International Journal of Mechanical Engineering and Technology (IJMET)
Volume 10, Issue 01, January 2019, pp. 643–649, Article ID: IJMET_10_01_065
Available online at http://www.iaeme.com/ijmet/issues.asp?JType=IJMET&VType=10&IType=01
ISSN Print: 0976-6340 and ISSN Online: 0976-6359
© IAEME Publication
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COLD STORAGE DESIGN IN CONTAINER
Peter Sahupala and Reinyelda D. Latuheru
Mechanical Engineering Department, Faculty of Engineering, Universitas Musamus, Merauke,
Indonesia
ABSTRACT
The purpose of this paper is to calculate the cooling load in frozen shrimp cold
storage, calculate the performance of the vapor compression cycle including mass flow
rate, compressor power, and COP. This study uses a theoretical design method. The
design of cold storage for shrimp commodity, with the capacity of one container, will be
calculated how much cooling should be given so that the maximum cold storage efficiency
is obtained. Design data obtained from observations in the field. When the research was
conducted in April 2015. The calculation results show that the Refrigerant used is
Refrigerant 12 (R-12), Cooling load = 14.3022 TR = 50.254 kW, Shrimp product = 12
tons = 12,000 kg, Cold storage temperature: 10 ° C, Superheated: 5 ° C, Sub cooled: 5 °
C, refrigerant temperature in the condenser: 35 ° C, refrigerant temperature in the
evaporator: 5 ° C, condenser pressure: 0.80 MPa Pressure in the evaporator: 0.40 Bar
and COP: 4.76.
Keywords: Refrigerant, Cooling Load, Performance
Cite this Article: Peter Sahupala and Reinyelda D. Latuheru, Cold Storage Design in
Container, International Journal of Mechanical Engineering and Technology, 10(01),
2019, pp.643–649
http://www.iaeme.com/IJMET/issues.asp?JType=IJMET&VType=10&Type=01
1. INTRODUCTION
Shrimp is one of the seafood products that are liked and consumed by many people. Compared
to land animals, shrimp meat has better eating quality because it is not clay, homogeneous and
does not contain large blood vessels and muscles. Shrimp is very popular in the market because
of its distinctive taste, therefore marketing shrimp in fresh form is very popular with consumers.
One way to maintain the quality and freshness of the shrimp to be marketed is by freezing.
Because of its high protein content, shrimp is a perishable commodity caused by enzyme and
bacterial activities, therefore the handling of shrimp greatly affects the quality of processed
products. In order to maintain good quality, there is already a quality standard that includes raw
materials, handling methods, cooling and sanitation methods, both those carried out in factories
and in marketing and distribution.
The quality and freshness of shrimp must be maintained properly so that the shrimp reaches
the market or into the hands of consumers. Handling shrimp yields must be done quickly, because
the quality of shrimp is easily damaged. Errors or delays in handling result in shrimp not being
expected to become export commodities.
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Peter Sahupala and Reinyelda D. Latuheru
To maintain that the quality of shrimp remains good, it must be handled with care and not
carelessly, handling that must be paid attention to is the cleanliness of the equipment used,
handling must be fast and careful, avoid being exposed to direct sunlight, washing shrimp from
dirt and mud with clean water put in baskets, buckets or barrels and doused with clean water,
better than starting early using ice cubes to cool them, and grouping them according to their type
and size.
Cold Storage is one of the uses of refrigeration systems in the field of food preservation. Food
ingredients such as shrimp can rot easily, therefore to extend the shelf life of shrimp need to be
cooled. To inhibit bacterial growth and inhibit the activity of enzymes that can reduce the quality
of food, especially shrimp, shrimp is frozen in the freezer and then lowered in temperature and
experienced storage in cold storage.
From the above problems, the objectives of this paper are:
a) Calculate cooling load in frozen shrimp cold storage.
b) Calculate the performance of vapor compression cycles including mass flow rates,
compressor power, and COP.
2. METHODOLOGY
2.1. Research design
This study uses a theoretical design method. The design of cold storage for shrimp commodity,
with the capacity of one container will be calculated how much the cooling load must be given
so that the maximum cold storage efficiency. Design data obtained from observations in the field.
