN
END

SUBROUTINE SOLAIR (SOLRAD9PVO9TOBO9SOLT)
DIMENSION SOLRAD (4BT9PVO (4BI9 TDBO (48’9SOLT (48)
ALPHA=ABSORPTIVITY
EMIS=EMISSIVITY
HCONo=SURFACE HEAT TRANSFER COEFFICIENT
ALPHAzoS
EMIS=.S
HCOND=40 0
DO 1 K=194B
A! .173E'B ”(TDBOIK)*460.)*§4
DR=A-A*(.SS¢.33*SQRT(PVO(K)*2.036))
1 SOLTTK)=((ALPHAFSOLRAD(KI-EMISPDRT/HCOND)OTOBOTK)
RETURN
END

C

O (3 (3 D

O

88

SUBROUTINE CEILHT (T9ST9C9BLTH9HIDTH9CDEC909TAV)
TSIAV=AVERAGE INSIDE SURFACE TEMP FOR DAY

TSIAV=T*((.606*(TAV-T))/(.8560C))

TSI=TSIAV9CDEC*(ST-TAV)

OCEIL=1.6S*(TSI-T)

ACEIL=BLTH9HIDTH

Q=GCEIL*ACE1L

RETURN

END

SUBROUTINE HALLHT(T9TO9TOAVE9H9UDEC9HEIT9BLTH9WIDTH9O)
TWAVE=AVERAGE INSIDE WALL SURFACE TEMP FOR DAY

THAVE=T0((.606°(TOAVE-T))/(.8569H))

THS=THAVEOUDEC*(TO-TOAVE)

OWALL=1.65*(TwS-T)

0:HEIT*2.*(BLTH9UIDTH)*QHALL

RETURN

END

SUBROUTINE FLORHT (T9BLTH9HIDTH9Q9TSLAB9INDIC)
UTILIZ=PROPORTION OF FLOOR AREA NOT COVERED BY MANURE
UTILIZ=.25
HEAT FLOR PER SQ FT
HTFLO=1.65*(TSLAB‘T)
TOTAL HEAT FLOH
Q:HTFLO*BLTH“HIDTH*UTILIZ
IF (INDIC .E0. 1) 192
NEH SLAB TEMPERATURE
1 TSLAB=TSLAB-.S*HTFLO/22.12
INDIC=0
2 RETURN
END

SUBROUTINE VENTHT (BRDS9XO9T9QL9VENT 9HIDTH9BLTH9HEIT9
1 SVA9TODB9EVAPT9HTOTL9RHI9TSLAB)

CALC. MEAN AIR VELOCITY OUTSIDE BOUNDARY LAYER
VMEAN=3.*BRDS*VENT /(BLTH*HEIT*60.)

REYNOLDS NUMBER CALCULATION
REYNO=VMEAN*WIDTH/.000168

SURFACE FRICTION COEFFICIENT/2
CF2=OI44/REYNO**02

TEMP AT EDGE OF BOUNDARY LAYER
TEMP=(T*TODB)/2.

SURFACE TEMP OF MANURE
TSURF=(TSLABOTEMP)/2.

MEAN AIR DENSITY FOR BOUNDARY LAYER

or)

89

CALL PSYCRO (TEMP9TEMP9D9E9F9SVI9G9H)
CALL PSYCRO (TSURF9TSURF9A9B9XSATUR9SVSAT9C9D)
RHO=2./(SVSAToSVIT

SCH=SCHMIDT NUMBER
SCH-:06

COLBURN CORRELATION AND MASS TRANSFER COEFFICIENT
ST=CF2/SCH**.67
HD=ST°RHO*VMEAN

LATENT HEAT OF VAPORIZATION
VAPLH310750- 0569* (TSURF-320)
VLBS=BRDS*VENT*60.*RHO

BIRD MOISTURE PRODUCED AS LATENT HEAT
WATER:QL/VAPLH
X=X09NATERlVLBS

MOISTURE CONCENTRATIONS ACROSS BOUNDARY LAYER
CO=XO/(1.9XO)

CSURF=XSATUR/(1.*XSATUR)

SURFACE AREA AND EVAPORATION CALCULATIONS
AREA=.75*BLTH*HIDTH*2.
EVAPT=HD*AREA*3600.*(CO-CSURF)

CALCULATE HEAT OF EVAPORATION
HEAT=EVAPT*VAPLH

CALCULATE HEAT USED TO RAISE AIR TEMP
HAIR=VLBS*.24*(TODB"T)

HTOTL=HEAT 9 HAIR

CALCULATE INSIDE RH
XTOTL=X9ABSTEVAPTIVLBS)
PV=(14.7“XTOTLT/(.62190XTOTL)
PSDB=EXP(S4.6329‘12301.688/(T0459.69)-S.16923

1 *ALOG‘T94S9.69))
RHI=PV/PSDB

RETURN

END

SUBROUTINE HEADER
PRINT A HEADING FOR THE SUMMARY SHEET
PRINT 19
1 FORMAT (1H19*TIME OUTSIDE INSIDE*99X9“HEAT TRAN*9

1 *SFER RATES IN BTU PER HOUR*920X9*LBS H20 VENT*/
2 R TEMP RH TEMP RH ELEC SENS H *9

3 * LATENT CEIL HALL FLOOR VENT *9
4 “EVAP/HR CFM/BIRD“)

RETURN

END

SUBROUTINE PSYCRO3 (TDB9TDP9TWB)
THIS SUBROUTINE DETERMINES NET BULB TEMPERATURE AS A
FUNCTION OF DRY BULB AND DEN POINT TEMPS
TDB=TDB94S9.69

90

TDP=TDP94S9.69
THB=491.69
PV=EXP(54.6329-12301.688/TDP-5.16923‘ALOGITDP)T
DO 1 J=19600
TVB=TwB+.1
HFG=1075.8965-.569839(TUB-491.691
PSHB=EXP(54.6329-12301.688/THB-5.16923‘ALOG‘THB)I
PVT=PSHB*B*(TDB-TWB)
IF (PVT .GE. PV) GO TO 2

1 CONTINUE

2 THB=TWB~4S9.69
TDB=TDB-4S9.69
TDP=TDP~459.69
RETURN
END

FUNCTION TABLI (VAL9ARG9DUMMY9K)

C LINEAR INTERPOLATION FUNCTION FROM LLEUELLYN’S FORDYN
DIMENSION VAL(K)9ARG(K)
DUM=AMAX1(AMIN1(OUMMY9ARG(K))9ARG(1))

DO 1 I=29K
IF(DUM.GT.ARG(I)) GO TO I
TABLI=TDUM-ARG(I‘1))‘(VAL(I)-VAL(I'1)TITARGII)
1 *ARG(I*1))*VAL(I’1)
RETURN
1 CONTINUE
RETURN
END

C THIS SUBROUTINE PLOTS INSIDE AND OUTSIDE TEMPERATURES FOR
C THE 48 TIME PERIODS OVER A RANGE OF 35-100 DEGREES F
SUBROUTINE PLOT (TDBO9TI9DENSTY9BRDS)
DIMENSION LINET130)9TDBO(5819TI(4B)
INTEGER DOT9BLANK9ZERO9STAR9M9N
DATA BLANK9DOT9ZERO9STAR/1H 91H.91HO91H*/
C PUT READING ON THE ORDINATE AXIS
PRINT 10009
1000 FORMAT (1H1955X9*TEMPERATURE“/14X9*4O’918X9”50*918X9
1 *60*918X9*709918X9‘80’918X9*90*918X9*100*)
PRINT 10019
1001 FORMAT (1H 913K96(*.*919X))
C PRINT A LINE OF DOTS
DO 1002 J=19130
LINETJT=DOT
1002 CONTINUE
PRINT 10039TLINE(K)9K=19130)
1003 FORMAT (1H 9 3X9130A1)
DO 1007 I=1948

91

C FILL LINE WITH BLANKS

1004

DO 1004 J=19130
LINE(J)=BLANK
CONTINUE

C PUT GRID MARKS AT 5 DEGREE INTERVALS

1005

DO 1005 J=l9130910
LINE(J)=DDT
CONTINUE

C LOCATE 0 AND * AT PROPER POINTS IN LINE

1010
1012

1011
1013
1015

1014

M=2.*(TDBO(I)-3S.)91.
N=2.*(TI(I)-3S.101.

