heat and mass transfer modeling for microbial food safety applications in the meat industry: a...
TRANSCRIPT
REVIEW ARTICLE
Heat and Mass Transfer Modeling for Microbial Food SafetyApplications in the Meat Industry: A Review
J. F. Cepeda • C. L. Weller • M. Negahban •
J. Subbiah • H. Thippareddi
Received: 21 August 2012 / Accepted: 1 February 2013 / Published online: 26 February 2013
� Springer Science+Business Media New York 2013
Abstract Temperature is an important factor affecting
microbial growth in meat products, and hence the most
controlled and monitored parameter for food safety in the
meat industry. In the last few decades, modeling of heat
and mass transfer in products has gained special attention
in the meat industry as it can be integrated with predictive
microbial models, and eventually with risk assessment
models. Thus, heat and mass transfer models can be used as
practical tools to assess microbial safety of meat products
quantitatively, especially in the event of unexpected pro-
cessing issues such as thermal processing deviations. This
manuscript reviews research efforts related to heat and
mass transfer modeling in meat products that have been
published in recent years. It synthesizes the main ideas
behind modeling of thermal processing in the meat industry
encompassing common considerations and techniques.
This review specially emphasizes in research efforts that
have been oriented to industrial applications, and can be
potentially integrated with food safety tools. Literature
indicates that despite great advances in the field, there are
several challenges that persist and the scientific community
must address them to develop models applicable to the
meat industry.
Keywords Meat processing � Meat cooling � Finite
elements � Numerical analysis � Food safety � Computer
modeling � Predictive microbiology � Meat safety
Introduction
Ready-to-eat meat products are susceptible to rapid
microbial growth unless stored and processed appropri-
ately. Meat processors must control the growth of spoilage
bacteria such as Brochothrix thermosphacta, Pseudomonas
spp., and lactic acid bacteria. Moreover, food safety regu-
latory agencies such as the United States Department of
Agriculture Food Safety and Inspection Service (USDA–
FSIS) issue different policies and regulations that enforce
meat processors to restrict the presence or limit the growth
of foodborne pathogens such as Clostridium perfringens,
Listeria monocytogenes, Salmonella spp., and Escherichia
coli in their products [44].
Product temperature profile during processing and stor-
age is an important factor affecting microbial growth in meat
products. Therefore, it is one of the most controlled and
monitored parameters in the meat industry. Maintaining
product temperature profiles within safe limits that reduce
the risk of potential microbial outgrowth represents a chal-
lenge for some meat processors, especially when processing
products of large mass and volume (e.g., products over 4 kg)
[1]. In the event of a presumptive microbial outgrowth, the
meat industry and regulatory agencies rely on sampling and
microbial testing to determine the safety of the products.
However, sampling and testing may be impractical
because it is time-consuming, generates extra costs, and
J. F. Cepeda � C. L. Weller (&) � J. Subbiah
Department of Biological Systems Engineering, University
of Nebraska-Lincoln, 210, L.W. Chase Hall, East Campus,
Lincoln, NE 68583-0726, USA
e-mail: [email protected]
J. F. Cepeda � C. L. Weller � J. Subbiah � H. Thippareddi
Department of Food Science and Technology, University
of Nebraska-Lincoln, Lincoln, NE 68583-0919, USA
M. Negahban
Department of Mechanical and Materials Engineering,
University of Nebraska-Lincoln, Lincoln, NE 68588-0526, USA
123
Food Eng Rev (2013) 5:57–76
DOI 10.1007/s12393-013-9063-6
can be unreliable as microorganisms are not uniformly
distributed in the products. In the last two decades, com-
puter modeling, including heat transfer, predictive micro-
biology, and risk assessment modeling, has gained special
attention in the meat industry as it is a practical resource to
estimate meat safety quantitatively. In fact, regulatory
agencies recommend the use of computer modeling as a
tool to prevent and evaluate the severity of potential
microbial contaminations [77, 78].
The following review focuses on heat transfer modeling
of meat products; emphasizing in practical models with
potential use in food safety industrial applications. It pro-
vides perspective on the evolution of this field, its novel
advances, and its current shortcomings. In addition, it
offers a synopsis of the state-of-the-art in the heat transfer
modeling area, which can be used to get a better under-
standing of future research opportunities.
Thermal Processing in the Meat Industry
Thermal processing of meat products refers to a broad
range of products, processing techniques, and equipment
utilized during cooking and/or cooling. Despite this vast
diversity, most of the thermal processing systems in the
meat industry operate under similar physical principles of
heat and mass transfer [38].
The manufacturing of heat-treated meat products
includes three basic steps: meat-matrix preparation, heat
treatment, and cooling. Although the meat-matrix prepa-
ration may differ between products, the heat treatment and
cooling steps follow similar principles for most products.
During heat treatment (or cooking), products are placed
into industrial meat ovens or smokehouses in which they are
exposed to a hot fluid, usually humid hot air. This step serves
several purposes such as heat stabilization of the meat
matrix, and fixing of meat color. Products are normally
cooked to at least -55 �C (131 F) to ensure proper heat
stabilization of the meat matrix by protein denaturation [5,
60, 90]. This cooking step is also critical for destroying
foodborne pathogens and assuring microbial safety. The
heat treatment must achieve the lethality performance
standard established by the USDA–FSIS (i.e., 7-log reduc-
tion in Salmonella spp. in ready-to-eat poultry, and a 6.5-log
reduction in Salmonella spp. in ready-to-eat beef products).
According to the USDA–FSIS recommended compliance
guidelines, lethality can be accomplished by different tem-
perature and holding time combinations. For instance,
lethality can be accomplished by reaching a minimum
temperature of 60 �C (140 F) and maintaining it across the
whole product for at least 12 min [78].
After the heat treatment, some meat products are exposed
to cold-water showers right before entering the cooling
chamber. This procedure helps drop the surface temperature
of the product, minimizing the weight loss caused by evap-
oration from the surface during the cooling step [1]. Cold-
water showers also help generate a gradient of temperature
within the product that facilitates the heat conduction process
from the core to the surface during the cooling step [12].
Consequently, water-showered products have non-uniform
initial temperatures prior entering the cooler.
Cooling is a critical step for preventing potential growth
of spore-forming bacteria that can survive the heat treat-
ment. Heat-shocked spores of foodborne pathogens may
germinate and grow if the cooling is not rapid and uniform.
In general, processors need to employ fast cooling rates to
minimize the risk of potential microbial outgrowth while
avoiding surface freezing. Ice formation causes micro-
structural changes in meat products that may lead to unde-
sired changes in product properties (e.g., color, viscosity,
pH), cell dehydration, drip loss, and tissue shrinkage [45].
The cooling step must meet the stabilization performance
standard established by USDA–FSIS (i.e., no multiplication
of toxigenic microorganisms such as Clostridium botulinum,
and no more than a 1 log10 multiplication of C. perfringens
within the product). According to the recommended com-
pliance guidelines, stabilization can be accomplished by
following save cooling methods. For instance, the maximum
internal temperature of a non-cured product should drop
from 54.4 to 26.6 �C (130 to 80 F) in less than 1.5 h; and
must reach 4.4 �C (40 F) within the next 5 h.
Cooling can be performed using different methods such
as water immersion, slow air flow, blast air, and vacuum
cooling. Vacuum cooling is a faster method for cooling
compared to water immersion, blast air, and slow air
cooling. Also, vacuum cooling results in a more uniform
temperature distribution of the product during the cooling
process, which is beneficial from the microbial safety
standpoint [72]. Conversely, vacuum cooling may result in
greater weight loss as the heat transfer is mainly governed
by water evaporation from the product surface. Hence, it is
not suitable for various meat products. Sun and Wang [72]
suggested that the excessive weight loss caused by vacuum
cooling could be overcome by using greater rates of water
injection during the meat preparation step. Despite the
potential advantages of vacuum cooling, traditional cooling
methods such as slow air and blast air cooling are more
common in the meat industry.
Modeling Heat and Mass Transfer in Meat Products
Heat and mass transfer in meat products is a complex
phenomenon affected by multiple physics involving energy
transport, mass transport, fluid flow dynamics, and
mechanical deformation (e.g., shrinkage and swelling).
58 Food Eng Rev (2013) 5:57–76
123
In traditional meat processing, products are exposed to a
colder or warmer airflow, which triggers the driving force
for heat transfer. As a result, thermal energy is conducted
across the product domain due to temperature differences
between the core and surface of the product. Heat and mass
are also transferred due to convection between the product
surface and the air. In addition, thermal radiation from the
product surface and from the cooler/over walls can occur.
Differences in temperature and moisture levels between the
air and the product can cause moisture evaporation from
the product surface. As the product surface dries, internal
moisture transport toward the product surface can occur.
Furthermore, the meat matrix undergoes structural and
physical changes during thermal processing that may also
affect heat transfer rates.
On the other hand, meat-processing environments are
diverse and processing conditions may vary over time.
Hence, heat and mass transfer rates are influenced by
multiple parameters including cooler/oven temperature,
product load, airflow velocity, type of heating/cooling
medium, product arrangement inside cooler/smokehouse,
and type of products (e.g., shape, dimensions, and thermal
properties). Consequently, modeling of heat and mass
transfer of meat products under industrial environments is a
challenging task. During the last two decades, researchers
have proposed different models to describe and simulate
the physics behind heat and mass transfer in meat products
(Table 1). Some of the key modeling principles and
methodologies are described in the following sections.
