development of air cycle technology for transport refrigeration
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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Purdue University
Purdue e-Pubs
I&2* R&'2*&2* % A*2 C%***C'&2&$&
S$ ' M&$*$ E*&&2*
1996
Development of Air Cycle Technology forTransport Refrigeration
S. Engelking University of Hannover
H. KruseUniversity of Hannover
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* %$5& #&& %& *#& 25 P52%5& &-P5#, &2 *$& ' & P52%5& *&2* L*#22*&. P&& $$ &05#@052%5&.&%5 '2
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H&22*$+/E&/2%&2*.
E&+*, S. % K25&, H., "D&&0& ' A*2 C$& T&$ '2 T202 R&'2*&2*" (1996). International Reigerationand Air Conditioning Conference. P0&2 348.0://%$.*#.052%5&.&%5/*2$$/348
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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•
A
pr
o
p
ri
e
ta
r
y
p
r
o
je
c
t
fo
r
a
le
a
d
in
g
G
e
r
m
a
n
m
a
nu
f
a
ct
u
re
r
in
t
h
e
r
ai
lw
ay
se
c
to
r
r
e
la
te
d
t
o
ra
il
w
a
y
a
n
d
t
ra
m
ap
p
l
ic
a
ti
on
s
.
•
A
p
r
o
p
ri
e
ta
r
y
p
r
o j
e
c t
fo
r
a
l
ea
d
in
g
G
e
rm
a
n
m
a
nu
f
a
ct
u
re
r
i
n
th
e
a
re
a
o
f
h
ig
h
s
p
e
ed
e
le
c
tr
ic
a
l d
r
iv
e
s
r
e l
a
te
d
to
h
i
g
h
s
p
ee
d
-
m
o
to
r
-c
o
m
p
r
e
ss
o
r-
e
x
pa
n
d
e
r
un
i
ts
.
• An overview about ava
il
ab
l
e
c
o
m
p
re
s
si
o
n
a
n
d
ex
p
a
n
si
o
n
m
a
c
h
in
e
s,
m
a
in
l
y
f
o
r
a
pp
l
ic
a
ti
o
n
s
w
i
th
sm
a
ll
t
o
m
e
d
iu
m
ca
p
a
ci
ti
e
s,
i
n
cl
u
d
in
g
e
x
p
er
im
en
t
a
l r
e
su
l
ts
c
o
n
c
er
n
in
g
c
a
pacity
data
and a flexible simula tion program
f
or
a
ir
c
y
cl
e
s
y
st
em
s,
b
a
s
ed
o
n
r
ea
l
c
h
ar
a
c
te
ri
s
ti
c
d
a
ta
f
o
r
m
a
c
hi
n
e
s
a
nd
h
ea
t
e
x
c
ha
n
g
e
rs
[4
]
•
T
he
de
v
e
lo
p
m
e
n
t
o
f a
n
a
ir
c
y
cl
e
s
y
st
e
m
f
o
r
t r
a
n
sp
o
r
t
re
f
r i
g
er
a
ti
o
n
[
5]
3
P
R
E
S
E
N
T
S
IT
U
A
T
IO
N
IN
G
E
R
M
A
N
Y
3
.1
G
er
m
a
n
H
ig
h
Sp
e
e
d
T
r
a
in
I
C
E
B
as
e
d
o
n
th
e
e
v
a
lu
a
ti
o
n o
f
al
te
r
n
at
iv
e
a
i
r
co
n
d
it
io
n
i
ng
cy
c
le
s
t
w
o
d
i
ff
er
e
nt
co
m
p
a
n
ie
s
w
e
r
e
a
sk
e
d
b
y
t
h
e
D
e
u
t
s
c
h
e
B
u
n
d
es
b
a
h
n
A
G
t
o
b
u
il
d
a
ir
c
y
c
le
s
y
s
te
m
s
f
o
r
a
ir
c
o
n
d
it
io
n
in
g
in
t
h
e
G
e
r
m
a
n
hi
g
h
s
p
ee
d
tr
a
in
IC
E
.
B
o
t
h
systems have b een runn ing successfully since spring
1
99
5
a
n
d
t
h
er
e
fo
r
e
i
t i
s
p
la
n
n
e
d
to
u
se
t
h
e
se
s
y
s
te
m
s
i
n
th
e
n
ew
g
en
e
ra
t
io
n
o
f
th
e
t
ra
i
n
,
th
e
I
C
E
2
.2
s t
a
r t
in
g
on
th
e
n
ew
h
ig
h
sp
e
e
d
t
ra
c
k
b
e
tw
ee
n
H
an
n
o
v
e
r and Berlin in 1998.
O
n
e
m
a
n
u
fa
c
tu
r
e
r
h
ad
c
ho
s
e
n
a
n
o
p
e
n
c
y
cl
e
u
n
it
w
hi
c
h
w
as
d
e
ri
v
ed
fr
o
m
a
n
ai
r
c
o
n
di
ti
o
n
in
g
s
y
st
e
m
f
o
r
a
ir
c
ra
f
ts
.