IF (M.GT.130) 101091011

PRINT 10129

FORMAT (1H 950X9*0 VALUE OUT OF RANGE“)
M=IJO

IF (N.GT.130) 101391014

PRINT 10159

FORMAT (1H 9SOX9§X VALUE OUT OF RANGE“)
N8130

IF (N.LE.0) N=1

IF IMOLEOU) M=I

LINE(M)=ZERO

LINE(N)=STAR

C PRINT DATA LINE HITH POINTS IN IT

1006
1007

1008
1009

PRINT 10069I9(LINE(K)9K=19130)

FORMAT (1H 9 I291X9130A1)

CONTINUE

PRINT 10089 DENSTY

PRINT 10099BRDS

FORMAT (1H 9/?BIRD DENSITY IN SQ FT/BIRD IS‘9FS.2)
FORMAT (1H 9‘TOTAL NUMBER OF BIRDS IS‘9F7.0)
RETURN

END

 

APPENDIX B

VERIFICATION STUDY DATA

 

92

93

.uuososnuovcanu
mcwcuoa 99900

£993 aunt and 969090 «unsung: .uaaaa can
.965090 999969 .uocuuok EH93 .hvaoao aauuom «Hogan»:
95. 5.«. «.. 9.9. 95. 9.9. .9. 9.9. 55. 9..9 .9. «.9. .5. .... 5.. 9.95 ... 9.9. 9.
95. 9.9. 99. 9... 9.. 9.«. «c. 9.«9 .5. 9.99 .5. .... 95. 9... 9.. 9.«5 9.. 9.5. 5.
«5. 5.9. 99. 9... 5.. 9.«. «9. 9.«9 95. 9.99 95. 9... «5. ..9. 5.. 9.«5 ... 9... ..
95. ..9. 99. 9... 9.. 9.«. 95. 9.99 95. 9..9 .5. «.9. .5. 9... 95. 9.«5 95. 5.5. m.
9.. «.9. .9. 9... 9.. 9.9. 95. 9.99 9.. 9.59 95. ..9. 95. ..9. 9.. 9.95 9.. 9... ..
... ..9. 59. 9.5. 9.. 9.9. «5. 9.99 ... 9.99 ... 9.99 55. ..9. 9.. «.95 95. 9... 9.
... 5... 99. 9... .9. 9... 9.. 9.99 9.. 9.9. «.. 9.99 .5. 9.9. 95. 9.95 .5. 9.9. 9.
9.. 9.9. .9. 9.9. .9. 9.9. 9.. 9.99 59. 5.9. 99. 9.59 .5. 9.9. «5. 9.95 95. 9.9. 9.
9.. 9... 99. 9.9. «9. 9... 9.. 9.9. .9. 9... «9. 9.99 95. 9.«. 9.. ...5 9.. 9.«5 9.
.9. .... «r. 5.95 9.. 9.5. 9.. 9.«. «9. 9.9. 9.. 9.«. «5. 9.95 5.. 9.95 ... 9.95 on
.9. 5.5. 9.. 9.«5 9.. 9.9. 9.. ..9. «9. 9.9. 9.. «.9. 95. 9.95 9.. 9..5 9.. 9..5 99
n9. «.9. ... 9.95 9.. ..«5 99. 9.9. 9.. 9... ... 9.9. 9.. 9..5 «.. 9..5 9.. 5..5 5n
9.. 9.95 9.. 9.95 mm. 9.95 9.. ..9. 5.. n... 9.. 9.«. 9.. ...5 99. 9.55 99. 9.99 .n
9.. 9.«5 ... 9..5 5n. 9..5 .9. 9... 9.. ..5. 9.. ..9. 9.. ...5 99. 9..5 99. 9.95 99
99. ..95 99. 5..5 .9. 9.95 99. 9.9. ... 9.9. 9.. 9... ... ...5 9.. ...5 99. 9.95 .9
99. 9.95 .9.. 9.95 .9. 9.95 99. 9.9. 5.. «.9. 9.. 9.9. ... 5..5 «.. ..55 99. ..95 99
9.. 9.«5 5n. 9..5 ... 9..5 99. 9.9. 5.. ..9. 9.. 9... 9.. 9.95 «.. ..59 9.. 9..5 9n
... 5.95 59. 9..5 .9. 9.95 99. 9.5. ... 9.9. «.. 9... ... ..55 99. ...5 59. 9.55 «n
9.. ..95 .9. ...5 «9. 9.55 99. ..5. 9.. 9.9. 9.. 9.5. 9.. 9.95 59. 9.95 59. 9.55 99
9.. ...5 on. 9.95 99. 9..5 «9. 5... 9.. 9.9. 99. 9... «.. 9.9. 99. 9.95 .9. ..95 99
9.. ..95 99. 9..5 59. 5.95 .9. ..9. 9.. 9... 9.. 9... «.. 5.9. 99. ..95 99. 9.95 .9
9.. 5.«5 99. 9..5 99. 9.95 99. ..9. 9.. 9.5. ... 9... ... 9.95 59. 9.95 .9. 9.99 59
99. ..«5 9.. 5.95 9.. 9.95 .9. ..9. 9.. 9.5. 9.. 9... 9.. ..9. 99. ..95 59. 9.95 .9
5.. 9.«5 9.. 9.95 .9. 9.95 .9. ..9. ... 9.5. 9.. 9... 9.. ..9. 9.. 9.95 59. ..95 99
... 9.95 9.. 9.95 99. 9..5 99. 9.9. 5.. 5.9. 99. 9.«. 9.. 5.9. 99. 9.95 59. 9.95 .9
9.. ..«5 9.. 9.95 59. 9.95 99. ..9. 9.. 9.9. 9.. ..«. «.. «.95 9.. «.95 9.. 9.95 99
99. ..9. 5.. 9.95 9.. 9.95 ... 9.9. .9. ..9. 59. 9.59 9.. 9.95 9.. 5.95 9.. 9..9 99
99. 9... 9.. 9.9. 9.. .... ... 9.9. .9. 9.9. 59. 9.59 9.. 9.95 ... 9.95 9.. ..55 «9
99. 5... 99. 9.5. ... 9... 9.. 9.9. .9. 9.9. 99. 9.99 .5. 9.55 95. ..55 95. 9.99 99
99. «... 59. 9... 99. 9.9. ... ..9. 99. ..9. 9.. ..59 55. 9..5 95. ..95 .5. 9..9 9«
9.. 9.9. 99. 9... n9. 9.«. 5.. ..9. .9. ..9. «.. 9.59 .5. 9..5 95. 9..5 .9. 9.99 .«
9.. 9.9. 99. ..«. «.. 9.59 9.. 9.9. .9. 9.9. ... ...9 55. 9..5 99. 9..5 .5. 9.«9 5«
95. 9.59 9.. 9.99 95. 9..9 95. ..99 59. 9.9. 9.. 9.99 95. 5.95 9.. ..95 .5. 9.99 .«
«9. 9..9 «5. 9..9 .9. 9.99 «5. 9.99 .9. 5.9. 9.. 9..9 55. ..«5 9.. 9.95 55. 9.9. 9«
... 9.99 9.. 9..9 .9. 9... 95. ..99 ... 9.9. 9.. 9.99 9.. 9.95 9.. 5.«5 99. 9... .«
9.. ..9. .5. 9.«9 99. 9.9. 95. ..9. 9.. 9.9. 95. 9..9 9.. 9.9. 9.. ..95 .9. 9... 9«
9.. 9.9. 9.. ..9. 99. 9.99 .5. 9.9. 9.. ..9. 95. 9..9 9.. «.9. «9. 9.95 59. 9.9. 9«
.9. 5... 95. 9.9. 99. 9... .5. 9.9. 9.. ..9. 95. ...9 59. 9... «9. 9.«5 .9. ..9. ««
9.. ..9. .5. 9.9. .9. 9.99 95. 9.9. ... 9... 95. ...9 .9. 9.9. .9. 9.«5 99. 9.9. 9«
99. 9.9. 95. 9.9. .9. 9.99 .5. ..9. ... 9... 95. 9..9 99. 5.9. .9. 9.«5 .9. 9.9. 9
«9. 9... 9.. 9.«9 .9. ..9. .5. ..9. 9.. 9... 95. 9..9 9.. 9.95 ... 9.95 .9. 9... .
9o. 9... 95. 9.99 9.. 9.9. 95. 9.99 5.. 9... 95. 0.99 «o. n.99 no. 9.95 99. 9... 5
55. .... 55. 9.99 9.. 9.9. 95. 5.9. 5.. 9... 95. 9.59 .5. ..95 95. 9..5 .5. 9.9. .
.5. 9.9. .5. 9.99 «o. 9.9. «5. 9.«. 5.. .... ... 9..9 .5. 9.95 99. 9.95 .5. 9.99 9
95. ..9. 55. 9.99 9.. 9... 9.. ..9. ... 9.9. ... 9.99 .5. 9.95 99. ..95 .5. 9.9. .
«o. 9... .5. 9.99 9.. 9... 95. 9.9. 9.. «... 9.. 9.9. 9.. 9.95 9.. 9.95 95. ..9. 9
95. «.9. .5. 9.99 99. 9.9. «5. 5.». «.. 9.5. ... 9.9. 95. 9.95 9.. 9.95 95. 9.9. 9
9.. 5... .5. 9.99 «9. 9... 9.. 5... 59. 9.9. «.. 9.9. 55. 9.«5 «9. 9.95 95. 9.95 «
:9 9:99 :9 9:9» :9 9:99 :9 9:95 19 9x99 :9 9:99 :9 9:9» :9 9x99 :9 9:99
999999999 ..999. 999999999 9.99.. 9999—9999 9.999.
99.92. 99.9999 99992. 9999599 99.929 999.599 9..5