Governing Equations
Energy and mass transport are important governing equa-
tions for modeling heat transfer at the product level.
Energy Transport
The energy transport equation is commonly described by
transient heat conduction without internal heat generation.
It can be represented in Cartesian (x, y, z) coordinates as:
oq
oxþ oq
oyþ oq
oz¼ qCp
oT
ot
S.T. Boundary conditions and initial conditions
where variables k, q, and Cp represent thermal conductivity,
density, and specific heat, respectively; at a particular time t,
temperature T, and location (x, y, z). The conduction heat
flux q is commonly modeled by Fourier’s law,
q ¼ �k rTð Þ
which states that q is equal to the material’s thermal conduc-
tivity k times the negative local temperature gradient (-rT).
Some researchers have suggested that the nature of heat
conduction in porous materials with non-uniform inner
structure like RTE meats may be better described by non-
Fourier models. It has been shown that heat wave propa-
gation may take a finite time; contrary to the instantaneous
propagation established by Fourier [3, 50, 65]. Moreover, it
is believed that this phenomenon may be further noticeable
at low temperatures such as the ones encountered in meat
cooling, when the energy levels of molecules are highly
reduced [49]. Thus, the traditional Fourier heat conduction
model would include an extra term containing a finite
thermal characteristic time or relaxation time constant (s),
qþ soq
ot¼ �k rTð Þ
resulting in non-Fourier models such as the hyperbolic and
dual phase lag (DPL) models [4, 33, 34].
However, the heat wave propagation velocity in meat
products is high; thus, the finite thermal characteristic time
is minimal and can be neglected [33, 34]. Hence, the
Fourier model provides a practical description of heat
conduction in meat products. Non-Fourier models are yet
to be shown to be of practical value.
Mass Transport
The mass transport governing equation is usually based on
Fick’s law of mass diffusion. It can be represented in
Cartesian (x,y,z) coordinates as:
omw
ot¼ o
oxD
omw
ox
� �þ o
oyD
omw
oy
� �þ o
ozD
omw
oz
� �
where D represents moisture diffusivity in the meat matrix
and mw represents the moisture mass fraction in the meat
product.
Modeling internal water transport is a challenge as it is
not well understood, especially in meat matrices with
complex internal porous structures. Therefore, it has not
been included in multiple models for practical purposes [1,
35, 83]. Such models are built upon the assumption that
internal moisture transport compensates for the moisture
evaporation from the meat surface. As a result, water
activity and moisture concentration on the meat surface are
assumed to remain constant. The validity of those
assumptions is discussed below in the boundary conditions
and thermo-physical properties sections.
Initial Conditions
Considering a uniform initial temperature is a common
assumption when modeling heat transfer in meat prod-
ucts because non-uniform initial temperatures are diffi-
cult to provide. For instance, the final temperature of the
Food Eng Rev (2013) 5:57–76 59
123
Ta
ble
1M
od
els
for
hea
tan
dm
ass
tran
sfer
of
mea
tp
rod
uct
sd
evel
op
edin
rece
nt
yea
rs
Ref
eren
ces
Ap
pli
cati
on
Pro
du
ct(g
eom
etry
)T
echniq
ue
(so
ftw
are)
Go
ver
nin
geq
uat
ion
Bo
un
dar
yco
nd
itio
ns
Tra
nsf
erco
effi
cien
tsT
her
mal
pro
per
ties
Ad
dit
ion
ald
etai
ls
Am
ezq
uit
aet
al.
[1,
2]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Co
ok
edh
am
(1/4
elli
pse
)
2D
Fin
ite
elem
ents
(Mat
lab
)
2D
hea
tco
nd
uct
ion
Co
mbin
edh
eat
con
vec
tio
n
and
ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
elli
pso
ids
Lew
isre
lati
on
ship
Em
pir
ical
corr
elat
ions
[13
]V
alid
ated
inin
du
stri
alen
vir
on
men
ts
Use
dp
oly
nom
ial
reg
ress
ion
for
no
n-u
nif
orm
init
ial
tem
per
atu
res
Use
dto
eval
uat
em
ult
iple
indust
rial
cooli
ng
scen
ario
s
Inte
gra
ted
wit
hC
.per
frin
gen
sg
row
thm
od
el
Cep
eda
etal
.[1
2]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Rea
dy
-to
-eat
mea
ts
(3D
irre
gu
lar
shap
eso
bta
ined
by
CT
scan
nin
g)
3D
fin
ite
elem
ents
(Jav
a)
3D
hea
tco
nd
uct
ion
Co
mbin
edh
eat
con
vec
tio
n
and
ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
com
ple
xsh
apes
Lew
isre
lati
on
ship
Em
pir
ical
corr
elat
ions
[13
]V
alid
ated
inin
du
stri
alen
vir
on
men
ts
Use
dp
reli
min
ary
hea
ttr
ansf
eran
alysi
sto
esti
mat
en
on
-un
ifo
rmin
itia
lte
mp
erat
ure
s
Av
aila
ble
tou
seth
rou
gh
aw
ebsi
te(h
ttp
://
foo
dsa
fety
.un
l.ed
u)
Inte
gra
ted
wit
hvar
ious
dy
nam
icm
icro
bia
lg
row
thm
od
els
Ch
un
tran
ulu
cket
al.
[14
–1
6]
Air
-co
oli
ng
tim
eF
oo
dm
ater
ial
(sp
her
e,in
fin
ite
slab
,an
din
fin
ite
cyli
nd
er)
Fin
ite
dif
fere
nce
s1
Dh
eat
con
duct
ion
Co
mbin
edh
eat
con
vec
tio
nan
dth
erm
alra
dia
tio
n
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
Rep
ort
edv
alu
esS
how
edth
eef
fect
of
surf
ace
ph
ysi
cal
bar
rier
sto
mo
istu
retr
ansp
ort
(e.g
.,p
eele
dan
du
np
eele
dca
rro
ts)
Dav
eyan
dP
ham
[20,
21
]
Pro
du
cth
eat
load
and
wei
ght
loss
du
rin
gai
rco
oli
ng
Bee
fca
rcas
s
(co
mb
inat
ion
of
cyli
nd
ers
and
slab
s)
Bee
fca
rcas
s
(2D
cross
-se
ctio
ns)
Fin
ite
dif
fere
nce
s
2D
fin
ite
elem
ents
2D
hea
tco
nd
uct
ion
Co
mbin
edh
eat
con
vec
tio
nan
dth
erm
alra
dia
tio
n
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
slab
and
ver
tica
lsu
rfac
e
Reg
ress
ion
equ
atio
ns
Rep
ort
edv
alu
es
No
tem
per
atu
revar
iati
ons
Val
idat
ion
inp
seu
do
-in
du
stri
alen
vir
on
men
ts(w
ind
tun
nel
pla
ced
insi
de
anin
du
stri
alco
ole
r)
Acc
ou
nte
dfo
rre
sist
ance
toh
eat
tran
sfer
gen
erat
edfo
rv
isib
lefa
tse
ctio
ns
of
the
bee
fca
rcas
s
Go
ni
and
Sal
vad
ori
[29,
30]
Roas
tin
gte
mp
erat
ure
pro
file
and
wei
ght
loss
Hal
fse
mit
end
ino
sus
bee
fm
usc
le(i
rreg
ula
rsh
ape
from
imag
es)
3D
fin
ite
elem
ents
(Co
mso
l)
3D
hea
tco
nd
uct
ion
Hea
tco
nv
ecti
on
Ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
aci
rcle
Em
pir
ical
corr
elat
ions
[13
]
An
iso
tro
py
effe
ctfo
rk
Use
dfo
ro
pti
miz
atio
no
fb
eef
roas
tin
gto
min
imiz
eco
ok
ing
tim
ean
dw
eig
ht
loss
Incl
ud
edth
eef
fect
of
dri
ppin
glo
ss
60 Food Eng Rev (2013) 5:57–76
123
Ta
ble
1co
nti
nu
ed
Ref
eren
ces
Ap
pli
cati
on
Pro
du
ct(g
eom
etry
)T
echniq
ue
(so
ftw
are)
Go
ver
nin
geq
uat
ion
Bo
un
dar
yco
nd
itio
ns
Tra
nsf
erco
effi
cien
tsT
her
mal
pro
per
ties
Ad
dit
ion
ald
etai
ls
Hu
and
Su
n[3
5]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Co
ok
edm
ince
dp
ork
(1/8
of
acy
lin
der
)
Ex
per
imen
tal
win
dtu
nn
el(b
ox
)
CF
D
(Fo
rtra
n)
3D
hea
tco
nd
uct
ion
Hea
tco
nv
ecti
on
Ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Av
erag
eca
lcu
late
dfr
om
ap
reli
min
ary
CF
Dst
ead
y-
stat
efl
ow
fiel
dan
alysi
s
Lew
isre
lati
on
ship
Rep
ort
edv
alu
es3
-ste
psi
mu
lati
on
pro
toco
l:
1.
Ste
ady
CF
Dfl
ow
fiel
dan
alysi
s
2.
Est
imat
ion
of
h
3.
Sim
ult
aneo
us
hea
tan
dm
ass
tran
sfer
Val
idat
edin
exper
imen
tal
air-
bla
stch
ille
r
Ku
itch
eet
al.