The time of the study was conducted in April 2015. Methods were provided (Maulany et al.,
2018; Samudro et al., 2018; Waremra, RS and Bahri, 2018).
2.2. Design of Cold Storage
Designing a cooling system in containers for shrimp commodity using referigeran R-12.
Recommended design data include the electrical installation refrigerator container ignored,
water flow rate rate 96.3 - 77 m3 / min, uniform shrimp temperature between 0oC-17.8oC,
steady state air condition and steady flow refrigerant flow, mean air temperature outside the
300C container, the outer surface temperature of the container is 36.8oC, cooling load
calculation using the reference method of the cooling load carrier method (TETD method).
The dimensions of the container are as follows:
1. Container dimensions = 2,438 m (height); 2,438 m (width); 6.096 m (length)
2. The type of product is shrimp
3. Place of shrimp: carton
4. Cardboard size: 46 cm (length) + 43 cm (width) + 40 cm (height)
5. Temperature of the outside air cooler 30oC.
The container material layer can be shown as follows:
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Cold Storage Design in Container
Figure 1. Layer of container building material
3. RESULTS AND DISCUSSION
Furthermore, as explained earlier, the design dimensions are as follows:
a. Container Size: Height: 2,438 meters; Width: 2,438 meters; Length: 6.096 meters
b. Product type: Shrimp
c. Maximum load: 12 tons
d. Place of shrimp: Carton
e. Carton Dimension: Height: 40 cm; Width: 43 cm; Length: 46 cm
f. The outside air temperature is 300C
g. The air temperature in the container is assumed to be uniform which is -17.8oC
h. The average air flow rate is 96.3-77 m3 / minute.
By knowing the data above, we can calculate the cooling load.
1. Outside air temperature of the container
Tf = T∞ + Ti
Tf = 32+ 273 = 305 K
2. Air temperature in the container
Tf '= -17.8 + 273
Tf '= 255.2 K
3. Transmission load
a. Outer container
The type of flow is determined using the Reynold Number equation.
where:
ρ : Type of fluid mass (1.17 kg/m3)
μ : Absolute viscosity (4.81 x 10-6 kg/m.s)
V : Initial fluid speed (5.5 m/s)
L : Container length (6.096 m)
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Peter Sahupala and Reinyelda D. Latuheru
So that it is obtained:
(turbulence)
The type of convection heat transfer is determined by the comparison equation of the Grasof
Number with the Reynold Number.
where:
g : Gravity acceleration (9.81 m/s2)
ν : Kinematic viscosity (20.75 x 10-6 m2/s)
β : Volumetric Thermal Expansion Coefficient
β = 1/Tf = 1/255,2 = 0,00392 K-1
Then obtained:
0,00386 < 1 (Forced convection)
The comparison is as follows:
=
= 5.79873 x 10-15
The surface area of walls and doors is:
Awalls
= (2.438 x 6096 x 1.219) + (2.438 x 2.438 x 1.219)
= 25.362 m2
Then large cooling loads through walls and doors:
The surface area of the roof is:
Aroof. = 2.438 m x 6.096 m
= 14.862 m2
then large cooling loads through the roof:
The surface area of the floor is:
Afloor = 2.438 m x 6.096 m
Afloor = 14.862 m2
Then the large cooling load through the floor is:
So that the total cooling load through the building / container is:
Qbuilding = q1 + q2 + q3
Qbuilding = 386.645 + 219.868 + 165.209
Qbuilding = 771.722 Watt
The product cooling load is above freezing: q1 = 6081 kJ/hour
Cooling load for the freezing process: q2 = 118338.33 kJ.hour
Cooling load below freezing: q3 = -10203.72 kJ/hour
So the total cooling load of the product above is:
Qproduct = q1 + q2 + q3 = 114215.63 kJ/hour
As a result of the cold storage door that is sometimes opened so that it will cause air
permeation or air change, therefore the cooling load can be determined by the following equation:
V = Volume of room
V=PxLxT
V = 6,096 x 2,438 x 2,438
V = 36.2336 m3 = 1279.5775 ft3
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Cold Storage Design in Container