0 65¢ m :5“ c and

94

.9000 can Macao .uonuuoz
95. 5.«. 9.. .... 95. 9.99
95. ..«. 9.. 9... 95. 9.99
«5. ..9. 9.. ..9. 9.. «.99
9.. 9.9. 9.. 5.9. 5.. 9.99
9.. 5.9. 9.. 9.9. 9.. 9.9.
95. 9.9. 9.. 9... ... 9.«.
95. 9.9. 9.. 9.5. ... 9.«.
5.. 9... 9.. 9.9. 9.. 9.9.
9.. «... .9. 9.95 .9. 9.9.
9.. 5.5. .9. 9.«5 99. 9...
59. 9.9. .9. 9.95 ... 9.«5
.9. ..95 99. 9..5 «.. 9.95
.9. ..95 «9. 9.55 9.. «..5
99. 9..5 99. 9.95 .9. 9.95
... 5.55 5.. 9.9. 99. 9.«.
5.. ...5 5.. «.99 .9. ..99
... 9.95 5.. 9.9. 99. «.99
... 9.95 5.. 5.99 99. 9.9.
... 9.95 5.. 5.9. 99. ..9.
9.. 9.55 .9. 9.95 .9. ..99
9.. 9.55 «9. 9..5 .9. ..9.
99. 9.95 99. 9.55 59. 5.95
99. ..95 99. 9.95 9.. 9.55
99. 9.95 99. 5.95 9.. 9.95
99. 9.95 .9. 9.95 9.. «..5
99. 9.95 59. 9.«5 9.. 9.95
.9. ..95 59. 9.95 5.. ..95
9.. 9... «.. 9.9. 99. 9.5.
9.. 5... 9.. 9.5. .9. 9.9.
5.. 9... ... 9.9. 9.. 9.«.
5.. .... 9.. 9... 9.. 9.«.
«5. «.9. ... ..9. 9.. 9.99
95. 5.9. ... 9.9. 95. 9.59
95. 9.99 ... 9.9. 95. 9.99
.5. 9.59 9.. 9.99 95. 9.99
.5. 9.9. 9.. ..59 95. 9.99
.5. 9.99 ... 9.99 99. «.9.
9.. 9.99 95. 9..9 9.. 9...
.5. ..9. 95. 9.99 9.. «...
95. ..«9 .5. 9..9 .5. 9...
.5. ..«9 95. 9..9 95. 9...
.5. 9.99 95. 9.99 .5. 9.5.
«9. «.99 95. 9.99 9.. 9...
95. 9.99 55. 9..9 9.. 9...
9.. 9.99 55. 9..9 9.. 9...
95. 9.99 «5. 9..9 95. 9.99
.5. 9..9 95. 9.99 .5. 9.«9
95. 9..9 5.. 9.9. 95. ..99
19 9:99 :9 9:99 :9 9999
9999.999. ..999.
99.92. 99.9599
9 can

.auu: can 905090

.5. «.59 5.. 9.9.
.5. 5.99 9.. 9.«.
95. 9.99 ... 9.9.
«5. 9.9. 9.. 9.9.
95. ..9. 9.. 9.9.
95. 5.9. ... 9...
«5. ..«. ... 9.9.
«5. ..9. 9.. 9...
«5. 9.9. 9.. 9...
95. «.5. 95. 9.95
95. 9.95 .5. ..95
95. 9.95 95. «.95
95. 5.95 95. 9.55
.5. 9..5 .5. 9..5
«5. 9.55 95. 9.95
«5. 9.95 95. 9.95
«5. 9.95 95. ..95
.5. 5..5 .5. 9.55
95. «..5 55. 9.95
9.. 9.95 99. ..95
95. ..95 95. 9..5
9.. 9.95 9.. 5.95
95. ..95 co. n..5
9.. 9.95 99. ...5
95. ..95 95. 9..5
95. 9..5 «5. «.55
9.. ..55 ... 9.55
9.. ...5 9.. 9..5
9.. ..95 ... 9..5
... 9..5 9.. 9..5
5.. «.95 9.. 9.95
9.. 5.95 9.. 9.95
9.. 5.95 ... 9.95
0.. 9.95 0.. n.99
«5. 9.9. 9.. 5.9.
95. ..9. 9.. 9...
95. ..5. ... 9...
.5. 5... 9.. 9...
9.. 9... 95. 9.5.
55. «... .5. 9.5.
55. «... 95. ..5.
95. .... «5. 9...
95. 9.5. ... 9.9.
.5. 9.5. ... 9.9.
.5. 9.5. 9.. 9.9.
.5. 9.5. ... ..9.
95. 9.5. ... 9.9.
«5. 9... 9.. ..95
.9 9:95 :9 9:99
995999999 9.95..
99_9z«
9 as“

«uonunoz
95. 9.99
95. 9..9
95. 9.99
9.. 9..9
5.. 9.59
... 9.99
9.. 9.99
... 9.9.
9.. 9...
... «...
... «.95
9.. «.95
... 9.95
95. 5.95
9.. 9.95
9.. 9.95
9.. ...5
95. ...5
.5. «.95
«9. 9.95
.5. ..95
.5. 9.«5
55. 5.«5
55. ..95
95. «.95
9.. 9.95
... 9..5
9.. 9.55
.9. 9..5
99. 9..5
9.. ..95
... 9.95
9.. 9.«5
... 9.9.
... 9.5.
«5. 9.9.
95. 9...
.5. 9.9.
9.. 9.9.
55. 9.9.
55. 9.9.
95. 9.9.
«5. 9.9.
95. 9...
95. 9...
N6. no'o
«5. 9.9.
9.. ....
19 9199

9999599

.accau and 91090

9.. ..9. 9.. 9.95
9.. 9.9. ... 5.95
9.. 5.9. 9.. 9.95
9.. 9.9. ... ..«5
9.. 9.9. 9.. «.95
«5. 5... 9.. 9.95
95. 0.9. ... 9.n5
5.. ..«5 «.. 9.95
... 9.95 99. ...5
9.. 9.95 «.. ...5
9.. 9..5 99. 9.9.
99. ...5 .9. ..9.
mm. 9.95 cm. ..«9
5n. 5... on. 0.90
99. «.9. .9. 9.9.
.9. 9.9. 59. 9.9.
.9. ..«9 .9. 9.9.
.9. 9.9. .9. 5.9.
59. 9.9. 99. 9...
59. 9.9. 99. 9.9.
cm. 9.«. 9.. 5.99
.9. 9.«. 9.. 9.9.
oo. 9.90 no. 9.99
«.. «.«9 ... 9.«.
99. ..9. ... 9.«.
«o. 9.«. 9.. «.9.
9.. 9.«. 9.. 9.95
«o. 5.9. «5. 9.95
9.. 9..5 95. 9.55
9.. ...5 95. 9.95
.0. «.95 m5. o.n5
9.. ..95 55. 9.95
5.. ..«5 95. 9.«5
9.. ..9. 95. 9.9.
«5. 9.5. 95. 9.5.
95. 9.9. 5.. 9.9.
.5. «.9. 95. 9...
.5. 9.9. 95. ..9.
.5. «.«. 95. 9.9.
.5. 9.«. 55. 9.9.
.5. 5.9. 95. 9.9.
.5. 9.9. 95. 9.9.
55. 9.99 95. 9.«.
95. ..99 55. 9.«.
9.. 9..9 .5. ..«9
9o. ..99 55. 9.«.
55. ..99 .5. ..9.
.5. 9.9. 95. 9.9.
:9 9:95 99 9:99
9950—9999 9.256.
99.92_

a flux

.uonuoox
5.. 9... c.
5.. 9.5. 5.
5.. 9.5. ..
... 9.5. 9.
5.. 9.5. ..
5.. 9... 9.
... 9.9. 9.
99. ..95 9.
.9. ...5 9.
.9. 5..5 99
99. ...5 cm
«9. 9.9. 59
9.. 9.«. .9
5.. «.9. 99
9.. «.9. .9
... 9.9. an
9.. 9... 9»
9.. 9.9. 99
5.. 9.9. 99
... 9.99 99
9.. 9... c9
9.. 9... 59
99. 9.99 .9
99. 9.9. 99
.9. 9.9. .9
.9. «.99 99
.9. 9.«. 99
59. n.99 9N
99. ..59 99
«.. 9.95 9«
9.. 9.95 .«
9.. 9.99 5«
... ..9. .«
5.. 9.5. 9«
9.. 9... .9
95. 9.9. 9«
55. n.9n 99
.5. 9.99 ««
55. 9.59 9«
55. 9..9 o
c5. 9..» o
55. 9..9 5
.5. 9.99 .
9.. 9..9 .
9.. «..9 .
99. 9..9 9
99. ..99 9
55. 9..9 9
:9 9:99
9c_mhao wx_5

955

.uqlna and 000 .hqu

90. ..95
90. .995
00. 9.05
00. 0.55
90. 9.05
90. .9.90
90. 0.90
90. ..90
55. 9..0
95. 9.50
90. 9.00
00. 9.50
«5. 9.00
90. 0.99
00. 9.90
90. 0.99
90. 9.99
99. 5.09
90. «..9
90. 9.09
00. 0.99
99. 0.99
.0. 0.99
00. «.99
00. 9.99
90. «.99
90. 0.99
90. 9.99
00. 0.50
«5. 9.50
95. «.50
95. 9.00
95. 0..:
95. 0.90
95. 9.90
«0. 9.«.
.0. 9.90
00. 9.05
50. 9.05
00. 9.55
50. 9.05
00. 5.05
90. 5.05
90. 0.05
90. 5.05
.0. 9.95
90. 9.05
90. 0.55
19 9:09
9090.9999
90.92.