[42]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Bee
fca
rcas
sh
ind
qu
arte
r
(in
fin
ite
cyli
nd
er)
An
aly
tica
l1
Dh
eat
con
duct
ion
Co
mbin
edh
eat
con
vec
tio
n,
ther
mal
radia
tion,
and
evap
ora
tio
n
Rep
ort
edv
alues
Lew
isre
lati
on
ship
Ex
per
imen
tal
val
ues
Use
dre
gre
ssio
neq
uat
ion
toac
cou
nt
for
no
n-u
nif
orm
init
ial
tem
per
atu
res
Acc
ou
nte
dfo
rti
me
var
iab
lem
eat-
pro
cess
ing
condit
ions
incl
ud
ing
rela
tiv
eh
um
idit
yan
dco
oli
ng
roo
mte
mp
erat
ure
Mal
lik
arju
nan
and
Mit
tal
[46]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Bee
fca
rcas
s(fi
ve
2D
cro
ss-
sect
ion
s)
2D
fin
ite
elem
ents
(Fo
rtra
n)
2D
hea
tco
nd
uct
ion
wit
hin
tern
alh
eat
gen
erat
ion
2D
mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Em
pir
ical
corr
elat
ions
for
ver
tica
lp
late
Lew
isre
lati
on
ship
Em
pir
ical
corr
elat
ions
[13
]V
alid
ated
inp
ilo
tp
lant
Use
dir
reg
ula
rg
eom
etry
gen
erat
edb
yg
eog
rap
hic
alin
form
atio
nsy
stem
Mar
cott
eet
al.
[47,
48]
Coo
kin
g–co
oli
ng
pro
file
san
dle
thal
ity
Sau
sages
(fin
ite
cyli
nd
er)
N.A
.
(Vis
ual
Bas
ic)
2D
hea
tco
nd
uct
ion
Hea
tco
nvec
tion
Rep
ort
edval
ues
Rep
ort
edval
ues
Inte
gra
ted
wit
hpro
cess
leth
alit
yca
lcu
lati
on
sfo
rS
.se
nft
enber
g,
E.
coli
,L
.m
on
ocy
tog
enes
,E
.fa
ecali
s
Incl
ud
eden
erg
yco
nsu
mp
tio
nes
tim
atio
nfo
rp
roce
ssin
gopti
miz
atio
n
Le
Pag
eet
al.
[53]
Dry
ing
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Un
wra
pp
edst
ack
edfo
od
pro
duct
s
(cy
lin
der
sar
ran
ged
ina
row
)
CF
D
(Flu
ent)
2D
hea
tco
nd
uct
ion
wit
hin
tern
alh
eat
gen
erat
ion
2D
mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Ev
apora
tiv
eh
eat
loss
Ex
per
imen
tal
corr
elat
ions
Rep
ort
edv
alu
esC
on
sid
ered
mult
iple
pro
du
cts
pro
cess
edsi
mu
ltan
eou
sly
Ph
amet
al.
[57]
Tru
jill
oan
dP
ham
[74]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Bee
fca
rcas
s
(3D ap
pro
xim
atio
n,
and
2D
cro
ss-
sect
ion
s)
3D
CF
D
(Flu
ent)
2D
fin
ite
elem
ents
3D
/2D
hea
tco
nd
uct
ion
1D
mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Lo
cal
val
ues
calc
ula
ted
by
regre
ssio
neq
uat
ion
so
bta
ined
from
CF
Dsi
mu
lati
on
s
Reg
ress
ion
equ
atio
ns
Rep
ort
edv
alu
es
Val
idat
edin
ind
ust
rial
env
iro
nm
ents
Food Eng Rev (2013) 5:57–76 61
123
Ta
ble
1co
nti
nu
ed
Ref
eren
ces
Ap
pli
cati
on
Pro
du
ct(g
eom
etry
)T
echniq
ue
(so
ftw
are)
Go
ver
nin
geq
uat
ion
Bo
un
dar
yco
nd
itio
ns
Tra
nsf
erco
effi
cien
tsT
her
mal
pro
per
ties
Ad
dit
ion
ald
etai
ls
Pra
dhan
etal
.[5
8]
Con
vec
tio
nco
ok
ing
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Ch
ick
enb
reas
t
(1/2
elli
pse
)
2D
fin
ite
elem
ents
(Mat
lab
)2
Dh
eat
con
duct
ion
2D
mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Rep
ort
edval
ues
Rep
ort
edval
ues
Inte
gra
ted
wit
hfi
rst-
ord
erle
thal
ity
mod
els
for
L.
inn
ocu
a
Rin
ald
iet
al.
[61]
Coo
kin
gte
mp
erat
ure
pro
file
and
wei
ght
loss
Mo
rtad
ella
Bolo
gn
aN
.A.
Hea
tco
nd
uct
ion
Mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Ex
per
imen
tal
Ex
per
imen
tal
Val
idat
edin
anin
du
stri
alp
lant
San
tos
etal
.[6
3,
64]
Wat
er-b
ath
hea
tin
gte
mp
erat
ure
pro
file
Sau
sage
(irr
egu
lar
2D
cross
-sec
tions)
2D
fin
ite
elem
ents
(Mat
lab
)
2D
hea
tco
nd
uct
ion
Hea
tco
nv
ecti
on
Ex
per
imen
tal
val
ues
Rep
ort
edval
ues
Inte
gra
ted
wit
ha
firs
t-ord
erle
thal
ity
mod
elfo
rE
.co
li
Ass
um
edn
on
-tim
e-v
ary
ing
ther
mal
pro
per
ties
and
pro
cess
ing
con
dit
ion
s
Sin
gh
etal
.[6
6]
Ov
en-r
oas
tin
gte
mp
erat
ure
pro
file
Mea
t
(1/4
of
are
ctan
gu
lar
slab
)
Fin
ite
dif
fere
nce
s2
Dh
eat
con
duct
ion
Hea
tco
nv
ecti
on
Ev
apora
tiv
eh
eat
loss
Arb
itra
ryv
alues
Rep
ort
edv
alu
esN
ov
alid
ated
Con
clud
edth
aten
erg
yre
qu
ired
tom
elt
and
soli
dif
yfa
tsco
uld
be
neg
lect
ed
Sp
ragu
ean
dC
olv
in[6
8]
Ng
adi
and
Hw
ang
[51]
Fry
ing
tem
per
atu
rep
rofi
lean
dq
ual
ity
Bee
fp
atty
(cy
lin
der
)
2D
fin
ite
elem
ents
(Fo
rtra
n)
2D
hea
tco
nd
uct
ion
2D
mas
sd
iffu
sio
n
Vap
or
gen
erat
ion
Hea
tco
nv
ecti
on
Ev
apora
tiv
eh
eat
loss
Mas
sco
nv
ecti
on
Rep
ort
edv
alues
Ch
oi
and
Ok
os
[13]
Inte
gra
ted
wit
ha
model
top
red
ict
gen
erat
ion
of
het
ero
cycl
icam
ine
Su
nan
dH
u[7
0,
71]
Vac
uu
m-c
oo
lin
gte
mp
erat
ure
pro
file
and
wei
ght
loss
Co
ok
edh
am
(1/8
of
acy
lin
der
)
CF
D
(Fo
rtra
n)
3D
hea
tco
nd
uct
ion
Vap
or
and
mois
ture
dif
fusi
on
(po
rou
sm
ediu
m)
Hea
tco
nv
ecti
on
Ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Arb
itra
ryv
alues
Em
pir
ical
val
ues
Rep
ort
edv
alu
esV
alid
ated
inla
bo
rato
ryv
acu
um
coo
ler
Incl
ud
edth
eef
fect
of
po
rous
dia
met
eran
dori
enta
tion
(anis
otr
opy)
toes
tim
ate
mas
str
ansf
erco
effi
cien
t
Incl
ud
edef
fect
of
shri
nk
age
Tru
jill
oan
dP
ham
[74,
75
]
Air
-co
oli
ng
tem
per
atu
rep
rofi
lean
dw
eig
ht
loss
Bee
fca
rcas
s
(3D
reco
nst
ruct
edfr
om
cross
-se
ctio
ns)
CF
D
(Flu
ent)
Fo
ra
ir:
con
tin
uit
y,
mom
entu
m,
turb
ule
nt
kin
etic
rate
,tu
rbu
lent
dis
sip
atio
nra
te,
hea
tco
nd
uct
ion
and
mois
ture
dif
fusi
on
Fo
rm
eat:
hea
tco
nd
uct
ion
and
mas
sd
iffu
sio
n
Hea
tco
nv
ecti
on
Ther
mal
radia
tion
-Mo
istu
reev
apo
rati
on
Mas
sco
nv
ecti
on
Lo
cal
val
ues
calc
ula
ted
fro
ma
pre
lim
inar
yC
FD
stea
dy
-st
ate
flo
wfi
eld
anal
ysi
s
Fro
mp
rev
iou
sst
ud
ies
Dif
fusi
vit
yfr
om
Tru
jill
oet
al.
[76]
Fo
llo
wed
sim
ula
tio
np
roto
col
pro
pose
db
yH
uan
dS
un
[35]
Ass
um
edco
nst
ant
loca
ltr
ansf
erco
effi
cien
tsd
uri
ng
the
coo
lin
gp
erio
d
Inco
rpora
ted
chan
ges
inw
ater
acti
vit
yo
nth
eca
rcas
ssu
rfac
e
62 Food Eng Rev (2013) 5:57–76
123
Ta
ble
1co
nti
nu
ed
Ref
eren
ces
Ap
pli
cati
on
Pro
du
ct(g
eom
etry
)T
echniq
ue
(so
ftw
are)
Go
ver
nin
geq
uat
ion
Bo
un
dar
yco
nd
itio
ns
Tra
nsf
erco
effi
cien
tsT
her
mal
pro
per
ties
Ad
dit
ion
ald
etai
ls
Wan
get
al.