T
h
e
ot
h
e
r
sy
s
t
em
i
s
a
n
e
w
d
e
v
e
lo
p
m
e
n
t u
s
in
g
a
c
lo
s
ed
a
ir
c
y
cl
e.
F
ig
.
1
s
h
o
w
s
t
h
e
cl
o
se
d
ai
r
c
yc
l
e
c
om
p
ac
t
u
n
it
t
o
b
e
in
s
ta
l
le
d
i
n
t
h
e
ro
o
f
o
f
t
h
e
tr
a
in
.
F
i
g
u
re
1
:
A
ir
c
y
cl
e
c
o
m
p
a
ct
u
n
i
t
a
s
in
s
ta
ll
e
d
i
n
th
e
G
e
rm
an
h
ig
h
s
p
ee
d
t
ra
in
IC
E
.
In
c
om
p
ar
i
so
n
t
o
v
a
p
o
r
c
o
m
p
re
s
si
o
n
c
yc
l
es
th
i
s
m
a
c
hi
n
e
h
a
s
g
o
t
th
e
s
a
m
e
d
im
e
n
s
io
n
s,
ne
a
rl
y
t
h
e
s
am
e
p
r
ic
e
a
n
d
m
o
r
e o
r
le
s
s
th
e
s
a
m
e
w
ei
g
h
t.
T
h
e
r
e
la
ti
v
e
e
n
er
g
y
c
o
n
su
m
pt
io
n
i
n
c
o
m
p
a
r
is
o
n
to
th
e
cu
r
re
n
tl
y
u
s
e
d
R
1
2
s
p
li
t
s
y
s
te
m
an
d
to
a modern R134a s ystem is shown
in
Table 1 ( R134a is s et to have an energy consump
ti
o
n
o
f
1
.0
)
[
6
]
T
a
bl
e
1
:
A
c
om
p
ar
is
o
n
o
ft
h
e
re
la
t
iv
e
e
n
e
rg
y
c
o
n
su
m
p
t
io
n
an
d
t
he
T
E
W
J-
n
u
m
b
e
r
.
T
r
ai
n
S
y
s
te
m
E
ne
r
gy
(
fa
c
to
r
)
T
E
W
I k
g
C
0
2
f
e
a
r
1
IC
E
1
R
1
2
s
p
li
t
sy
s
te
m
1
2
11
1
7
0
0
IC
E
2
R
l
3
4
a s
y
st
e
m
1
.0
-
3
1
2
0
0
IC
E
2
.2
a
ir
c
y
cl
e
u
n
it
1
2
2
6
40
0
35
0
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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In
tern
al
hea
t ex
chan
ger
A
m b
ien t
C
old
stor
age
roo
m
F
ig u
re 2: B
oot
strap
ope
n cy
cle c
onf
ig ur
ati o
n w i
th i
n te r
na l he
at
ex c
ha ng
er .
F ig
ure
3: Co
mpa
ct
uni
t for
use
in an
a
ir cy
cle
re fri
gera
ti on
sys
te m
.
ano t
her
m od
ule
by
a no
de.
The
co
nne
ction
s m
ust
be
de fin
ed
by th
e u
se r,
dep
end
ing
on
th
e
c
onf
ig ur
at io
n o f
th
e
c
ycle
. O
ut
o
f
a ll
conn
ect
io ns
t
he p
rogr
am
its
elf s
et s
up
a
set
of e
qua
tion
s wh
ic h
are
solve
d u
sing
a sl
ig ht
ly m
od if
ied
iter
a tio
n me
tho
d w
hi ch
is b
ase
d on
the
N ew
ton
-R a
phs
on -s
che
m e.
To
p erf
o rm
a cc
ura t
e m o
dul
es fo
r th
e co
m pr
es so
r
and th
e
expa
nde
r, ch
ara
c te r
ist ic
di
agra
ms
fo
r pe
rf o r
m an
ce
da
ta
a
t d
if fe
rent
loa
d co
ndit
io ns
f
rom
th
e m
anuf
ac tu
rer
we
re u
sed t
o i
m pl
em e
nt p
o lyn
om i
al fu
nct
io ns
for
th
e is en
tr op
ic e
fficie
ncy
, the
m a
ss f
low
ra te
, th
e ro t
a tio
nal
sp ee
d
an
d th
e
po
wer
con
sum
ptio
n .