.9000003
00. 9.05 99. 9.95
50. 0.05 99. 9.95
90. 9.55 «o. 9..5
90. 9.05 90. 9.95
90. 9.95 00. 9.05
90. 9.«. 90. 0.05
90. 9.«. .0. 9.95
.9. 9.99 «9. ..99
05. «.90 .5. 9..0
95. 9.00 95. 9.00
«5. 9.90 90. ..00
95. 0.50 00. 9.50
«5. «.90 90. 9.90
50. 0.«9 «0. 0.99
00. 5.«9 90. 9.99
90. .... 99. 9.59
90. 9..9 90. 9.99
90. 9.99 5.. 9.«9«
50. 0.99 99. 9.09
90. 9.99 9.. «.«9«
90. 9..9 59. 9.09
.0. 9..9 0.. «.«9«
90. 9.99 99. 0.59
«9. «.«o 09. 9.99
95. 0.99 90. 9.99
90. 9.«9 .9. 9.99
90. 9.99 99. 9.99
95. 9.99 99. 9.99
95. 9.59 09. 9.99
55. 9.09 90. 9.99
59. 9..9 95. «.00
09. 9.90 «5. 9.90
«o. 9.99 55. 9.99
0.. 9.99 95. 9.99
«9. 0.95 .0. 9.05
09. 9.05 99. 9.55
99. 0.55 99. 9.05
«o. 9.95 99. 9.05
99. 0.55 90. 9.05
99. 9.55 99. 5.95
99. 9.55 «9. «.05
«o. 9.95 90. 0.05
«o. 9.95 59. 9.05
«o. 9.95 59. 9.55
9.. «.95 00. 9.55
99. 9.95 99. 0.05
99. 9.95 99. 9.55
59. 9.95 99. 9.05
:9 9299 :9 9109
.(th‘

w:_m9:o
9« :99

.0900 Add) 9::50

90. 0.05 50. 9.05
90. 9.05 50. «.05
.5. ..95 .9. 9.95
05. 9.95 99. 9.99
95. 9.90 90. 9.90
.5. 0.90 90. 9.99
.5. 9.«0 90. 5.99
95. 0.«0 «0. 0.«9
«5. 5.99 «0. 9.99
90. 9.99 95. 9..9
00. «.09 05. 9.99
99. 9.09 55. 9.09
.0. 9.59 .5. 9.09
.0. 9.09 05. ..09
.0. 0.59 .5. 9.59
.0. «.59 05. «.09
.0. ..50 «5. «.09
.0. 0.00 95. 9.99
90. 9.99 95. 9..9
50. 9.99 .5. 9.99
00. 9.99 95. 0.«9
00. 9.99 95. 9.«9
90. 9.99 95. 9.«9
.0. 5.99 95. 5.99
90. 9.99 95. 9.«9
90. 9.«0 95. 9.95
.0. 9.99 «5. 9.95
00. 9.05 00. 9.55
50. «.55 95. 5.95
50. ..05 90. 9.95
50. 9..5 95. 0.95
00. 9.95 00. 9.95
90. 9.95 90. 9.«5
95. 9.«5 90. 9.«5
95. «.95 95. 9.90
95. 9.90 95. 9.90
.5. 9.90 95. 9.90
05. «.50 95. 9.50
05. 9.50 .5. 9.00
55. «.50 05. 0.50
99. 9.00 05. «.50
95. 9.00 05. 9.50
95. 9.50 05. 9.50
95. 5.50 05. 9.50
95. 5.50 95. 0.50
90. 9.00 99. 9.50
99. 9.50 90. 0.59
99. 9.50 05. 9.00
99 9:99 29 9:99
9999.9999 9.999.
99.92.
«« :99

«Masada!
99. 9.55
«9. 9.05
559 0.95
95. 9H95
.5. 9 95
95. 9.90
95. 9.90
«5. ..«0
00. 9.90
00” 5H9.
9. ....
90. 9.50
90. «.59
99. 9.90
99” .u59
09. 9.50
9. ....
00” 9u«0
.9 5 «9
... .9...

0 9
90. ..«0
59. 9.99
M0. 9H95

0. 9 95
90. ..55
90. 0.95
.0. 9.95
.0. ..95
90. 9.95
00” 0Uo5
9. a.
«5. 9.00
.5. 9.00
95. 0.90
55. 9.90
95. 9.90
99. 9..0
05. «.90
95. 0.90
95. 9.00
95. 9.90
.9. 0..0
99. «.90
99. «.00
19 9199

99.0909

au«> 50:0«0 0:0

. agfih 80509 N G

90. 9.50 90. 5.50
.0. 9.00 00. 9.50
90. 9.00 90. 9.50
90. ..50 «0. 9.00
90. 9.50 90. «.00
90. 0.50 «0. 9.00
90. 0.50 95. 9.90
90. 5.00 55. 9.90
95. 9.90 55. 5.95
05. 9.«5 05. «.«5
55. 9.95 05. 9.95
«5. 0..5 95. 9..5
.0. 9.05 00. «.95
90. 9.95 00. 9.95
90. ..55 «0. 0.05
59. 0.95 90. 9.55
99. 0.55 «0. 9.05
90. 9.05 .0. 5.95
«0. ..05 «0. 9.05
99. 9.90 09. «.05
99. 9.«0 59. 9.05
«9. 5.90 90. 9.05
.9. «.95 99. 9.95
99. 0.05 90. 9..5
50. 9.«5 90. 9.95
50. 9.00 «5. «.50
90. ..50 95. 9.00
95. ..00 05. 5.90
«5. 0.00 .5. 9.00
00. 0.00 95. 0.90
90. 9.00 .5. 9.90
95. 0.90 90. 9.90
95. ..9. 95. 9.90
95. 9.90 05. 9.00
05. 0.90 «0. 0.99
90. 9.09 90. 0.59
.0. 5..9 90. «.99
99. 0.«9 90. 0..9
99. 9.99 90. 9.99
00. 9.99 05. 9.99
99. 9.99 90. 9.99
90. 9.99 05. ..99
99. 0.99 55. 9.99
00. 9.99 55. 5.99
90. 9.99 05. 9.09
00. 5.99 55. 0.09
90. «.99 05. 5.59
99. «.09 05. 5.09
19 9299 99 9:9.
9099.9uza 9.999.
99.92.

ca cam

009990 .uonunox
.0. 9.90 0.
50. 0..0 5.
00. 9..0 0.
90. ..90 9.
90. 9.90 ..
90. 9.90 9.
.0. 5.90 9.
«0. 9.50 «.
95. 0.50 9.
90. 5.50 99
«0. 0.00 09
«5. 9.95 59
«0. 9.95 09
90. 9..5 9»
.9. 9.55 .9
99. 9.95 99
.9. 9.55 99
09. 0.95 «9
99. 9.95 99
99. 9.90 99
9.. 9.90 09
9.. 9.«0 59
0.. 9.05 0m
0.. 9.95 99
.0. 0.90 .9
90. 9.00 99
50. 9.90 99
00. 0.90 «9
90. 9..0 99
90. 9..0 9«
50. 9..0 09
«5. 5.90 5«
«5. 9.90 0«
00. 9.90 9«
90. 5.09 .«
00. 9.99 9«
99. 9.90 9«
99. 9.5. ««
99. 9.0. 9«
99. 9.9. 9
09. 9.0. 0
99. 9.9. 5
99. 0.0. 0
99. 9.0. 9
00. ..9. .
99. 0.9. 9
59. 9.«9 9
.0. 0.99 9
1; 9109
09.9999 92.9

96

09. 0.00
09. 0.~0
99. 0.00
09. 0.00
99. 0.00
09. 0.00
09. 0.00
09. 9.00
09. 0.00
«9. 0.90
99. 0.00
99. 9.00
99. 0.00
00. 0.99
00. 0.99
00. 0.99
90. 0.99
00. 0.99
«0. 0.09
00. 0.99
00. 9.09
00. «.09
00. 0.09
00. 9.09
00. 9.09
00. 0.09
00. 9.09
99. 0.09
99. ~.~9
00. 0.09
00. 0.09
09. 0.99
99. 0.99
09. 0.99
09. 9.99
09. 0.00
09. 0.00
90. 9.00
90. 9.00
«0. 0.00
90. 9.00
90. 0.00
90. 9.00
90. 0.00
09. 9.00
09. 9.90
90. 0.90
90. 0.00
10 0:09
9099.9u00
09—029