[83]
Air
-bla
stco
oli
ng
tem
per
atu
rep
rofi
le
Co
ok
edh
am
(1/4
elli
pse
)
2D
fin
ite
elem
ents
(Vis
ual
C?
?)
2D
hea
tco
nd
uct
ion
Co
mbin
edh
eat
con
vec
tio
n
and
ther
mal
radia
tion
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
elli
pso
id
Lew
isre
lati
on
ship
Em
pir
ical
corr
elat
ions
[13
]V
alid
ated
inla
bo
rato
ryai
r-b
last
coo
ler
Inte
gra
ted
wit
hL
.p
lan
taru
mg
row
thm
od
el
Wan
gan
dS
un
[85–8
7]
Slo
wai
r,ai
rb
last
,w
ater
imm
ersi
on
coo
lin
gte
mp
erat
ure
pro
file
Co
ok
edm
eat
join
ts
(1/4
elli
pse
)
(1/4
bri
ck)
3D
/2D
fin
ite
elem
ents
(Vis
ual
C?
?)
3D
hea
tco
nd
uct
ion
Co
mbin
edh
eat
con
vec
tio
nan
dth
erm
alra
dia
tio
n
Mo
istu
reev
apo
rati
on
Em
pir
ical
corr
elat
ions
for
elli
pso
id
Lew
isre
lati
on
ship
Em
pir
ical
corr
elat
ions
of
mu
ltip
leso
urc
es
Use
din
terp
ola
tio
nto
acco
un
tfo
rn
on
-un
ifo
rmin
itia
lte
mp
erat
ure
s
Val
idat
edin
aco
mm
erci
alai
rco
ole
r
Stu
die
dth
eef
fect
of
air
vel
oci
tyo
nco
oli
ng
tim
e
Wan
gan
dS
un
[88]
Vac
uu
m-c
oo
lin
gte
mp
erat
ure
pro
file
and
wei
ght
loss
Co
ok
edm
eat
join
ts
(ell
ipso
idan
db
rick
)
3D
fin
ite
elem
ents
(Vis
ual
C?
?)
3D
hea
tco
nd
uct
ion
wit
hin
ner
hea
tg
ener
atio
n
Vap
or
tran
spo
rtw
ith
inn
erv
apo
rg
ener
atio
n(p
oro
us
med
ium
)
Hea
tra
dia
tio
n
Ev
apora
tiv
eh
eat
loss
Su
rfac
ep
ress
ure
=v
apo
rp
ress
ure
inv
acu
um
cham
ber
Em
pir
ical
corr
elat
ions
Rep
ort
edv
alu
esV
alid
ated
inla
bo
rato
ryse
ttin
gs
Incl
ud
edth
eef
fect
of
po
rous
dia
met
ero
nm
ass
tran
sfer
coef
fici
ent
Pro
po
sed
empir
ical
corr
elat
ion
sto
rela
tep
rod
uct
geo
met
ric
dim
ensi
on
sw
ith
pro
duct
wei
ght
Food Eng Rev (2013) 5:57–76 63
123
meat-matrix preparation step is used as the uniform initial
temperature to simulate heat transfer during cooking; and
the final cooking temperature is used as the uniform initial
temperature to simulate cooling. However, in real meat-
processing environments, transitory operations and/or
unexpected delays between processing steps are common;
resulting in non-uniform initial temperatures. Such is the
case of water showering prior to air cooling, which drops
the surface temperatures of the product. Hence, initial
temperatures of the product Tinitial should be represented as
a function of location:
Tinitial ¼ f x; y; zð Þ at t ¼ 0
Most proposed models lacked to consider this important
factor, which compromises model performance and limits
model applicability in the meat industry. For instance,
assuming temperatures around the product surface higher
than the actual values may increase the driving force for
convection and evaporation, resulting in overestimation of
cooling rates [12].
Regression models fitting experimental initial tempera-
tures as function of 1D and 2D (x, y) locations have been
used to predict non-uniform initial temperatures [1, 2, 42].
However, this approach is dependant on geometry and
process, which imply that a particular product and process
(e.g., 30 vs. 15 min water showering) would require its
own regression model. A better approach may be the usage
of preliminary analysis to simulate heat and mass trans-
fer taking place during the intermediate processing steps
[12, 74].
Boundary Conditions
Boundary conditions represent a set of physical restraints
that occur at the boundary of the system being analyzed.
When modeling heat transfer at the product level, boundary
conditions would include physics occurring at the product
surface due to interaction with the cooling/heating med-
ium. In traditional meat processing, thermal energy trans-
fers from the product surface to the air and vice versa by
convection and evaporation. In addition, thermal radiation
from the product surface can occur.
Heat Convection
Heat transfer due to convection is an important boundary
condition used for thermal processing modeling of meats.
As it is well known, convection encompasses thermal
energy movement between a fluid (e.g., air, water) and the
meat product surface. This phenomenon is usually modeled
by Newton’s law of cooling in which the heat flow due to
convection is equal to the convective heat transfer coeffi-
cient times the driving force [38]. The convective heat
transfer coefficient (hconv) is a function of the air proper-
ties, airflow conditions, and product shape. The driving
force is the difference between the bulk fluid temperature
(Ta) and the product surface temperature (Ts),
qconv ¼ hconv Ts � Tað Þ
Changes in heat load in the product are notoriously
affected by heat convection. Hu and Sun [35] estimated that
convection can be responsible for removing about 35 % of
the heat load removed during cooling of unwrapped meats.
The percentage may be higher in products where
evaporation is negligible. Rates of heat convection usually
increase in proportion with air velocity in the 0–5 m/s
range. This is because higher air velocities would lead to
higher convective heat transfer coefficients. However, rates
of heat convection would likely remain constant for air
velocities above 5 m/s, as the surface temperature would
reach thermal equilibrium faster. Hence, the cooling rate
would be controlled by conduction. As the thermal
conductivity of meats is low, higher air velocities would
not reduce the processing time [85].
Thermal Radiation
Some models include the effect of thermal radiation as a
boundary condition. The net rate at which radiation is
exchanged (qrad) between the surface of the meat (s) and
surrounding radiative surfaces (sur) is,
qrad ¼ er T4s � T4
sur
� �where the emissivity of the meat product (e) expresses
the fraction of incident energy absorbed by the meat, and
the Stefan–Boltzmann constant (r) is equal to 5.676 9
10-8 Wm-2K-4. A common practice to account for
thermal radiation is to consider the surrounding surfaces
to be at the same temperature of the airflow surrounding the
meat products (i.e., Tsur & Ta). In such a case, qrad can be
expressed as:
qrad ¼ er T4s � T4
a
� �¼ hrad Ts � Tað Þ
where hrad represents the radiative heat transfer coefficient.
Therefore, a collective effect of heat convection and
radiation could be calculated by Newton’s cooling law as,
qconv þ qrad ¼ h Ts � Tað Þ
where h represents the combined, also called effective, heat
transfer coefficient [1, 2, 42, 84].
The heat flow due to thermal radiation can be signifi-
cant, especially during heating treatments, as emissivity of
meat products can be as high as 0.9 [59]. However, radi-
ation effects have been neglected in various models [46,
47, 63, 66].
64 Food Eng Rev (2013) 5:57–76
123
Some studies have shown that heat transfer due to radi-
ation should be considered under industrial processing
conditions, as its effect is comparable to the convective heat
transfer phenomenon [42]. Radiation may be responsible for
about 15 % of the heat loss during air cooling [35]. Radia-
tion is theoretically higher during cooking operations; and it
is critical for modeling vacuum cooling [71].
Moisture Evaporation
Another boundary condition frequently used is the heat loss
due to evaporation. Evaporation can be defined as the
process by which available liquid water found at the meat
product surface is converted into vapor. The water phase
change process requires energy (i.e., latent heat of evapo-
ration), which is extracted from the product.
Considering moisture evaporation at the product surface
is particularly important for air cooling of unwrapped meat
products where evaporation may be responsible for
removing about 40 % of the total removed heat load [35].
Evaporation is responsible for about 2–5 % weight loss
during air cooling of unwrapped products [32].
Evaporative heat loss (qevap) is commonly described as,
qevap ¼ kv
omevap
ot
where the latent heat of vaporization (kv) is taken at the
average between the product temperature and the cooling/
heating medium temperature [14]. The evaporative weight
loss rate ðomevap=otÞ can be coupled with the mass transfer
governing equation.
A common strategy is to relate omevap=ot to the con-
vective mass transfer to the surrounding air due to the
vapor pressure difference between the meat surface and the
surrounding air,
omevap
ot¼ k00 Ps � Pað Þ
which can also be written as [14–16],
omevap
ot¼ k00 awps � RHpað Þ
where (k00) represents the mass transfer coefficient. The
following method based on the Antoine equation can be
used to estimate the saturation vapor pressure of water at
surface and cooling/heating medium temperatures, (ps) and
(pa), respectively [14, 70, 76, 84–88]:
p� ¼ exp 23:4795� 3; 990:56
T� þ 233:833
� �
where * can be substituted for the subscripts s or a.
Another similar approach to represent omevap=ot is to
define it as function of the mass fraction gradient of water
(dry basis) between meat surface (mw,s) and the air sur-
rounding the product (mw,a) [57],
omevap
ot¼ k00 mw;s � mw;a
� �
The mass fraction of water (dry basis) at the meat surface
can be calculated from [74]
mw;s ¼aw � ps=pTotal
1� aw � ps=pTotal
18
29
where pTotal represents the total pressure.
