dynamic simulation model of a vapor compression domestic refriger
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8/10/2019 Dynamic Simulation Model of a Vapor Compression Domestic Refriger
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Purdue University
Purdue e-Pubs
International Refrigeration and Air ConditioningConference
School of Mechanical Engineering
1996
Dynamic Simulation Model of a VaporCompression Domestic Refrigerator Running
With R134aX. XuEcole des Mines de Paris
D. ClodicEcole des Mines de Paris
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Herrick/Events/orderlit.html
Xu, X. and Clodic, D., "Dynamic Simulation Model of a Vapor Compression Domestic Refrigerator Running With R134a" (1996).International Reigeration and Air Conditioning Conference. Paper 370.hp://docs.lib.purdue.edu/iracc/370
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2 D
ESCRIP
TIO N
OF TH
E M T
HE M
TIC L
MODE
L
T he dom
estic re
fr igeratin
gsystem
which i
s studied
in this p
aper is i
llu strated
in figur
e
1.
It c
onsists o
f a com
pr essor
a
conden
ser a ca
pi llary tu
be an ev
aporator
a capill
ar y tube-
suction l
in e heat e
xchange
r and an
insulated
c abinet.
2.1 Ma
themati
cal
m
o el
of the
he
at excha
ngers
In this w
ork the
same ty
pe math
ematical
model
is develo
pped for
the
thre
e excha
ngers of
the sys
te m : co
ndenser
evapo
ra tor and
t he cap
illary tub
e- suction
l ine hea
t exchan
ge r. he
refrigera
nt flow i
n the ex
changers
is comp
lex beca
use of
the refri
gerant p
ha se cha
nge. Th
e follow
ing assu
m ptions
are used
:
i)
the
flow
in the e
xchanger
s is sup
po sed to
be
unidim
ensionn
al ; ii v
iscous d
issipatio
n is neg
lected; iii xi l
conducti
on is ne
glected; iv
the
gravitan
ional te
rm is
neglect
ed . Follo
wing the
se assum
ptions
the conse
rvation
equations
are as fo
llows:
Mass co
nservatio
n
1
)
Momen
tum cons
ervation
2)
W here
P x is th
e friction
force pe
runit vo
lume :
with
c
1
0,
7
9 e
25
Energv
conserv
ation
J ph)
a puh
) dp
dp
--
=q
u
dt
dX
dt
d
X
3)
w
ith
For
the
tube an
dfins th
e energy
c onserv
ation eq
ua tion is:
4)
i
n w bich
Mb e t M
z are th
emass
of
the tub
eand fin
spe r un
itary leng
th.
T L
is
the fins
ef ficienc
y.
T
he extern
al heat e
xchange
coefficie
nt betwe
en the ex
changer
nd
the a
ir
a
e is
determin
ed throug
h empir
ic al corr
elations
by
ta k
in g in ac
count the
combin
at ion
of
natural c
onvectio
n nd ra
diation. T
he conv
ective ex
change c
oefficien
t inside
the tube
i
iscalculated withcorrelations
of
theforcedconvection according to the various thermal configura tions.
For
th
e two-ph
ase flow
ZIVI s
void frac
tion mo
del is ch
osen:
1
nd
conse
quently
a
4
90
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B IB L
IO GR
APH
Y
L
CHE
N Z.J. L
IN
W .
H . D
ynam
ic sim
ulatio
n n
dopti
m al m
atchi
ng of
a sma
ll-sca
le ref
rigera
tion s
ystem
, R ev
. int.
Froid
N
ovemb
re 19
91, V
ol. 14,
pp.
329-3
35.
2
. JAN
SSE
N
MJ
.P.
K
UIJP
ERS L
.J.M.
et a l
. The
oretic
al and
expe
riman
tal in
vestig
ation
of a
dynam
ic mo
del fo
r sma
ll
refr
igerati
ng sy
stems
, Proc
eedin
gs o P
urdu
e IIR m
eetin
g Pu
rdue 1
988/2
Com
miss
ion B
2, pp
.245-2
57.
3.
PAT
ANK
AR S
.V.
Num
erical
heat
transf
er
nd
fluid
flow
, Ma
cGraw
-Hill
, Hen
nisph
ere P
ublish
ing,
Wash
ingto
n,
198
0.
4.
TA K
AISID
Y. an
d O
G UC
HI
K
.
Sol
ubili ty
of t
he sol
u tions
o f H
FC-1
34a and
po
lyoles
ter ba
sed oi
l , Pro
ceedi
ngs o
Purd
ue 1/R
meet
ing G
hent
199
3/2 C
om m i
sion Bl
/2,
pp.14
1-148
.
5.
XU X
. M
odelis
ation
dynam
ique
d'un s
ystem
e frig
orifiq
ue dom
estiq
ue
compr
ession
r
v
apeur
, Ph.D
. the
sis
1996,
Ecole
des M
ines d
e Par
is, Fra
nce.
Jn
sula lion
cabin et
Evap on n
or
Ca
pillary
t u b e ~ m c
t i o n
line
he
aL exch
anger
c pi l l ry
tube
Condcn
tcr
Fi
gure
1 : Va
por co
mpres
sion d
omest
ic refr
igera
tor
493
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mp
M lin
t
)
Figur
e 2 :H
erm e
ti c com
press
or
/
,2.J1)
p