.:909 uaouvaauouaw
dud? 9000 6:0 965090

uuonuuoz
90. 0.00 00. 0.00
00. 0.00 00. 0.00
90. 0.00 00. 0.00
90. 9.00 90. 9.00
09. 0.00 00. 9.00
09. 9.00 09. 0.00
09. 0.00 90. 9.90
09. 0.00 90. 0.90
99. 0.00 09. 9.90
99. 0.00 90. 9.00
90. 9.00 99. 9.90
99. 0.00 99. 0.90
09. 9.90 09. 0.90
99. 0.90 09. 0.00
09. 9.00 99. 0.90
«9. 0.00 09. 0.00
09. 0.00 00. 0.00
99. 0.00 00. 0.00
00. 9.99 00. 9.99
90. 9.99 00. 9.00
00. 0.99 00. 0.00
00. 9.99 00. 0.90
00. 0.99 00. 9.90
00. 0.99 00. 0.00
09. 0.99 09. 9.00
N9. «.99 99. 0.90
09. 0.99 99. 0.90
99. 0.99 99. 9.00
09. 0.00 09. 0.00
09. 0.99 99. 0.90
99. 0.99 99. 0.90
90. 0.00 09. 0.00
90. 0.00 09. 0.00
00. 0.90 00. 0.00
90. 0.90 90. 0.90
00. 9.90 90. 0.90
00. 0.00 00. 0.00
00. 0.00 90. 9.00
00. 9.00 90. 9.00
00. 9.00 90. 0.00
00. 0.00 00. 0.00
90. 9.00 00. 9.00
90. 0.00 90. 0.00
00. 9.90 00. 9.90
90. 0.90 00. 9.90
90. 0.00 00. 0.90
90. 9.00 00. 9.00
00. 0.00 00. 0.00
:0 0:09 :0 0009
.09900
ma_m9:o
m H 9.93“

.uuoabnnuovcdnu

90. 0.00 00. 0.99
90. 0.99 00. 9.99
90. 0.99 00. 9.99
90. 0.99 00. 9.99
90. 0.99 90. 0.99
09. 9.99 09. 0.09
09. 9.09 90. 0.09
99. 0.09 00. 9.09
09. 0.09 09. 0.09
09. 0.09 09. 0.09
00. 9.90 00. 0.09
90. 0.00 00. 0.00
00. 0.00 90. 9.90
00. 9.00 00. 9.00
90. «.00 N0. 9.90
90. 9.90 00. 0.00
90. 9.00 00. 9.00
00. 0.00 90. 0.90
00. 0.00 00. 0.90
00. 0.00 90. «.90
00. 0.90 00. 0.90
00. 0.00 00. 0.00
00. 9.00 00. 0.90
00. 0.00 90. 0.00
90. 0.00 00. 0.00
00. 0.00 00. 0.00
00. 0.00 09. 0.00
00. 9.00 09. 0.90
00. 0.00 09. 0.90
90. 0.00 09. 0.90
00. 9.00 09. 9.90
00. 9.00 09. 0.09
00. 0.90 09. 0.09
09. 0.90 90. 9.09
09. 0.99 00. 0.09
99. 9.99 00. 0.09
09. 0.09 00. 9.09
00. 0.09 90. 9.09
00. 9.09 90. 9.09
00. 0.09 00. 0.09
00. 0.09 00. 0.09
00. 9.09 90. 0.09
00. 0.09 90. 9.09
00. 0.09 90. 9.09
00. 9.09 00. 9.09
0 . 0.09 00. 0.09
00. 0.09 00. 9.09
00. 9.09 00. 0.09
10 0:09 :9 0:09
9090_9000 00990.
09_mz.
09 cam

0:9:0»0 009: 09950
can 969090 aauunm

9 HOfiGOB
00. 0.00
00. 0.00
00. 0.00
00. 0.00
00. 9.00
90. 9.90
90. 0.90
09. 0.00
09. 9.99
09. 9.09
00. 9.09
00. 9.09
00. 0.90
00. 0.00
00. 0.00
00. 9.90
00. 9.90
00. 9.00
90. 9.00
00. 9.00
00. 0.00
00. 0.00
00. 0.90
90. 9.00
00. 0.00
90. 0.00
90. 9.00
00. 0.09
99. 9.09
90. 0.09
00. 0.09
99. 9.09
99. 0.09
99. 0.09
00. 0.99
00. 0.00
90. 0.00
00. 0.90
00. 9.00
00. 0.00
90. 0.00
90. 0.00
90. 9.00
00. 0.00
00. 0.00
09. 9.99
00. 0.99
00. 9.99
;a club

09_0909

.0055: 0:0

ac: .maunuoa 90900 :9 00h .uonuno:
00. 0.09 00. 0.09 90. 0.99 00
00. 0.09 90. 9.99 00. 9.99 90
00. 0.99 00. 9.09 00. 9.09 00
00. 0.09 00. 0.09 00. 9.09 00
90. 9.09 90. 0.09 00. 0.09 00
99. 0.00 «0. 9.00 09. 0.00 00
09. 0.00 90. 0.00 09. 9.90 «0
09. 0.00 09. 0.00 99. 9.00 90
09. 9.00 99. 0.00 99. 0.90 90
99. 0.00 09. 0.00 00. 0.00 00
00. 0.90 99. 0.00 90. 0.00 00
90. 9.00 00. 0.90 00. 0.90 90
99. 9.90 00. 9.90 00. 0.90 00
00. 0.90 00. 0.90 00. 0.00 00
90. 0.90 00. 0.90 00. 9.00 00
90. 0.90 90. 9.90 00. 9.00 00
99. 0.90 00. 9.90 00. 9.00 00
00. 0.00 00. 0.00 00. 9.90 90
00. 9.00 00. 0.00 00. 9.90 90
00. 0.00 00. 0.90 90. 0.00 0m
00. 0.00 00. 0.90 00. 9.00 00
00. 0.90 00. 9.00 90. 0.00 90
99. 0.90 09. 9.00 90. 9.00 09
00. 0.00 09. 9.00 00. 9.00 09
00. 0.00 09. 9.00 00. 9.00 00
99. 0.00 00. 9.90 09. 0.09 00
09. 0.00 90. 0.09 00. 0.09 «a
09. 0.90 00. 9.09 «0. 9.00 9~
09. 9.90 «0. 9.09 90. 0.09 9N
99. 0.00 00. 9.90 00. 0.09 09
99. 9.00 90. 9.90 00. «.09 09
99. 0.00 00. 9.90 00. 0.99 99
09. 9.00 90. 0.90 90. 0.09 09
09. 0.90 «0. 0.09 00. 0.09 09
90. 0.90 00. 9.99 00. 0.09 09
90. 0.90 90. 0.09 00. 0.99 09
90. 0.09 90. 0.09 90. 0.99 09
90. 0.09 90. 0.09 90. 9.00 99
90. 0.09 90. 0.09 90. 9.00 99
00. 0.09 90. 0.09 00. 9.00 0
00. 0.09 00. 0.09 00. 9.00 0
00. 0.09 90. 9.09 00. 9.90 9
00. 9.99 90. 0.09 00. 0.99 0
00. 0.09 90. 0.09 90. 9.09 0
00. 0.09 90. 0.99 90. 0.09 0
00. 0.09 00. 9.09 90. 9.09 0
.0. 0.90 00. 0.09 00. 0.09 0
00. 0.90 00. 0.90 00. 9.99 9
I: 0209 10 0109 1; 0x09
90.099u20 942990

09.02. 09_m999 0:.»