Moisture evaporation is a complex process regulated by
several parameters including air relative humidity, air
temperature, air velocity, airflow regime, water activity of
the product, product temperature, meat-matrix structure
(e.g., porosity, skin, fat regions), and type of product cas-
ings (e.g., fibrous casings, collagen casings, natural cas-
ings, nets). High airflows (i.e., 1–3 m/s) are necessary to
increase heat transfer coefficients and reduce processing
times. However, high airflows also increase the mass
transfer coefficients, increasing moisture evaporation and
weight loss rates [7]. Evaporation rates are reduced and can
be negligible when processing in high relative humidity
environments, wrapping the products, and/or lowering
cooking temperatures [66].
The evaporation process can be described in three
stages. During the initial stage, moisture from the meat
surface evaporates at the same rate as from a free water
surface. Then, the moisture evaporation rate from the
product surface decreases as the surface dries. Finally, the
moisture evaporation rate increases due to progressively
rewetting of the product surface by moisture migration
from product interior. Hence, the rate of evaporation is
influenced by the internal moisture transport and transport
properties of the product [32].
When internal moisture transport is not considered, a
practical approach to account for changes in surface
moisture is to consider surface water activity as a function
of time, or to assume a different value of water activity for
each of the three evaporation stages.
Mass Conservation
Models considering internal moisture transport include a
mass conservation boundary condition commonly descri-
bed by,
omevap
ot¼ q
omw
ot
����s
¼ Dqomw
oxnx þ
omw
oyny þ
omw
oznz
� �
which establishes that at the meat surface, the convective
moisture transfer rate to the surrounding air is equal to the
internal mass transport rate by diffusion.
Food Eng Rev (2013) 5:57–76 65
123
Additional Modeling Approaches
The previously discussed governing equations, boundary
conditions, and initial conditions correspond to the most
common methods used to define heat and mass transfer
problems oriented to practical food safety industrial
applications. In recent years, porous-media approaches for
heat and mass transfer modeling in meat products have
been proposed [17, 18, 24, 81]. Meat products may be
considered as capillary porous media as they are solids
having small void spaces filled with air, vapor, and liquid.
Hence, thermal processing of meats can be studied as a
phenomenon involving mass and thermal energy move-
ment through those interconnected void spaces. Porous-
media analysis consider that mass transport through a
porous material may occur due to molecular diffusion (for
gases), capillary diffusion (for liquids), and convection
(pressure driven or Darcy flow) [17, 90].
van der Sman [81] proposed a model based on porous-
media approaches for simulating water transport during meat
cooking. The model is based on the Flory–Rehner theory of
rubber elasticity. The model considers that during cooking
the muscle proteins denature, leading to decrease in their
water holding capacity and to shrinkage of the protein net-
work. The model considers evaporation of water from the
product surface, internal heat conduction, convective heat
transfer by water flow, dripping of water from the surface,
and one-dimensional heat transfer between meat and airflow.
The model was validated with experimental data collected
from roasting processes of rectangular pieces of beef [81].
Dhall et al. [24] proposed a multiphase multicomponent
model for modeling meat cooking based on porous-media
approaches. The model considers the flow of four fluids
through the meat matrix: water phase, liquid fat phase,
water vapor, and air. The definition of the model includes
mass balances equations for each of the fluids, and a global
energy equilibrium equation. The proposed model was
applied to double-sided contact heating of hamburger pat-
ties, considering the simulations from a frozen product.
Thus, phase change was considered in the analysis.
Recent developed models based on porous-medium
approaches are noteworthy. Such models allow for better
understanding of internal moisture transport in meat matri-
ces, including not only different components, but also the
interactions among them (e.g., water release from protein
matrix during heating due to protein denaturation). In
addition, models based on porous-media approaches may
allow for analysis of spatial profiles of not only temperature,
but also moisture content and fat content, which may be used
to determine critical points for microbial food safety.
Nevertheless, models based on porous-media approa-
ches are yet in development phase. Also, there is a lack of
data regarding some of the parameters and transport
properties required for simulations using porous-media-
based models. For instance, diffusivities of liquid water
phase and fat phase due to concentration gradients and
temperature gradients are difficult to estimate, and there is
a lack diffusivity values for meat reported at cooking
temperatures [24].
Therefore, porous-media approaches, to date, may be
unfeasible for practical microbial food safety applications.
Simpler models like the ones described in Table 1 seem to
be sufficient for the current needs of the meat industry as it
relates with microbial food safety applications. Advances
in simulation technology and further development on por-
ous-media modeling may provide opportunities of making
those models applicable to practical microbial food safety
applications in the future.
Transfer Coefficients
Heat Transfer Coefficient
The heat transfer coefficient is one of the most difficult
parameters to estimate when building models for industrial
applications. In meat-processing environments, there are
multiple factors that may affect the heat transfer coeffi-
cient. Examples of such factors include irregular product
shapes; variable product arrangement during processing;
turbulent, swirling and non-parallel airflow; variable
boundary layers; local variations of temperature and
thermo-physical properties around the oven/cooler and on
the meat surface; etc. Typical uncertainties of ±10–20 %
in predictions of heat transfer coefficients are frequently
reported in the literature [22].
Different strategies can be used to estimate heat transfer
coefficients. Some of the most common techniques include
the use of experimental values, assumptions from values
reported in the literature, and use of empirical correlations
(Table 2).
Using experimental h values would theoretically
improve model performance as inherent factors of the flow
regimen can be captured. Theoretical h values are com-
monly considered constant during simulations; which may
limit model applicability for industrial use.
The use of empirical correlations is a practical strategy
to incorporate the flow variations like the ones found in
industrial applications [23]. However, empirical correlation
models applicable to irregular geometries can be limited.
When empirical correlations for the specific geometry of
interest are not available, a set of experimental values (e.g.,
by the mass-loss rate method) can be used to select among
empirical correlations available for similar shapes. A
straightforward methodology to select among different
empirical correlations was described by Ryland et al. [62].
66 Food Eng Rev (2013) 5:57–76
123
The convective heat transfer coefficient hconv commonly
includes the effect of forced convection hfc and natural
convection hnc, following the empirical equation proposed
by [8, 21],
hconv ¼ffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffiffih3
fc þ h3nc
3
q
The radiative heat transfer coefficient is commonly
estimated by [1, 12, 21, 27, 83, 85–87]:
hrad ¼ re TK;s þ TK;a
� �T2
K;s þ T2K;a
�
where TK,s and TK,a correspond to the product surface and
air absolute temperatures in Kelvin, e represents the
emissivity of the product, and r is the Stefan–Boltzmann
constant, 5.676 9 10-8 Wm-2 K-4. Another common
equation used to estimate radiative heat transfer
coefficient is [42]:
hrad ¼ 4reT3a
The heat transfer coefficient is commonly used as a
combined or effective coefficient h representing the
collective effect of convection and radiation. It can be
calculated as [1, 2, 84]:
h ¼ hrad þ hconv
h can also be calculated as [42]:
h ¼ hconv 1þ hrad
hconv
þ kL
hconv
Ps � Pwbl
Ts � Twbl
� � �
Table 2 Strategies to estimate the heat transfer coefficient
Strategy Technique(s) Additional details Reference(s)
Experimental values Back calculations from transient
temperature data
A mathematical model is fitted to experimental data
h is back-calculated
[59, 64]
Measurements with commercial heat
flux/heat transfer sensors
h = heat flux reading/DT [10, 91]
Mass-loss rate and psychrometric methods Considers the constant drying rate period, where the
net heat flux exchange is equal to zero
h = experimental mass loss/latent heat of evaporation
[40, 39]
Empirical correlations
from dimensionless
numbers
Re, Pr, Ra, and Gr dimensionless numbers
calculated for specific flow conditions
Correlations used to estimate Nu for a
particular shape
Nu ¼ f ðRe;Pr;Ra;GrÞBack calculate h from
h ¼ kNuL
RTE meats (ellipsoid)
Nuð Þnc¼ 3:470þ 0:510Ra1=4
Nuð Þfc¼ 2ffiffiffippþ 0:150p1=4Re1=4 þ 0:350Re0:566� �
Pr1=3
Nu ¼ 0:32� 0:22G� �
Re 0:44þ0:23Gð Þ
[1, 2, 12, 92, 93,
67, 62, 85–87,
88]
RTE meats (horizontal ellipsoid)
Nuð Þnc¼ 3:470þ 0:510Ra1=4
Nuð Þfc¼ 2ffiffiffippþ 0:150p1=4Re1=4 þ 0:350Re0:566� �
Pr1=3
[83, 73]
Roast beef (circle)
Nu ¼ 0:683Re0:466Pr1=3
[29, 30]
Beef carcass (vertical surface)
Nuð Þnc¼ 0:555� Pr Grð Þ0:25
Beef carcass (slab)
Nuð Þfc¼ 0:664Re1=2Pr1=3
[20, 21]
Beef carcass (vertical plate)
Nu ¼ 0:228Re0:731Pr1=3
[46]
Beef carcass (fitted)
Nu ¼ C Re m_
Pr1=3TuA
[57, 74]
Cooked meat joints (horizontal cylinder)
Nuð Þnc¼ 1:02� Pr Grð Þ0:148
Nuð Þfc¼ 0:555Re0:633Pr0:333
[85–87]
Reported values Assumptions from values reported in the
literature for similar products and
operating conditions
Typical range
5\h\50 W
m2K
[42, 47, 48]
Preliminary CFD
simulation
Values of steady-state CFD simulation for
the air phase are used to back calculate hh = estimated heat flux from meat surface/DT
Allows estimation of local or average h
[35, 57, 74, 75]
Food Eng Rev (2013) 5:57–76 67
123
where Twbl represents the wet-bulb temperature and Pwbl
corresponds to the water vapor pressure calculated at wet-
bulb temperature.