If it is assumed that within 24 hours the cold storaga door is opened for 5 times to carry out
work activities then 5/24 = 0.2083 and air change factors at room temperature 30oC (86 F) and
cold storage temperatures 10oC (50 F) with a humidity ratio of 60% 1.50 BTU / cu.ft, then
obtained:
Qpu = 1279.577508 x 0.2083 x 1.50
Qpu = 399.804 BTU/hour
Qpu = 421.817 kJ/hour
The light beam radiation will also affect the cold storage cooling load, this also depends on
the number and specifications of the lights. In this design, the lamp data installed is as follows:
a. Number of lights: 1 piece
b. Lamp power: 5 Watts
c. Ignition time: 24 hours
d. Lamp type: TL (allowance factor value = 1.25)
From the data above, the cooling load is obtained due to lighting factors:
qWatt = Watt total x use factor x allowance factor
qWatt = 5 x 3.4 x 1.25
qWatt = 21.25 kJ/hour
Electric motors are used in the cooling cycle, which serves to rotate the evaporator fan so that
the evaporator can emit heat. It is planned that the electric motor power is 8 HP and works 24
hours so that the cooling load can be determined as follows:
qm = motor load factor x motor power x number of motors
qm = 3700 BTU/HP.hour x 8 HP x 1
qm = 29600 BTU/hour
qm = 31229.766 kJ/hour
It is assumed that the entry limit for cold storage is 5 workers and the working time per day
is 3 hours, the heat from the human body is equivalent to 1000 BTU / hour so that it is obtained:
qpek = the number of workers x work hour x equivalent heat
qpek = 5 x 3 x 1000
qpek = 15000 BTU/hour
qpek = 15840 kJ/hour
The total heat generated is equal to:
Qtotal = ql + qm + qpek
Qtotal = 21.25 + 31229.766 + 15840
Qtotal = 47090.016 kJ/hour
The total cooling load for cold storage is:
Qteo = qbuilding + qproduct + Qk + Qpu + Qtot
Qteo = 2778.1992 + 114215.63 + 96 + 421.817 + 47090.016
Qteo = 164601.6622 kJ/hour
Qteo = 156024 BTU/hour
If there is an excessive load, so that there is no over load on the engine, it needs to add a safety
factor of 10%, so that it is obtained:
10% safety factor = 156024 BTU/hour
= 171626.4BTU/hour
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Peter Sahupala and Reinyelda D. Latuheru
So the total cooling load is
= 14.3022 TR (ton refrigerant)
= 50.254 kW
The P-h diagram for R-12, we assume the initial data is as follows:
a. Refrigerant used: R-12
b. Cold storage temperature: 10oC
c. Superheated: 5oC
d. Subcolling: 5oC
e. The temperature of the refrigerant is in the condensor: 35oC
f. Pressure on the condenser: 0.80 Mpa
g. Pressure on the evaporator: 0.40 MPa
Obtained the following results:
Point 1
P1 = 0,40 Mpa
h1 = 215 kJ/kg
Point 2
P2 = 0,80 Mpa
H2 = 240 kJ/kg
Point 3
P3 = 0,80 Mpa
h3 = 96 kJ/kg
Point 4
P4 = 0,40 Mpa
h4 = 96 kJ/kg
a. Reynolds numbers
Re = h1 – h4
Re = 215 – 96
Re = 119 kJ/kg
b. The refrigerant cycle in the evaporator
c. Compressor power
P = G x (h2 – h1)
P = 0,4223 x (240 – 215)
P = 10.5575 kW
Thus the COP is obtained, determined by the following equation:
COP = 4.76
4. CONCLUSION
Based on the calculation of cooling load, it can be concluded as follows:
1. The design of this type of refrigerant used is Refrigerant 12 (R-12). The cycle cooling load
is 14.3022 TR or 50.254 kW. Cold storage designed for the preservation of shrimp with a capacity
of 12 tons or 12,000 kg.
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Cold Storage Design in Container
2. Design parameters include Cooling temperature in cold storage 10 ° C, Superheated
temperature is 5 ° C, Sub cooled temperature is 5 ° C, Refrigerant temperature in the condenser
is 35 ° C, Refrigerant temperature in the evaporator is 5 ° C, Pressure in the condenser is 0.80
MPa, the pressure in the evaporator is 0.40 MPa so that the coefficien of performance (COP) of
4.76 is obtained.
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