ma cum

97

.huooun

.Muooun 000 unoHU 09000008 000 000090 hauuum .9000003 .0985: 000 9000990 .auum «hands»:
09. 0.99 09. 0.99 09. 0.00 99. 0.99 09. 9.09 09. 0.00 09. 0.90 00. 0.09 00. 0.09 00
09. 0.99 09. 0.09 09. 9.00 09. 0.09 09. 0.09 99. 0.00 09. 0.90 90. 9.09 00. 0.00 90
09. 9.99 09. 0.09 09. 0.00 09. 9.09 99. 0.09 90. 0.00 99. 9.90 90. 0.09 90. 0.09 00
09. 9.09 09. 0.09 99. 0.00 09. 0.09 99. 9.09 90. 0.00 09. 0.90 00. 9.09 00. 0.09 00
99. 9.09 09. 0.09 09. 9.90 09. 0.09 09. 9.09 90. 0.00 09. 0.90 00. 9.90 00. 9.99 00
99. 0.09 99. 0.09 99. 0.00 09. 0.09 09. 0.09 99. 9.99 90. 9.00 90. 0.90 90. 0.99 00
99. 0.09 99. 0.09 99. 0.00 09. 0.09 09. 9.09 99. 9.99 90. 0.90 00. 0.90 90. 0.09 00
00. 0.99 00. 9.09 90. 9.99 99. 0.99 09. 0.09 09. 9.09 90. 9.90 00. 0.90 00. 9.09 90
00. 9.99 99. 0.09 00. 0.09 09. 0.99 «9. 9.99 09. 9.09 09. 0.90 00. 0.90 00. 9.09 90
90. 9.00 00. 0.09 90. 0.09 00. 9.90 99. 0.99 00. 9.09 99. 0.00 90. 9.90 00. 0.09 00
00. 9.00 00. 9.90 00. 9.09 00. 0.00 99. 0.09 00. 0.09 99. 0.90 90. 0.00 99. 0.90 00
90. 0.00 90. 0.90 90. 9.90 90. 0.00 00. 0.09 00. 0.09 09. 9.90 90. 9.00 09. 0.90 90
00. 9.00 00. 0.00 90. 9.90 90. 0.00 00. 0.09 90. 0.09 09. 0.90 09. 0.00 09. 0.90 00
00. 0.00 90. 0.00 90. 9.00 00. 0.00 90. 9.90 00. 0.99 99. 0.90 09. 0.00 09. 0.90 00
90. 9.00 00. 9.00 90. 0.00 00. 0.00 00. 0.90 00. 0.90 99. 0.90 09. 9.00 99. 0.90 00
00. 0.00 00. 0.00 00. 0.00 00. 0.00 90. 9.00 00. 0.90 99. 9.00 09. 0.00 09. 0.90 00
00. 0.90 00. 9.90 00. «.00 00. 9.00 00. 0.00 90. 0.90 00. 0.90 09. 0.00 00. 0.90 00
00. 0.00 00. 9.00 00. 9.00 90. 0.00 00. 9.00 00. 9.90 90. 0.00 99. 0.00 00. 9.00 90
90. 0.00 00. 0.00 90. 0.00 90. 9.00 90. 0.00 90. 0.90 99. 0.90 09. 0.00 99. «.90 90
00. 0.00 00. 0.00 00. 9.00 90. 9.00 90. 0.90 00. 0.09 00. 0.00 09. 9.00 00. 0.00 00
00. 0.00 00. 0.00 00. 0.00 00. 0.00 00. 9.00 00. 0.00 99. 9.90 09. 0.00 99. 0.00 00
00. 0.00 00. 0.00 00. 9.00 00. 9.00 00. 0.00 90. 9.90 09. 9.00 09. 0.00 09. 9.00 90
00. 0.00 00. 0.00 00. 9.90 00. 0.00 00. 0.90 00. 0.90 99. 9.00 09. 9.00 99. 0.00 00
00. 9.00 00. 0.00 00. 0.00 00. 0.00 00. 0.00 00. 0.90 00. 0.00 99. 0.00 00. «.00 00
00. 0.00 00. 0.00 90. 9.00 00. 9.00 00. 0.00 90. 9.90 00. 0.00 00. 9.90 90. 0.90 09
00. 9.00 00. 0.90 00. 9.90 00. 0.00 00. 0.00 90. 0.90 90. 0.00 00. 9.00 90. 0.00 09
90. 9.00 90. 0.09 00. 9.09 00. 0.00 00. 9.00 00. 0.90 00. 9.00 99. 9.00 00. 0.00 00
00. 0.90 00. 0.99 90. 0.09 00. 0.00 00. 9.00 90. 0.90 90. 0.90 99. 9.00 00. 0.00 90
00. 9.90 00. 0.09 90. 9.09 00. 0.00 90. 0.90 90. 0.90 90. 0.00 99. 0.00 90. 0.90 99
90. 0.09 00. 0.09 90. 0.99 00. 9.00 00. 0.90 00. 9.90 00. 0.00 09. 0.00 99. 0.90 09
90. 9.99 00. 0.09 90. 0.00 00. 0.00 99. 0.90 00. 0.09 90. 0.00 09. 0.90 99. 0.09 09
90. 9.09 00. 0.09 00. 0.90 00. 0.00 00. 9.90 99. 0.09 90. 0.00 09. 9.90 99. 0.09 99
00. 9.09 90. 0.09 90. 0.00 00. 0.00 99. 0.90 99. 0.09 00. 0.00 99. 0.90 09. 0.09 09
00. 9.09 00. 9.09 99. 9.00 90. 0.00 09. 9.90 09. 9.09 00. 0.00 09. 9.90 09. 9.09 09
00. 9.09 99. 9.99 09. 0.00 00. 0.00 09. 0.90 09. 0.09 00. 9.00 09. 0.09 09. 9.09 09
00. 0.09 99. 9.99 99. 9.90 09. 0.00 99. 0.90 00. 9.09 00. 9.00 09. 0.09 09. 9.09 09
90. 9.99 09. 9.00 09. 0.90 09. 9.00 00. 0.09 00. 9.09 99. 0.00 90. 0.09 90. 0.09 09
09. 0.00 09. 0.00 90. 9.90 90. 0.90 00. 0.09 00. 0.09 09. 9.90 09. 0.09 09. 9.09 99
99. 0.00 09. 0.00 90. 0.90 90. 9.90 00. 0.09 00. 0.09 09. 0.90 09. 9.09 09. 0.00 99
09. 9.00 09. 9.00 09. 9.90 00. 0.90 00. 0.09 90. 0.09 09. 0.90 09. 0.09 09. «.09 0
99. 9.00 09. 9.00 09. 9.90 99. 9.90 90. 0.09 00. 0.09 09. 0.90 99. 0.09 09. 0.09 0
09. 9.00 09. 9.00 90. 9.90 90. 0.90 90. 0.09 00. 0.09 09. 0.90 09. 0.09 9.. 9.09 9
09. 9.00 09. 0.00 90. 9.90 90. 0.90 00. 0.09 00. 9.09 09. 9.90 09. 0.09 09. 9.09 0
99. 9.99 99. 0.99 09. 0.90 90. 0.90 00. 0.09 00. 9.09 09. 9.90 90. 0.09 09. 0.09 0
09. 9.99 99. 9.99 90. 0.00 90. 9.90 00. 0.09 00. 0.09 09. 9.90 09. 0.09 09. 0.00 0
99. 9.99 99. 0.99 09. 0.00 09. 0.90 00. 0.09 00. 0.09 99. 9.90 09. 9.90 09. 0.09 0
99. 0.99 09. 0.99 09. 9.00 09. 0.90 00. 0.09 .0. 0.09 09. 0.90 09. 9.90 09. 9.99 0
99. 9.99 99. 9.99 09. 9.00 09. 0.90 00. 9.09 00. 0.09 99. 0.90 90. 9.90 90. 0.09 9
10 0:09 :0 0:09 10 0:09 .0 0:0. :0 0:09 10 0999 :2 0:09 .0 020. :1 0x09

9099.9000 .00900 9099.:000 942900 9090.9070 002900
09.0.. 09.0.99 09.02. 09.0999 09.02. 09.0909 0:.»