Davey and Pham [20] accounted for the additional
resistance to heat transfer generated for visible sections of
fat in beef carcasses by estimating an effective heat transfer
coefficient as:
h ¼ 1
1ðhconvþhradÞ þ
Xfat
kfat
�
where Xfat represents fat thickness.
In meat-processing environments, heat transfer coeffi-
cients may vary between locations on the product surface
due to local variations in flow patterns surrounding the
product. Variations in local heat transfer coefficients can be
significant and should be taken into account, especially
when modeling heat transfer of products with complex
shapes. Willix et al. [91] calculated experimental values of
heat transfer coefficients at different locations on the sur-
face of a fiberglass model of a meat product with complex
shape (i.e., side of beef carcass). Authors showed that local
heat transfer variations can be as high as 140 % of the
mean, and they are more notorious as the air velocity and
turbulence intensity increase.
Calculations of local transfer coefficients can be
obtained by studying the fluid flow patterns surrounding the
product by computational fluid dynamics (CFD) analysis.
However, full CFD analysis can be complex as it requires
simultaneous calculation of continuity, momentum, energy
transport, mass transport, and turbulent dissipation rate
equations [74]. Moreover, CFD models may have issues
when modeling turbulent flow [39]. This is because tur-
bulence models require detailed modeling of boundary
layers near the product surface, in addition to several
empirical coefficients that may affect the accuracy of the
prediction [23, 55].
Hu and Sun [35] proposed a three-step methodology to
simulate heat and mass transfer with CFD-generated heat
transfer coefficients (Table 2). The methodology involves
an initial steady-state CFD simulation of the air phase,
followed by back calculation of mean heat transfer coef-
ficients in the second step. In the third step, the calculated
mean heat transfer coefficients can be used for the transient
heat and mass simulation at product level. The Hu and Sun
[35] method was further implemented by Trujillo and
Pham [74, 75] to allow calculation of local heat and mass
transfer coefficients in beef carcass cooling. The main
disadvantage of the three-step methodology is that the
calculated local transfer coefficients have to be assumed
constant during the heat–mass transfer simulation, which
may be unrealistic. Moreover, although the three-step
methodology requires less computational power than a full
CFD simulation, it still requires rigorous analysis; which
may be currently impractical for industrial applications.
Therefore, empirical correlations for estimating heat
transfer coefficients continue to be the best approach to
estimate heat transfer coefficients in models intended for
industrial use. However, CFD modeling can be a valuable
tool to simulate multiple flow conditions and irregular
shapes, and back calculate local heat transfer coefficients
[6, 55]. Then, the multiple CFD-generated heat transfer
coefficients can be fitted into empirical correlations that
allow the prediction of local variations, and inclusion of
turbulence effects. This approach has been successfully
implemented by Pham et al. [57] and Trujillo and Pham
[74].
Mass Transfer Coefficient
The mass transfer coefficient (k00) is also a difficult
parameter to estimate when building models for industrial
applications. As in the case of the heat transfer coefficient,
the mass transfer coefficient can be estimated from
experimental values [53], assumptions from values repor-
ted in the literature [58], use of empirical correlations, and
CFD simulations [57, 74, 75].
Nevertheless, the mass transfer coefficient is regularly
estimated from the Lewis relationship [20, 21, 42],
h
k00¼ Cp;aLe2=3
which relates the heat and mass transfer coefficients.
Analogies typically used to represent the proportion
between the heat and mass transfer coefficients based on
the Lewis relationship are presented in Table 3.
Thermo-physical Properties
Air Properties
Air properties such as viscosity, density, thermal conduc-
tivity, and specific heat are frequently calculated using
linear regressions of tabulated values found in the litera-
ture. Usually, they are calculated as a function of air
temperature [1, 37].
Meat Properties
Thermo-physical properties of meats such as specific heat,
thermal conductivity, and density are affected by temper-
ature and composition. It is well known that moisture and
fat contents are the most influencing parameters. Carbo-
hydrate content has been reported to be particularly
important for estimating density of meat emulsions [48].
68 Food Eng Rev (2013) 5:57–76
123
Meat emulsions with high carbohydrate content exhibit
lower densities during cooking due to several chemical and
structural changes take place in the meat matrix (e.g.,
volume expansion due to gelation). Other factors such as
meat fiber orientation have shown to influence the thermal
conductivity of fresh meats [80].
Thermal properties of meat products are fairly under-
stood under processing temperatures observed in traditional
thermal processing (i.e., product temperatures ranging
from 2 to 80 �C). For instance, ground beef exhibits
densities of 1,006–1,033 kg/m3 and thermal conductivities
of 0.35–0.41 W/m �C at 5–75 �C [54]. Thermal conduc-
tivity and specific heat of meat and poultry emulsions range
between 0.26–0.48 W/m �C and 2,850–3,380 J/kg �C,
respectively [25, 47, 48].
The empirical correlations for predicting thermal prop-
erties of food components as functions of composition and
temperature proposed by Choi and Okos [13] are the most
common correlations used when modeling heat and mass
transfer of unfrozen meat products. Studies have shown
that the maximum relative error between the observed and
predicted thermal properties of ready-to-eat meats using
Choi and Okos’s correlations was 5.3 % [62].
Alternative correlations to predict thermal conductivity
of meats have been proposed. For instance, a Kirschner-
based model to predict the thermal conductivity in different
meat emulsions proposed by Marcotte et al. [47, 48], and
linear-regression models to estimate thermal conductivity
of meat as a function of temperature and water content
proposed by Elansari and Hobani [25].
Thermal properties of meats are not fully understood
during freezing stages because the amount of ice formation
as a function of temperature is still under investigation.
Thermal conductivity of frozen meat products may be up to
2–3 times higher than the thermal conductivity of unfrozen
meat products. For instance, thermal conductivity of
fresh chicken and beef rapidly increases from about 0.5 to
1 W/m �C in the 0 to -3 �C range, and it continues increasing
to about 1.5 W/m �C when it reaches -40 �C [80]. van der
Sman [80] proposed a model to predict thermal conductivity
of frozen meats based on composition. The model is based on
a model for ice formation, and a model for predicting water
activity in frozen meats. Additionally, the model takes into
account the fibrous meat structure and the anisotropy of ice
crystals.
Water Activity in Meat
Surface water activity (aw) is another important property to
be estimated when modeling heat transfer. It is affected by
the water concentration on the surface of the product, the
presence of boundary layers and casings, and the rate of
evaporation. aw has been reported to be between 0.95 and
1.0 for most meat products [8, 82]. Hence, it is usually
assumed as a constant value within that range. According
to Daudin et al. [19, 21], aw slowly decreases during meat
cooling operations, but it remains between 0.95 and 1.0
during up to 23 h of cooling even when the drying rates are
very high. Hence, the common practice of considering
constant aw values is a practical strategy that may not have
considerable effects on the overall model performance.
However, there are situations when variations in surface
water activity are significant as the internal water move-
ment rate within the product may not be enough to main-
tain a fully wetted product surface during the entire
processing operation [14–16]. In such cases, models should
include the time-varying effects of aw to avoid incorrect
estimations of heat losses due to evaporation. For instance,
models for cooling of meat products should account for
three different aw values: one to represent the starting
condition, one to represent aw during active cooling, and
one to represent the quasi-equilibrium phase [14–16].
Variation in aw can be also estimated by empirical
models. For instance, van der Sman [80, 82] described an
empirical model to predict water activity in cooked meats
as a function of composition and salt content. The model
stated that aw can be estimated from the individual con-
tribution of added sodium chloride (NaCl) and/or sodium
polyphosphates (NaPP), and remain salts (ash):
aw ¼ aw;NaClaw;NaPPaw;ash
The NaCl contribution aw,NaCl can be estimated by an
approximation of the Pitzer equation [80, 82],
aw;NaCl ¼1
1þMwð1:868þ 0:0582mol1:618Þmol
where the molality mol can be calculated as:
mol ¼ MNaClmNaCl=mwf
The molar mass of water and NaCl are Mw = 18 g/mol and
MNaCl = 58.15 g/mol, respectively. mNaCl corresponds to
mass fraction of NaCl in wet basis (wb), and mwf represents
Table 3 Common strategies to account for mass transfer coefficient
from Lewis relationship
Typical application Equation References
Air cooling k00 ¼ hconv
Cp;a
ScPr
� ��2=3 [20, 21, 42]
Air cooling k00 ¼ hCp;a
Mw
MaP�1
atmðLeÞ�2=3 [10, 91]
Oven roasting, slow air, air
blast, water immersion
cooling
k00 ¼ hconv
64:7kvap
[66, 85–87]
Air cooling k00 ¼ 18h29Cp;aPatm
[14–16, 1,
2, 35, 46,
12]
Food Eng Rev (2013) 5:57–76 69
123
the current mass fraction of free water (wb) which can be
estimated as function of the current mass fraction of water
(mw), proteins (mp), and carbohydrates (mc),
mwf ¼ mw � 0:29mprot þ 0:1mcarb
On the other hand, the NaPP contribution aw,NaPP and the
remaining salts contribution aw,ash can be estimated by
Raoult’s law [80, 82]:
aw;� ¼mwf
mwf þ n�Mwm�=M�
where * can be substituted by the subscripts NaPP or ash.