D
ata
fo
r hea
t
ex ch
ang
ers
were
t
aken
fr o m
m
easu
re m
ent
re su
lt s
an d
pol
yno
m ia l
f
unct
io ns
we
re es
ta bl
ishe
d
to ca
lc u la
te
the p
re ss
ur e
d ro
p an
d t
he hea
t
tr an
sfer
cap
ac ity
. P
re ss
ure
dro p
s in
tub
es
ar
e ca
lc ul
a te d
dep
end
in g
on the
R ey
nold
s nu
m be
r
and b
o un
dary
con
diti
ons
wer
e se
t to
m ee
t
the re
quir
em e
nts f
or
tr
ansp
ort
r
efr ig
era
tion 30
C am b
ie n t
tem
per
a tu r
e
and 5
C
in the
co ld s to rage room ). Sim ulati on r esults ha ve
sh
own
th
at the
co
nce
pt, u
sin
g the
c
om
pact
u
nit ,
is o
f g re
a t p
ro m
is e.
Fig
. 4
(left
han
d si
de)
sh ow
s si
m ul
a ted
CO
P
re
sult
s fo
r b
ot h
5
°C t
emp
era
ture
an
d
-3
0°C
i
n
the co
ld s
to ra
ge r
o om
as
a fu
nctio
n o
f the
ro t
a t io
n al
sp ee
d.
The
ca
lcu l
a te d
eff
icien
cies
for t
he
exp
ansi
on
m ac
h in e
are
b as
ed
on c
hara
cte
r isti
c dat
a a
vail
able
for
us e
wit
h
6
00°C
exh
aust
gas
. F
rom
exp
er ie
nce
wit
h th
e te
s t r i
g the
ef
fic ie
nc ie
s fo
r us
e with
l
owe
r tem
p er
a tu r
es
are
ab o u
t
1
0 to
15
low
er .
The
effi
cien
cy f
or
th e
c
om p
re ss
or i
s ac
cura
te b
ecau
se
the
av ai
la ble
ch
ara c
te ris
ti c
dat
a m e
ets
si
m ila
r co
nd it
io ns
as
th er
e a r
e at t
he
te
st rig
. Fig
. 4
(r ig
h t han
d
side
) sh
ow s
sim
ula
ted r
esu l
ts fo
r th
e C
OP
-v a
lue
w
ith
resp
ect
to
di ffe
re nt
eff
icien
cies
for
th
e exp
and
er w
hi le
usi
ng r
ea l
char
ac te
ri sti
c da
ta f
or
the c
om p
re s
so r and
the
he
at
ex c
han
ger.
As
can
be
seen
, eff
icien
cies
i
n
th
e ord e
r of
0.8
are
req
uir e
d in
or d
er to
ge
t a r
eson
abl
e
CO
P
352
-
8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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8/18/2019 Development of Air Cycle Technology for Transport Refrigeration
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e
xp
an
d
er
3
i
n le
t)
4
o
u t
le t
)
F i
g u
re
5
:
S
ke
tc
h
of
a p
re
ss
ur
e w
a
ve
m
ac
h i
ne
.
2
ou
tl
e t)
en
er
gy
tr
an
sm
is
si
o n
b
et w
e
en
bo
th
flu
id
f
low
s
oc
cu
rs
by
p
re
ss
ure
a
n
d e
x
pa
nsi
on
w
av
es
w
h
ich
r
es
u lt
s in
ve
ry
fe
w
l
os
ses
a
nd
h
ig
h e
ffi
cie
nc
ie
s f
or
co
m
p r
es
s io
n
an
d
ex
pa
ns
io n
.
D
u
e to
th
e
fa
ct
t
ha
t t
he
re
is
a
d
ir
ec
t c
on
ta
c t
b
etw
e
en
bo
th
flu
id
fl
ow
s
th
er
e
is
a
di
ff i
cu
lty
in
cal
cu
la
ti n
g
eff
ici
en
cie
s.
T
h e
a
ir
flo
w
en
te
ri n
g
vi
a i
n l
et
lin
e
3 m
us
t
n
ot
ne
ce
ss
ar i
ly
e
x it
c
om
pl
et
el y
a
t o
u
tle
t l
in
e
4.
De
pe
nd
in
g
o
n th
e
b
o
u n
d a
ry
w
o r
k i
ng
c
o n
d it
io
n s
w
hi
ch
ar
e
pr
es s
ur
e
ra
tio
s
as
w
ell
as
r
o t
a ti
o n
a l
sp
ee
d
th
er
e ca
n
b
e
a
le
ak a
ge
m
as
s
flo
w ra
te
fr
o m
i
n le
t
3 t
o o
u
tle
t
2
or
fr
om
i
n l
e t
1 to
ou
tl
e t
4
re
f. F
ig
.
6
).
F
o r
th
is
re
as
on
a
ll
di f
fe
re n
t
m a
ss
c
as
e 1
c
as
e
2
c
as
e
3
3
2
3
3
F i
g u
re
6: P
W
M
:
D
ef
in
it i
on
s f
or
ef
fic
ien
ci
es
fl
ow
r
at
es
hav
e
to
be
c
on
si
de
re d
f
o r
ev
a l
u a
ti n
g
eff
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3
54
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