ca cam 0H cam 0H cam

98

.coocuouua

.aaou .uu03bcn cw uuotonu aver 969090
cud: 9000 and avaoHU 9uonuuox sud) ouaan and unscau .uoaunox .mcchOE ad sun: can unmao 9uosu603
90. 9.00 90. 0.00 00. 0.90 00. 9.00 00. «.90 09. 0.00 90. 9.00 90. 9.90 00. 9.«0 00
99. 9.90 99. 9.90 no. 9.00 90. 0.90 09. 0.90 09. 0.00 99. 0.90 09. 9.90 «0. 9.n0 90
90. 0.00 09. 0.90 00. 0.00 00. 9.99 90. 9.90 99. 9.00 00. 0.00 99. 0.00 09. 0.00 00
09. «.90 99. 9.90 90. 0.00 90. 9.99 90. 9.99 90. 9.90 00. 0.90 00. 0.00 09. 9.00 00
«0. 9.90 90. 9.90 90. 0.00 90. 0.99 90. 0.99 99. 0.00 90. 0.90 90. 0.90 00. 9.00 00
00. 0.90 00. 9.90 «o. 9.00 90. 0.99 00. 0.99 00. 9.90 00. 0.00 90. 9.90 00. 0.00 90
«0. 0.90 90. 9.90 00. 0.00 00. 0.99 90. 0.99 09. 9.90 90. 0.90 90. 0.90 99. 0.00 «0
90. n.«0 90. 0.«0 00. 0.90 00. 0.99 99. «.99 00. 9.00 00. 9.90 00. 9.99 90. 0.00 90
09. 9.00 99. 0.00 90. 0.90 00. 0.99 90. 0.99 00. 9.00 00. 9.00 00. 0.99 90. 9.00 90
09. 0.00 09. 0.00 99. 0.90 00. 0.09 00. 9.«9 09. 0.00 «0. 0.«9 90. 0.99 99. 0.00 on
99. 0.00 09. 9.00 «0. 9.90 00. 0.09 90. «.«9 00. 9.90 90. 9.09 90. «.99 00. «.90 00
«9. 9.90 09. 9.00 09. n.«0 «0. 0.09 90. 0.«9 09. 9.00 90. 9.«9 90. «.99 9o. 0.00 90
«9. 0.90 «9. 0.90 09. 9.00 «0. 0.09 90. 0.«9 09. 9.00 90. 9.«9 90. 0.99 90. 9.90 00
«9. 9.00 09. 9.00 09. 0.90 «0. 0.09 90. 9.09 99. 0.90 00. 0.«9 00. 9.99 no. «.00 00
00. 9.90 09. 9.00 00. 0.«0 «0. 0.09 90. «.09 00. 9.99 00. 0.«9 00. 0.99 00. 0.00 00
09. 9.00 09. 9.00 09. 0.00 00. 0.09 09. 9.«9 09. 0.00 «0. 9.«9 90. 0.99 «0. 0.00 00
99. 0.00 09. 0.90 99. 0.00 00. «.09 90. 9.«9 0o. «.00 90. 9.09 90. n.«9 90. 0.90 «n
«9. «.00 09. 0.90 09. 9.90 00. 0.09 09. 0.99 00. 0.90 99. 0.09 00. 0.«9 90. 9.00 90
09. 0.00 90. 0.«0 00. 0.00 00. 0.09 90. 0.«9 99. 0.00 «9. 9.09 09. 9.09 «9. 9.«9 90
99. 0.00 99. 0.«0 «0. 0.90 00. 0.09 90. 0.«9 00. 9.00 90. 0.09 99. 0.99 00. 0.09 0«
99. 0.90 90. 9.«0 00. 0.90 «0. 0.09 00. 0.«9 09. 0.00 90. 0.09 99. 9.09 00. 9.09 0«
09. 0.«0 90. 0.90 00. 9.00 09. 9.99 00. 0.09 90. 9.«9 00. 0.09 99. 0.09 «0. 9.99 9«
99. 0.«0 90. 0.90 «0. 0.00 99. 0.99 00. 0.09 00. «.09 00. 0.99 00. 0.09 90. 0.99 0«
90. 0.90 90. 0.90 00. 9.00 09. 9.09 99. 9.09 «0. 0.99 00. 0.90 90. «.99 00. 0.09 0«
90. 0.90 00. 0.90 00. 0.00 09. 0.09 90. 0.09 00. 0.99 00. 0.90 90. 0.99 00. 0.00 0«
00. 9.90 00. 9.90 09. 0.00 90. «.09 90. 0.«9 90. 9.99 00. 0.99 99. 0.09 00. 9.99 9«
00. 0.90 00. 9.90 00. 0.00 99. 0.09 00. 9.09 00. 0.99 00. «.90 00. 9.99 «0. 9.09 ««
90. 9.90 00. «.90 00. 0.00 99. 9.09 00. 0.«9 90. 9.99 00. 9.90 90. 0.09 00. 0.09 9«
90. 9.90 00. 0.90 09. 9.00 99. 0.09 00. 9.«9 00. 0.00 00. 9.99 90. 9.09 90. 0.00 9«
90. 9.90 00. 0.90 00. 9.90 90. 9.09 90. 0.99 00. 0.00 00. «.09 00. 9.99 00. 9.09 09
00. 9.90 00. 0.90 00. 0.00 09. 0.09 90. 0.99 90. 9.99 90. 0.09 99. 9.09 00. 0.09 09
99. 9.90 90. 0.90 09. 9.00 90. 0.99 90. 0.90 99. «.00 90. 0.09 99. 0.09 90. 0.«9 99
00. 9.90 00. «.90 00. 0.00 90. «.«9 90. 0.90 90. 0.00 «9. 0.09 09. 9.09 09. 0.99 09
00. 9.90 00. 0.90 00. 9.00 99. 9.99 00. 0.90 00. 0.00 99. 0.09 «0. 9.09 90. 9.99 09
00. 9.90 00. «.90 90. 9.00 «0. 0.90 90. 0.90 99. 0.00 99. «.99 «0. 9.«9 90. «.00 09
00. 0.90 00. 0.90 99. 9.00 90. 9.00 00. 0.00 00. 9.90 99. 9.«9 90. «.«9 «0. 0.00 09
00. 9.90 00. 0.90 09. 0.00 90. 0.90 99. 9.00 09. 9.90 90. 0.99 90. 0.99 99. 0.00 «9
90. 0.90 90. 0.90 00. 9.00 90. 0.00 90. 0.00 no. «.90 90. «.00 00. 0.90 «0. 9.00 99
00. 0.90 00. «.90 09. 0.00 90. 0.00 90. 0.00 00. «.90 00. 9.00 00. 9.00 99. 9.00 99
00. 9.90 00. 9.«0 00. 0.00 00. «.00 90. «.00 00. 0.90 00. 0.00 00. 9.99 00. «.00 o
00. 9.«0 00. 0.«0 00. 9.00 00. 9.00 00. «.00 09. 0.90 90. 9.90 00. 9.99 90. 9.00 0
00. «.«0 00. ..«0 09. «.90 00. 9.00 90. «.00 00. 0.90 00. 9.99 00. 0.99 00. 9.00 9
00. 0.«0 00. 0.00 «o. 9.00 90. 9.00 99. 0.00 09. 0.90 00. 9.90 00. 0.99 90. 9.00 0
00. 0.90 «0. 9.00 90. 9.90 90. 9.00 90. 9.00 00. 9.90 00. 9.90 00. 0.99 90. 0.00 0
00. «.00 00. 0.00 99. 0.00 90. 9.00 90. 9.00 09. 9.00 00. 9.99 «0. o.«9 00. 9.00 0
00. 9.00 00. 9.00 «o. 0.90 00. 9.00 90. 9.00 99. 0.90 00. 0.«9 09. «.09 00. 9.99 0
90. 9.00 90. 0.00 00. 0.90 00. 0.00 00. 0.00 90. 0.90 .0. 0.«9 09. 0.09 09. 9.99 «
90. 0.00 00. 9.00 00. 9.90 00. «.00 00. 0.00 00. 9.90 90. 0.«9 99. 0.09 99. 0.99 9
:9 0109 10 0109 :0 0:09 :0 0x09 :0 0:99 .0 0009 :0 0:09 .9 000. :0 0xm9
90.9.9000 .09900 9099.9000 909990 90.9.9000 909900
09.02. 09.9999 09.02. 09.0999 09.02. 09.0999 01.9

MN cam ou cam ad and

99

.0uo3bsu uaouuwauouca

099: 900990-909099

oo. v.o0
oo. n.00
09. 0.00
0o. 9.o0
oo. 9.99
00. «.99
no. 0.99
09. 0.n9
09. 0.09
«0. n.n¢
no. ”.00
90. 0.00
90. v.vc
90. n.0o
o0. «.0o
on. «.00
on. 9.00
an. 9.0:
no. 0.0:
no. o.v:
00. 9.00
00. n.90
00. 0.90
no. 0.9:
99. «.o9
99. 0.09
99. «.09
n9. «.99
«9. 0.09
n9. o.oo
«9. 0.09
ms. 9.09
no. o.09
«9. o.o9
on. 9.9:
mm. 0.09
n9. o.o9
oo. 9.99
«o. 0.99
«o. «.99
oo. 0.99
«o. «.99
oo. 9.99
«o. 0.99
9o. «.99
oo. 0.99
oo. 9.99
oo. 0.99
xx uxw9
om9u.nw¢a
09.02.

9uununox
00. 0.00 no. 9.00
90. 0.90 no. 9.00
00. 0.00 90. 0.00
00. 0.o0 oo. 9.00
n0. 0.99 9o. 9.90
90. 0.99 9o. 0.90
o9. 0.n9 0o. o.o0
99. 9.99 09. 0.«9
09. 9.99 99. 9.09
99. 0.09 00. 9.09
00. o.o9 n0. 9.99
90. 9.90 90. «.09
00. 0.90 90. 9.09
«0. 0.90 90. 0.90
00. 0.99 00. 0.90
«0. 0.«0 90. 0.no
n0. 9.«o n0. 9.«0
n0. 0.90 «0. 9.90
00. o.99 90. o.9o
99. 0.o9 00. 9.09
09. 0.99 99. o.09
o9. 0.09 09. 9.«9
«0. 9.09 09. 9.«9
«o. 0.09 09. 9.99
00. 9.n9 0o. 9.o0
0o. 0.n9 09. 0.90
9o. 0.«9 0o. 0.90
«o. 9.«9 no. «.00
9o. «.«9 «o. 0.00
9o. o.«9 no. 9.90
no. 9.«9 «o. o.90
no. «.n9 0o. 9.90
no. 9.n9 no. «.o0
no. 9.n9 9o. 0.o0
«o. 0.«9 oo. 9.o0
9o. o.99 «o. 9.o0
«o. 0.99 «o. 9.00
no. 9.99 oo. 0.90
no. o.99 9o. 0.90
no. 0.99 oo. o.90
«o. 9.99 9o. 0.o0
no. 0.99 oo. 0.90
no. 0.99 0o. 9.o0
no. 9.99 99.9 9.90
«o. 0.99 0o. o.90
«o. 9.99 9o. n.o0
90. 9.99 0o. o.o0
9o. «.99 0o. o.00
:0 0:09 :0 0:09