The molar mass of NaPP and remaining salts are
MNaPP = 376 g/mol and Mash = 72 g/mol; with dissocia-
tion numbers nNaPP = 8 and nash = 2, respectively. In a
posterior study, van der Sman [79] described a method to
predict water activity and water holding capacity of meat
products using the free volume flory–Huggins (FVFH) the-
ory. The method allows for the prediction of water activity
and water holding capacity not only as a function of current
water and salt content, but also as a function of temperature.
For fresh meats having high aw (i.e., aw [ 0.9), aw has
been successfully estimated by the Lewicki equation [74],
mw;db ¼0:0488
ð1� awÞ0:8761� 0:0488
1þ a�34:7794w
where mw,db represents the mass fraction of water in dry
basis (db).
Moisture Diffusivity in Meat
Moisture diffusivity in the meat matrix D is commonly
taken from reported values. However, some empirical
correlations have been proposed. For instance, moisture
diffusivity in lean beef meat as a function of temperature
can be estimated using the following Arrhenius equation
proposed by Trujillo et al. [76],
D ¼ 4:67� 10�5 expð�3757:23=TÞm2s�1
Numerical Analysis
Heat and mass transfer modeling involves complex partial
differential equations that need to be solved by numerical
methods, as analytical solutions do not exist. Finite dif-
ference analysis (FD), finite element analysis (FEA), and
finite volume analysis (FVA) are three common numerical
methods (discretization methods) used in modeling of heat
and mass transfer.
In FDA, the product shape is approximated by a regular
geometry and equations are associated with heat flow
between the nodes. FDA is very simple to implement. It is
a practical method for one-dimensional models, but its
application is limited to products with regular shapes such
as cylinders, slabs, and boxes [22].
FEA is practical for products with irregular shapes. It can
be used to account for non-uniform material composition
and mixed boundary conditions. However, it is a more
complex method than finite differences. FEA states that a
problem involving differential equations over complex
geometries can be simplified by dividing the geometry into
small regions of well-understood behavior, called elements.
In other words, dividing the domain into simple small ele-
ments (e.g., triangles, tetrahedrons, or cubes) allows com-
plicated differential equations to be easily solved [52].
Hence, the behavior of a complex domain can be approxi-
mated by studying and accounting for the behavior of its
simple elements [94]. A step-by-step methodology to solve
heat transfer models for meat products by 3D FEA was
described in full detail by Cepeda et al. [11].
In FVA, the object is divided into small elements as in
finite elements; but the equations are imposed on the
control volumes rather than on the mesh nodes.
Various commercial/proprietary software packages
include general implementations of FDA, FEA, and FVA.
They can be used to solve heat and mass problems by
defining the specific model and inputting parameters
through user-friendly interfaces. Some common commer-
cial/proprietary packages include COMSOL Multiphysics,
ANSYS FLUENT, Abaqus SIMULIA, and NEi Nastran. It
is also common to build custom-made algorithms in differ-
ent computer programming languages/platforms (e.g.,
Matlab, C??, Visual Basic, and Java) to solve the models.
However, custom-made algorithms are usually restricted to
1D or 2D analysis due to programming complexity
(Table 2), although there are few exceptions including
Cepeda et al. [12], Santos [63], and Wang and Sun [84]. It is
important to validate custom-made algorithms by compar-
ing predicted temperatures against temperatures predicted
with analytical solutions (e.g., spheres and cylinders), or by
comparing simulation results against results obtained from
commercial/proprietary software packages.
Models for Food Safety Industrial Applications
Predictive microbiology models are useful tools for food
safety management and decision making in the meat indus-
try. They can be used to support hazard analysis, determi-
nation of critical limits, estimation of potential impact of
processing deviations, and simulation of multiple processing
scenarios for quantitative microbial risk assessment. A
thorough review on model definition of predictive microbial
models has been provided by Huang and Sheen [36].
Temperature is an important intrinsic factor affect-
ing microbial growth and inactivation. As a result, most
70 Food Eng Rev (2013) 5:57–76
123
predictive microbial models require the temperature pro-
files of the product as an input. Such temperature profiles
can be: (1) provided from recorded data, (2) estimated by
lumped-capacitance or analytical methods, or (3) estimated
by heat and mass transfer models like the ones discussed in
this review (Table 1).
Recording temperature profiles is a common practice in
the meat industry. However, the accuracy of the recorded
data may be compromised due to issues related with selec-
tion of adequate temperature probes (e.g., thick metal probes
that allow conduction of the heat through the metal sheath to
the tip of the probe), probe calibration, and probe placement
in irregular-shaped products [12]. Furthermore, temperature
is monitored usually at the core of a single product; which
does not reflect the actual temperature distribution of the
whole product, and may not capture differences among
products being processed simultaneously.
Simplified methods to estimate temperature profiles
involve the use of basic analytical solutions of heat transfer
problems, or the use of lumped-capacitance methods which
assume that the temperature of the product changes expo-
nentially with time,
T � Ta
T0 � Ta
¼ exp � hAs
qVCp
t
�
where h is the effective heat transfer coefficient (W/
m2 �C), Ta is the ambient temperature (�C); and T0 is the
initial temperature (�C), q is density (kg/ml), V is the vol-
ume (m3), and Cp is the specific heat (J/kg �C) of the meat
product.
However, simplified methods to estimate temperature
profiles may be inaccurate and only work under strict
conditions (e.g., uniform initial temperatures, Biot number
\0.1, and qVCp/hA ratio equal to total process time) [36].
Heat and mass transfer models like the ones discussed in
this review (Table 1), allow estimation of more accurate
temperature profiles. Each of the models included in this
review has weak and strong aspects that may affect its
applicability in industrial food safety applications. Con-
siderations involving definition of physics, product shape,
thermal properties, transfer coefficients, processing condi-
tions, in addition to validation procedures and model
availability, should be taken into account when selecting a
model for industrial use; and when developing future
models oriented toward food safety industrial applications.
Important considerations and future research opportunities
based on the strong and weak points of the current avail-
able models are discussed in the following sections.
Physics Considerations
The majority of the heat and mass transfer models that have
been developed in recent years consider physics occurring in
two dimensions. Such simplification is used to reduce model
complexity and computational time. However, two-dimen-
sional analysis may hold for different products where sym-
metry assumptions are valid (e.g., regular-shaped sausages)
[47, 48, 63], but it can be a source of errors for simulating heat
and mass transfer in products with complex shapes (e.g., bone-
in products, irregular-shaped ready-to-eat meats) [21, 42, 58].
On the other hand, heat and mass transfer is a multi-
physics phenomenon involving coupled energy transport,
internal mass transport, fluid flow variations, mechanical
deformation, and more. Internal mass transport and
mechanical deformation are yet poorly understood [26, 69],
and therefore neglected in many models for practical rea-
sons [1, 35, 83]. Research efforts by Datta [17, 18] and van
der Sman [79, 81] have provided better understanding of
internal moisture transport in meat products. Internal mass
transport in meat products should be further studied and
incorporated into future developed models.
It is also important to find a good balance between
inclusion of sophisticated physics and practicability for
industrial use. Including sophisticated physics may cause a
significant increase in model complexity and computational
time, which may not be reflected in significant improvement
of model accuracy. A perfect example was described by
Trujillo and Pham [74] in which a complete 3D CFD anal-
ysis of a beef carcass cooling proved to be impractical due to
technology limitations and excessive computational time
requirements. A simplified model integrating steady CFD
analysis with unsteady FE analysis was sufficient to provide
accurate temperature predictions in a reasonable time.
Advances in technology and commercial simulation
software may now provide the opportunity to incorporate
multiphysics analysis occurring in three dimensions [74,
75]; Le [53]. Also, different open-source algorithms to
solve three-dimensional problems such as the one devel-
oped by Cepeda et al. [12] are available.
Product Shape Considerations
Heat and mass transfer is shape dependent. Thus, adequate
shape of a product should be considered, especially in
products with complex shapes when shape simplifications
(e.g., assuming the shape of a chicken breast as an ellipse)
may lead to notorious deviations in the predictions. Current
computer-aided engineering (CAE) softwares such as
SolidWorks, CATIA, and Pro/ENGINEER provide tools to
build irregular product geometries, but yet very few models
have taken shape irregularity into account. Some examples
of models accounting for irregular-shaped product include
Trujillo and Pham [74] for cooling of beef carcasses,
Santos et al. [64] for heating of sausages, Goni and Sal-
vadori [29, 30] for roasting of beef, and Cepeda et al. [12]
for cooling of ready-to-eat meats.
Food Eng Rev (2013) 5:57–76 71
123
Irregular shapes can be generated by rough interpolation
of cross-sectional images, and by 3D scanning. Rough
shape interpolations from cross-sectional images can be
carried out by commercial CAE software [29, 30]. In
addition, there are commercial 3D scanners available in the
market that would allow a 3D representation of the surface
of an irregular-shaped product [41].
When dealing with meat products having a complex
internal composition (e.g., bone-in products), computer
tomography (CT) scanning, and medical imaging software
(e.g., materialize mimics) would allow for the inclusion of
the multiple materials and components found in the prod-
ucts (e.g., bone, fat, meat, skin). CT scans allow identifi-
cation of the different components of a product based on
the gray value of CT images (Fig. 1). A methodology to
build 3D representations from CT scans has been described
by Cepeda et al. [11, 12].
The effect of shape as a function of product weight may
be determined by interpolating and scaling 3D shapes of
known product weights.
Thermo-physical Properties Considerations
The majority of the heat and mass transfer models consider
meat products as materials with uniform composition. This
is a fair approximation for products such as cooked ready-
to-eat meats, but may be invalid for products exhibiting
complex compositions that may lead to significant varia-
tions in thermal properties such as bone-in products.
Geometry definition via CT scanning allows for the
incorporation of non-uniform product composition, without
adding major complexity to a heat and mass transfer
model. CT scanning can be used for identification and
selection of different materials (e.g., bone, fat, meat, skin)
present in a product, as each material would exhibit dif-
ferent image gray values. Then, geometries for each
material present in a product can be reconstructed from the
CT images, and proximate compositions can be assigned to
each material. Traditional empirical correlations may be
used to estimate thermo-physical properties of each mate-
rial as a function of temperature.
Considerations Regarding Processing Conditions
Heat and mass transfer models should be able to capture
the effect of time-varying processing conditions (e.g., air
relative humidity, air temperature, air velocity). Moreover,
the models should be able to include the effect of inter-
mediate processing steps (e.g., water showering) and
delays occurring in real processing environments that may
generate non-uniform initial temperatures.
Authors such as Cepeda et al. [12], Amezquita [1, 2],
Kuitche and Daudin [42], and Trujillo and Pham [74] have
incorporated the effect of non-uniform initial temperatures
in the models by regressions of experimental initial data, or
by preliminary heat transfer simulations. The use of pre-
liminary heat and mass transfer simulations is a practical
solution to account for typical intermediate processing steps
or delays occurring in meat processing. Further research and
model validations should be aimed at this area.
On the other hand, research efforts in recent years have
been concentrated on modeling heat and mass transfer of a
single product, as opposed to multiple products being
processed simultaneously. The model developed by Le
Page et al. [53] is one of the few that incorporate simula-
tions of stacked products, but it does not consider irregular-
shaped products. The lack of models involving irregular
products being processed simultaneously is due primarily
to issues related with modeling complexity and technology
limitations. However, recent advances in technology and
simulation software may overcome these issues. A good
example is the CFD model for simulating air cooling of
multiple beef carcasses proposed by Kuffi et al. [41].
Considerations Regarding Transfer Coefficients
The majority of the heat and mass transfer models devel-
oped in recent years use empirical correlations to estimate
Fig. 1 3D modeling of complex geometries by computer tomography CT scanning
72 Food Eng Rev (2013) 5:57–76
123
transfer coefficients. This approach has been valid for
multiple applications such as air cooling, vacuum cooling,
roasting and convection cooking of meat products of reg-
ular shapes. However, it is a fact that highly irregular
product geometries and challenging processing conditions
encountered in the meat industry may generate significant
variations in local heat transfer coefficients that cannot be
captured by traditional empirical correlations. CFD analy-
sis of airflow surrounding the products has been success-
fully used to estimate local transfer coefficients [35, 75].
However, CFD modeling, to date, seems to be impractical
as a tool for creating models that are easily applicable to
the meat industry. CFD models may be complex and
demand high computational power. Thus, they may not be
suitable for various practical applications in the meat
industry due to computational power limitations of current
technology. Nevertheless, simplified CFD models can be
used to run multiple simulations and generate data to
develop empirical correlations that allow estimation of
local transfer coefficients [74].
Validation Procedures
Model validation is critical to ensure model applicability in
the meat industry. However, most heat and mass transfer
models are validated under controlled laboratory settings;
thus, model performance under challenging meat-process-
ing facility conditions is uncertain. A limited number of
models have been validated in commercial meat facilities.
Examples of such validated models include the air-cooling
model for cooked boneless ham developed by Amezquita
et al. [1, 2], the air-cooling model for ready-to-eat meat
products developed by Cepeda et al. [12], and the models
for air cooling of beef carcasses developed by Trujillo and
Pham [74]. Further research efforts are needed to take the
validation process to the next level and prove that the
models can perform well in real industrial environments.
Another aspect to keep in mind is that meat processors
may not be able to provide all the input parameters
required for the simulation (e.g., product geometry, non-
uniform initial temperatures, time-varying processing
conditions). Hence, the model validation should include a
sensitivity analysis to determine how well the model can
perform with limited or uncertain input parameters. A
method to perform a sensitivity analysis has been described
by Kuitche et al. [42]. An example of model adaptation to
limited input parameters has been described by Cepeda
et al. [12].
Integration with Predictive Microbial Models
A limited number of heat and mass transfer models have
been integrated with predictive microbial models. A reason
for the scarcity of integrated models may be due to the fact
that experts in predictive microbiology modeling may not
have enough background in heat and mass transfer mod-
eling; and vice versa. Hence, further multidisciplinary
research and collaborations are needed to develop inte-
grated models that can be used to support food safety in the
meat industry.
Examples of integrated heat–mass transfer and predic-
tive microbial models include a model for air cooling of
ready-to-eat meats integrated with various dynamic
microbial growth models through a website [12]; a model
for air cooling of cooked boneless ham integrated with
microbial growth model of C. perfringens [2]; a model for
air-blast cooling of cooked ham integrated with a Lacto-
bacillus plantarum growth model [83]; a model for water-
bath heating of sausages integrated with a lethality model
for E. coli 0157:H7 [64]; a convection cooking model for
chicken breast integrated with lethality models for Listeria
innocua [58]; a model for inactivation kinetics of Salmo-
nella spp., L. monocytogenes, and other microorganisms
during pasteurization treatments of different food matrices
[28]; a model to predict E. coli growth in cartoned meat
undergoing thawing [56]; a model to estimate the effect of
drying and heating on the growth and inactivation of Lis-
teria [95]; and a cooking–cooling model for sausages
integrated with process lethality calculations for Salmo-
nella senftenberg, E. coli, L. monocytogenes, and Entero-
coccus faecalis [47, 48]. Additional integrated models not
included above have been discussed in a review by Lebert
and Lebert [43].
Model Availability
The main shortcoming of current heat and mass transfer
models is that most of them are not be readily available to
meat processors. There is a need for validated heat and
mass transfer models that can be easily accessed by meat
processors. Examples of research efforts focused on mak-
ing models available to meat processors include a general-
purpose food safety software developed by Halder et al.
[31], and a food safety website developed by Cepeda et al.
[12].
Halder et al. (2011) proposed a general-purpose pre-
dictive software package for food safety. The software
allows custom selection of product geometry, product
composition, processing conditions, and initial conditions
to simulate heat and mass transfer. The software allows
simulations using traditional heat and mass models, and
sophisticated models involving porous-media approaches.
The disadvantage of this software is that it is mainly a user-
friendly interface to COMSOL multiphysics, a commercial
simulation software. All the numerical and post-processing
analysis is performed in COMSOL multiphysics. Hence,
Food Eng Rev (2013) 5:57–76 73
123
meat processors must have a license for commercial use of
COMSOL multiphysics, in addition to basic knowledge/
training on post-processing methods in COMSOL; which
may be unattainable for some meat processors.
On the other hand, Cepeda et al. [12] developed a pro-
totype of an online tool for food safety (i.e., http://food
safety.unl.edu). The website allows online simulations
using various dynamic predictive microbial models, as well
as heat and mass transfer models validated in industrial
settings. However, the website is, to date, in development
phase and it currently has very limited models available.
Summary
In the last few decades, modeling has gained special
attention in the meat industry as it is considered as a
practical tool to assess meat safety quantitatively. Multiple
heat and mass transfer models for meat products have been
developed in recent years. Models range from traditional
energy and mass transport models to elaborated models
involving internal moisture transport and porous-media
approaches. However, despite the great advances in the
field, heat and mass transfer modeling of meat products
remains largely a research tool. Some of the currently
available models were built upon assumptions (e.g., sim-
plified physics, regular-shaped products, uniform product
compositions, average transfer coefficients, use of pro-
prietary software) that may limit applicability for food
safety industrial use.
Advances in technology and simulation software may
now allow further development of models that can capture
the complexity of heat–mass transfer physics that takes
place in industrial meat processing. Research efforts ori-
ented toward development of practical heat and mass
transfer models that can consider irregular-shaped prod-
ucts, products with non-uniform compositions (e.g., bone-
in products), products being processed simultaneously,
local transfer coefficients, and non-uniform initial condi-
tions, and that can be easily accessed by meat processors
are needed. Adequate estimation of transfer coefficients, as
well as of thermo-physical properties affecting microbial
growth such as water activity, is critical for accuracy of the
models. Hence, there is a need for validated methods to
accurately estimate transfer coefficients and thermo-phys-
ical properties, especially for irregular-shaped products,
and products with complex surfaces (e.g., products with
skin and/or significant sections of fat). Special consider-
ations regarding validations in commercial meat-process-
ing facilities, and integration with predictive microbial
models and/or risk assessment models are encouraged for
future models.
Acknowledgments This study is a contribution of the University of
Nebraska Agricultural Research Division, supported in part by funds
provided through the Hatch Act, USDA. Additional support was
provided by the USDA-IREE-CGP National Integrated Food Safety
Initiative Competitive Grants Program (Grant Contract Number:
2004-51110-01889). Mention of a trade name, proprietary products,
or company name is for presentation clarity and does not imply
endorsement by the authors or the University of Nebraska.
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