.¢29u<
wo—m920

vN as“

.mcwcuofi ouua :9
0903090 999: 909990

can Masada hauuum

90. 0.99 9o. 9.99
90. 0.99 00. 9.99
9e. 9.Ho on. c.9n
oo. n.99 oo. «.99
90. 9.o0 90. o.o0
00. o.o0 00. o.o0
09. 0.o0 0o. 0.99
00. 9.99 90. o.«9
00. 9.99 00. 9.n9
o0. «.09 00. 9.n9
00. «.09 00. 9.n9
oo. 0.99 no. «.no
00. 9.09 00. 0.n9
oo. «.09 0o. 0.n9
oo. 9.09 00. 9.n9
oo. 9.99 no. 0.«9
00. o.99 «o. 9.09
oo. 9.o9 99. o.09
oo. «.90 90. 9.09
90. n.90 99. 0.09
oo. o.90 n9. 9.09
90. o.o9 «9. 0.09
00. 0.09 n9. 9.09
90. «.99 99. 9.09
«0. 9.99 99. 9.09
on. 9.09 oo. 9.09
90. o.99 90. 9.09
o0. 0.09 00. 0.09
00. 9.09 90. 9.09
on. 9.09 oo. 0.n9
90. 9.99 09. 0.99
90. 0.09 09. «.99
«0. 0.n9 09. o.90
00. 9.99 o9. 0.00
00. 9.o0 o9. o.n0
00. 9.o0 9o. 0.o0
99. 0.90 00. 0.90
oo. 9.90 0o. 0.90
oo. 0.90 0o. 9.00
oo. 0.90 00. 9.00
oo. 0.90 00. «.00
oo. 0.o0 09. n.o0
9o. 9.o0 0o. o.o0
9o. o.o0 00. 0.90
9o. 9.90 00. 0.90
9o. 9.90 no. 9.90
oo. 0.90 no. «.«0
oo. o.90 o9. n.n0
0: 0:09 :0 0:09
9099.9000 909990
09.02.
n« can

9Honunu3
«o. o.00
9o. o.00
«o. n.00
0o. 0.90
99. «.00
9o. 9.90
9o. 9.90
9o. 9.90
00. 0.90
«0. 9.90
«0. 9.90
9o. o.90
90. 9.90
no. 0.90
no. 0.90
«0. 9.90
90. 0.90
09. 0.o0
00. 0.09
90. o.««
00. 9.09
90. 0.«9
o0. 0.o0
«0. 9.99
00. «.oo
o0. «.99
00. 9.99
on. 0.99
00. o.99
00. o.09
on. 9.o0
90. 0.00
oo. 0.n0
09. 9.90
o9. 0.00
09. o.00
0o. 9.«0
0o. 9.«0
no. 0.«0
0o. 0.«0
0o. o.«0
0o. 0.n0
9o. n.00
no. 0.00
«o. 0.00
«o. 0.00
9o. n.90
oo. 9.00
:0 0:09
09.0999

.hcns- can Macao

9o. o.om on. 9.90
«o. n.90 99. 0.90
«o. 9.90 o9. 9.«0
«o. 0.90 99. 9.00
99. o.«0 09. 0.00
99. o.n0 n9. 0.00
09. «.n0 n9. 0.00
09. 9.00 oo. 0.90
oo. 9.o0 00. 9.«9
on. 0.09 00. 9.09
90. 9.99 on. n.99
90. 9.99 90. «.o9
00. 0.90 00. 9.99
90. 9.99 00. 9.09
00. 0.«0 no. 0.99
00. 9.«0 00. 9.90
«0. 0.«9 n0. 0.90
00. 9.n9 n0. 0.99
00. 9.«9 00. 0.99
«0. 0.«9 n0. 9.99
no. 9.99 00. o.o9
me. 9.90 an. o.on
00. 9.99 00. 0.99
00. n.99 90. 9.99
90. 0.09 an. 0.09
«m. 0.09 an. 9.09
no. o.09 90. 0.n9
on. 9.n9 90. 9.99
9a. 0.99 «0. 9.99
on. 9.o0 00. o.90
«0. n.90 oo. «.00
00. 0.00 oo. 0.00
90. 9.n0 99. 9.n0
99. 9.«0 no. «.90
n9. 9.o0 no. o.on
on. 0.90 99. 0.9m
on. «.00 no. «.00
no. o.«0 oo. 9.nn
mo. n.«0 vo. 0.n0
oo. n.nm oo. 9.00
no. 9.n0 oo. 9.00
oo. «.00 no. 0.00
99. 9.00 no. 0.00
an. 9.00 no. «.00
no. «.00 oo. n.00
no. 9.00 99. 9.00
oo. 9.00 99. 0.90
on. 9.90 on. n.on
xx 0:w9 :u oxw9
9w9u.9000 909990
09.02.

«a 039

9909900:
00. 0.00 00
no. 0.nn 90
9o. n.00 00
90. n.90 00
00. 9.o0 00
90. 0.90 no
99. o.o0 «0
09. 0.n0 90
00. 9.00 90
«0. 9.n9 on
on. 0.99 on
on. 0.ou on
on. n.9o on
on. 9.oo on
on. o.no 0n
0n. 9.n9 nn
on. 9.00 «n
«n. 0.09 9n
«n. o.00 on
on. 9.nn o«
«n. 0.90 o«
0n. 0.99 9«.
on. 0.99 0«
nn. o.oo 0«
90. «.99 v«
00. 9.09 n«
00. 0.09 ««
00. «.no. 9«
90. 9.90 o«
n0. o.90 o«
90. 0.00 on
«0. 9.«0 99
00. 0.00 on
99. 9.90. an
99. 9.00 09
no. ovum. n9
on. a... «a
no. «no. 99
no. 9.09 99
0o. «.9n .9
no. o.99 o
oo. a.m.. 9
0o. 9.90 0
«o. 9.oo 0.
no. 0.oo 0
oo. .9090 n
00. 9290 «
oo. 9.”. H
:z «twp
09.0999 0:.9

100

 

.anauu 0:0 «nan .uoauan!
00. 9.99 00. «.«9 no. o.00 00
00. 0.n9 99. 0.n9 «o. n.99 «0
00. n.n9 00. 9.n9 o0. o..« 0o
00. 0.09 .00. 0.09 «o. 0.0« 00
00. «.09 00. «.09 oo. 0.00 00
n0. 9.09 «0. 9.00 00. 9.99 no
00. 0.99 09. 0.09 00. 0.09 «o
no. 9.o9 09. 0.00 00. 9.90 «v
09. «.00 09. 0.«0 co. 9.90 90
00. 9.00 09. 0.00 n0. 0.00 on
00. 0.90 00. «.00 90. 0.00 on
00. 0.90 «0. «o00 «0. 9.00 «n
«0. «.00 n0. 9.90 «0. 0... 0n
n0. 0.90 00. 0.90 00. 9.00 0n
00. «.00 «0. 0.00 00. 0.00 vn
«0. 0.00 00. o.00 n0. o.0- nn
n0. 9.00 90. 0.o0 no. «.00 «n
00. n.00 «0. 9.o0 9'” 0.00 an
00. 9.00 «0. 0.90 00. «.00 on
«0. n.00 n0. «.00 «0. 9.09 o«
«0. n.00 00. 0.00 «0. 9.00 0«
90. 0.00 n0. 0.90 00. 9.00 ««
«0. 0.00 00. 0.90 90. 9.90 0«
«0. 0.90 90. 9.00 «0. «.09 0«
00. 9.90 «n. o.n0 90. 0.00 0«
00. «.00 09. 0.«0 00. 9.00 n«
00. 9.«0 0n. 0.«0 «0. 0.00 ««
00. 0.00 «0. 0.90 vs. 0.00 ««
oo. 0.00 «0. «.90 «o. 9.0» 9«
o0. 0.00 no. 9.9o oo. 0.09 on
on. 9.«0 00. «.00 «c. 9.00 an
o0. 0.90 00. 0.09 «0. 0.0« «a
99. o.o9 o0. o.«9 «0. 0.00 00
«9. 0.09 «o. 0.09 0o. «.00 00
on. 9.0« «o. 0.00 00. 0.00 on
«no «.«« oo. 0.00 «o. 0.00 nu
«9. 0.«« «o. 0.00 «o. 0.00 «9
0o. n.o0 o0. o.00 0o. o.00 an
o0. 0.o0 0o. «.o0 0o. 0.00 00
00. 9.o0 oo. 0.00 «o. 9.00 o
o0. 0.00 0o. «.00 0o. «.00 0
00. «.00 oo. 9.«0 no. o.00 o
oo. 0.90 oo. 0.90 0o. «.00 0
oo. 0.00 0o. «.00 0o. 0.00 0
oo. 0.00 00. 0.00 9o. 0.00 0
om. «.00 oo. 0.00 0o. n.00 n
9o. «.00 o0. 0.90 oo. «.00 «
o0. 0.00 00. «.00 0o. 0.00 9
10 030910 000910 oxmo
9090.0030 .0090.
uc.02. 00.0999 02.9

m« dam

1293 03145 8718

M‘. .
All!
Rlll
ml.
L."
Y“
Tlll
5“
II"
III
"
Ell“
I"
I'll.
H
I"
”